api specification 1584 ip 3rd ed. 2001 four-inch hydrant system components and arrangements (1)
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FOUR-INCH HYDRANT SYSTEM
COMPONENTS AND ARRANGEMENTS
API/IP SPECIFICATION 1584
Third edition
April 2001
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FOUR-INCH HYDRANT SYSTEM
COMPONENTS AND ARRANGEMENTS
API/IP SPECIFICATION 1584
Third edition
April 2001
Published jointly by
American Petroleum Institute
and
The Institute of Petroleum, London
A charitable company limited by guarantee
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Copyright © 2001 by American Petroleum Institute, andThe Institute of Petroleum, London:
A charitable company limited by guarantee. Registered No. 135273, England
All rights reserved
No part of this book may be reproduced by any means, or transmitted or translated into
a machine language without the written permission of the publisher.
ISBN 0 85293 280 4
Published by The Institute of Petroleum
Further copies can be obtained from Portland Press Ltd. Commerce Way,
Whitehall Industrial Estate, Colchester CO2 8HP, UK. Tel: 44 (0) 1206 796 351
email: [email protected]
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v
CONTENTS
Page
Foreword . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . vii
Acknowledgements . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ix
1 Introduction, scope and referenced publications . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1
1.1 Introduction . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1
1.2 Scope . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1
1.3 Referenced publications . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2
2 Terms, definitions and abbreviations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3
2.1 Terms and definitions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3
2.2 Abbreviations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5
2.3 Units used . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5
3 General arrangements and features . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7
3.1 Typical arrangement of hydrant pit equipment and controls . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7
3.2 Mandatory requirements . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7
3.3 Optional items . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 19
4 Performance criteria and testing procedures . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21
4.1 Mechanical strength . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21
4.2 Test fluid . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21
4.3 Dimensional checks . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21
4.4 Proof and burst pressure . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 21
4.5 Pressure loss . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 22
4.6 Opening and closing times and overshoot . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 22
4.7 Vacuum test . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23
4.8 Pilot device override test . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23
4.9 External load resistance and failure mode . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23
4.10 Catastrophic excess flow . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 25
4.11 Decoupling spillage . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 26
4.12 Pressure, surge and flow control . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 26
5 Type approval testing and quality assurance . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27
5.1 Quality assurance . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27
5.2 Approval testing . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27
5.3 Documentation and instruction . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27
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Contents Cont.. Page
Annex A - Catastrophic excess flow . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 29
Annex B - Hydrant pit valve assemblies in small pit boxes . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 31
Annex C - Hydrant riser stress during impact of the hydrant pit valve/hydrant coupler assembly . . . . 33
Annex D - Air-operated pilot devices . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 35
Annex E - The inspection and testing of airport hydrant pit valves . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 37
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vii
FOREWORD
This joint Institute of Petroleum and American Petroleum Institute publication provides recommended minimum
performance and mechanical specifications for the design of aviation fuel hydrant system pit valves and associated
couplers.
This publication also specifies requirements that need to be met to achieve full interchangeability between
components of various manufacturers and requirements for optional features which component manufacturers may
be requested by users to provide.
This publication has been produced jointly by the API Aviation Technical Services Subcommittee and the IP
Aviation Committee. It replaces API Standard 1584 second edition, December 1994, IP Aviation hydrant pit systems
recommended arrangements, August 1990 and IP The inspection and testing of airport hydrant pit valves, July
1993.
It is possible that this joint publication will have a wider scope of usage and will encompass differing operating
practices and safety and environmental legislation. Therefore, this publication should be read in conjunction with
appropriate national and local statutory operating requirements. It is recommended that, if procedures defined in
this publication are more stringent than those at the point of use are they should be followed.
Whilst the use of hydrant pit valve assemblies designed for use with 150 mm (6 in.) hydrant riser flanges is
preferred, requirements for valves that are able to mate with other flanges are also included.
The requirements of this publication are not retroactive. Users of existing equipment should decide what action to
take if equipment in current use does not conform to the requirements of this edition. Due consideration should be
taken of the safety implications of non-conformance.
Within six months of the publication of this edition, manufacturers will be expected to be able to supplymodification kits, where necessary, for any existing equipment that does not conform to the requirements of this
edition.
The Institute of Petroleum and American Petroleum Institute are not undertaking to meet 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 and regional laws and
regulations.
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viii
Nothing contained in any Institute of Petroleum or American Petroleum Institute joint 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.
Although it is hoped and anticipated that this publication will assist both the manufacturers and purchasers of
aviation fuel hydrant system pit valves and couplers, the Institute of Petroleum and the American Petroleum Institutecannot accept any responsibility, of whatever kind, for damage or loss, or alleged damage or loss, arising or
otherwise occurring as a result of the application of the specifications or qualification procedures contained herein.
Suggested revisions are invited and should be submitted to the Manager of Standardization, American Petroleum
Institute, 1220 L Street, N.W., Washington, D.C. 20005, USA or to the Technical Department, Institute of
Petroleum, 61 New Cavendish Street, London W1G 7AR, UK.
Note for users of equipment covered by this publication. This publication includes a requirement for couplers
to break away cleanly from the pit valve adapter if struck with a force as defined herein. It is recommended
that, if a pit valve/coupler assembly is struck with sufficient force to remove the coupler during refuelling
operations, the pit valve should be removed from service for inspection and tested to prove its suitability for
further use. Users are referred to the recommended post-impact action in Annex C.
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ix
ACKNOWLEDGEMENTS
This edition of API/IP 1584 has been prepared by the IP Equipment Sub-Committee on behalf of the Institute of
Petroleum and the American Petroleum Institute Aviation Technical Services Sub-Committee. Much of the
redrafting was undertaken by Bob Simpson (Consultant) and Adrian Hamra (ExxonMobil).
Draft versions of this third edition were reviewed by representatives of the following companies:
AgipPetroli
Air BP Limited
Air TOTAL
Avery Hardoll SBU, BAE Systems Power & Control Ltd.
Caltex Corporation
Carter Ground Fueling Co.
Chevron Products Co.
Conoco Limited
Elf Aviation International
Equilon Enterprises
ExxonMobil Aviation International Ltd.
Intertechnique Zenith Aviation
Kuwait Petroleum International Aviation Company Ltd.
Phillips 66 Company
Shell Aviation Ltd.
Texaco Global Aviation Marketing Ltd.
Whittaker Controls Inc.
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x
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1
1
INTRODUCTION, SCOPE
AND REFERENCED PUBLICATIONS
1.1 INTRODUCTION
The performance requirements and optional
recommendations included in this publication are
intended to achieve the following:
(a) Establish the acceptable structural and operatingintegrity of the components involved.
(b) Provide a compatible coupling configuration and
arrangement at the hydrant pit that will permit
interchangeability between the components of
different manufacturers.
(c) Assist component manufacturers in their design
efforts by detailing operational, maintenance and
ergonomic features of components that are
considered desirable based upon experience in
aircraft fuelling.
(d) Describe the alternative arrangements of hydrant
pit components that are typical for API and IP 4
inch hydrant systems and thereby assist component
manufacturers and aircraft fuelling system
designers and operators in their efforts.
(e) Provide mechanical strength criteria for normal
handling loads and failure modes for excess
mechanical loadings and impact damage.
1.2 SCOPE
1.2.1 General
This publication specifies dimensions, coupling action,
activation, and other requirements to achieve the
necessary operational requirements and fullinterchangeability between components from
manufacturers of hydrant pit valve assemblies and
couplers. It also includes requirements for other
optional features which component manufacturers may
be requested to provide by purchasers. The performance
specifications are for equipment intended for systems in
aviation turbine fuel service. They do not apply to
aviation gasoline (Avgas).
1.2.2 Organization
If complete interchangeability is to be attained, certainfeatures of the mating components shall be
standardised. Other features, although desirable, are not
so critical, but are pointed out to assist manufacturers in
the design of these components.
The pit valve and coupler, along with any other
features attached, are considered to be as a whole for
the purposes of this publication.
Section 3 covers general arrangement and features,
specifying those features of the hydrant components
that are mandatory, as well as those that are optional.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
2
They are listed as "Mandatory" and "Optional"
respectively. Section 4 describes performance criteria
and test requirements for the hydrant pit valve assembly
and hydrant coupler. Section 5 contains the quality
assurance and information requirements. Five annexesare included for information only.
1.3 REFERENCED PUBLICATIONS
The following publications are cited in this publication.
The latest available edition of each referenced
publication applies.
API
RP 1004 Bottom loading and vapour recovery for
MC-306 tank motor vehicles.
Specification Q1 Specification for quality
programs for the petroleum and natural gas
industry.
ASME 1
B.16.5 Pipe flanges and flanged fittings.
IP 2
Fuel hydrant riser pipe stress analysis due to
accidental impact loads.
The closure behaviour of aviation hydrant pit valves (Delft Hydraulics).
Sanderson, T.A., and Simpson, R.A. 1990, Excess
flow testing of hydrant pit valves, Petroleum
Review, May 1990.
ISO 3
9000:2000 Quality management systems.
10012-1 Quality assurance requirements for
measuring equipment: Metrological confirmation
system for measuring equipment .
SAE 4
ARP 868A Method pressure drop test for fuel
system components.
1. American Society of Mechanical Engineers, 3 Park Avenue, New York, NY 10016-5990, USA. www.asme.org
2. Available from the Institute of Petroleum library, 61 New Cavendish Street, London W1G 7AR, UK
3. International Organization for Standardization, Case Postale 56, CH-1211 Geneva, Switzerland. www.iso.ch
4. Society of Automotive Engineers, 400 Commonwealth Drive, Warrendale, PA 15096-0001, USA. www.sae.org
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3
2
TERMS, DEFINITIONS AND
ABBREVIATIONS
2.1 TERMS AND DEFINITIONS
For the purposes of this publication the following terms
and definitions apply:
clean breakaway: when used in describing the
breakaway of the hydrant coupler from the hydrant pitvalve adapter, means that the coupler breaks away
completely to allow the pit valve outlet adapter poppet
to close. In practice, complete seating of the poppet
cannot be guaranteed as coupler debris that may be left
could prevent full poppet closing.
hydrant coupler: a unit that is attached to the inlet end
of the hydrant dispenser inlet hose or boom assembly to
provide for quick coupling to the outlet adapter of the
hydrant pit valve assembly. The coupler may be one of
four types, any of which can be equipped for product
selectivity:
— standard coupler : a quick coupling device that
allows for manually opening and closing the
poppet on the hydrant pit valve assembly and
provides a flow path from the hydrant pit valve
assembly to the dispenser.
— direct acting digital control coupler : a coupler that
incorporates the same features as a standard
coupler, but uses a digital module to control
pressure and flow for each hose combination. A
timer deadman may be included with this system as
an option.
— direct acting pressure control coupler : a coupler
that incorporates the same features as the standard
unit, but also includes air-operated deadman and
spring biased pressure regulation at a remotesensing point. This coupler also has optional
excess flow control.
— pilot-operated pressure control coupler : a coupler
that has the same features as the standard unit, plus
the air deadman feature, but controls pressure by
means of a pilot mechanism. This coupler also has
optional excess flow control (with either single or
dual flow rate settings).
hydrant coupler carriage assembly: a device fitted to
the hydrant coupler to assist in moving the coupler toand from the pit valve whilst keeping the coupler from
dragging on the ground.
Note: It generally takes the form of two small
wheels on a structure that may be folded up beneath the
inlet hose when not in use.
hydrant dispenser: (also known as 'hydrant servicer',
'aircraft fuel servicer' or 'hydrant cart') a fuelling unit
used to receive fuel from a hydrant fuel supply system
and deliver it to aircraft. It may be self-propelled, trailer
mounted or skid mounted.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
4
Note: It is normally fitted with filtration, pressure
control, deadman control and metering equipment and
is connected to the hydrant pit valve by a hydrant
coupler and an inlet hose or metal boom assembly. The
hydrant dispenser is used to deliver fuel into aircraft viaa delivery hose and nozzle.
hydrant pit valve assembly: a valve that is vertically
mounted on the flanged riser of an airport fuel piping
system.
Note: The valve is composed of three components:
the flanged inlet pilot-operated valve, the pilot device
and the outlet adapter that mates with the hydrant
coupler. Optional features may be included.
— intermediate strainer : an optional fine mesh screen
that is mounted internal to the hydrant pit valveassembly, normally between the pilot-operated
valve and the outlet adapter.
Note: The use of such a strainer is not
recommended.
— outlet adapter : the outlet portion of the hydrant pit
valve assembly to which the hydrant coupler
mates. The outlet adapter has a poppet that is
opened and closed by the coupler poppet. The
outlet adapter provides a seating for the poppet and
for optional product selectivity.
— pilot device: a mechanism which diverts pressure
to and from the actuating element of the pilot-
operated valve to enable it to either open or close
in a controlled manner.
Note: The required methods for operating the
pilot device are defined in 3.2.8.
— pilot device override: (also known as a 'servicing
valve') a manually operated valve or device that
overrides the action of the pilot valve thus
preventing opening of the pilot-operated valve.
— pilot-operated valve: located at the inlet, it forms
an integral part of the hydrant pit valve assembly
and isolates downstream components from the fuel
hydrant supply pressure. It is operated by the pilot
device and controls the flow of fuel out of the
hydrant pit valve assembly.
— pressure equalisation valve: a small valve located
in the centre of the outlet adapter poppet that is
actuated by the hydrant coupler poppet. This valve
allows equalisation of the pressure contained
within the hydrant pit valve assembly with the
pressure within the hydrant coupler.
— stoneguard : a mandatory coarse mesh screen (e.g.
5 mm or ¼ in. or equivalent) perforated metalstrainer that is mounted upstream of the hydrant pit
valve assembly to impede the flow of large debris
normally foreign to fuel systems.
flow:
— automatic excess flow control : a device installed on
or within the hydrant pit valve assembly and/or
coupler to prevent excess flow.
Note: Upon the flow rate increasing to a
predetermined level, the device will actuate the
hydrant pit valve assembly and/or coupler to close
and remain closed until the excess flow controldevice is reset.
— catastrophic excess flow: the maximum flow rate
required to be stopped by the hydrant pit valve.
— excess flow: a flow rate in excess of rated flow.
— rated flow: the maximum flow rate for which the
components of the pit valve assembly and coupler
are designed.
in-line pressure control (or regulating) valve: a valveinstalled on board the hydrant dispenser forming a part
of the fuel pressure control (or regulating) system. It
may also provide a deadman operation, being opened
and closed remotely by the fuelling operator. This valve
is outside of the scope of this publication and may be
fitted at the discretion of the user.
opening and closing times:
— closing time: the time required, after the operating
device is actuated to close, for flow to cease from
rated flow.
— deadman control : a hand-held control to actuate
the opening and closing of the hydrant pit valve
assembly and/or hydrant coupler.
— opening time: the time taken to achieve 90 % of
rated flow measured from the time that the
operating device is actuated.
— overshoot : the volume of liquid passing through
the valve during the closing time period.
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TERMS, DEFINITIONS AND ABBREVIATIONS
5
pressure:
— burst pressure: the pressure causing structural
failure of the external casing of the hydrant pit
components covered by this publication.
Note: For the purposes of this publication, the pressure defined in 4.4.2 is the minimum pressure
above which structural failure may occur.
— design pressure: the maximum pressure to which
the hydrant pit components will be subjected in
service.
Note: This pressure equates to operating
pressure plus surge pressure to which the
equipment may be exposed. The performance
criteria of this document do not apply at design
pressure.
— operating pressure: the maximum steady state
pump pressure that can be experienced in the
system. At this maximum pressure, the hydrant pit
valve assembly and coupler are required to
conform to the performance criteria of this
publication.
— pressure loss: the difference in static pressures
measured in the test set-up defined in Figure 6
from point A to point B.
— proof pressure: the maximum pressure required of the hydrant pit components without external
leakage or damage after which the components will
meet all other performance requirements.
pressure control valve: a control valve that may be
located either in the hydrant pit valve assembly or in the
hydrant coupler assembly. This valve forms part of the
pressure and flow control system delivering fuel to the
aircraft. May also be known as a pressure-regulating
valve.
vacuum test: a negative pressure applied to the hydrant
pit valve assembly under which the poppet shall remain
closed and not allow leakage of air in the reverse
direction.
2.2 ABBREVIATIONS
The following abbreviations are used within this
publication:
ft feet
in. inch
kg kilogram
kPa kiloPascal
kph kilometres per hour
lbs pounds mass
lbf pounds force
lpm litres per minute
m metre
mm millimetre
mph miles per hour
N Newton psi pounds per square in.
USG US gallon
USGPM US gallons per minuteoF degrees FahrenheitoC degrees Celsiuso degree of angle
2.3 UNITS USED
This publication uses the Système International
d’Unités (International System of Units or SI). In thissystem, the decimal point is a comma (,). In writing
numbers of greater than 3 digits, e.g. thousands, tens of
thousands etc. a comma may not be used to demarcate
the thousands. Thousands are demarcated by the use of
a space.
Within this publication SI Units are used with US
Customary Units following in parentheses.
Internationally agreed conversions have been applied to
these values.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
6
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7
3
GENERAL ARRANGEMENTS
AND FEATURES
3.1 TYPICAL ARRANGEMENT OF HYDRANT
PIT EQUIPMENT AND CONTROLS
A number of alternative component arrangements are
offered, essentially determined by the location of one or
more of the controls. The two extremes are shown in
Figures 1 and 2. In Figure 1, the controls are in aregulating valve installed inside the coupler. In Figure
2, the controls are in the pit valve assembly. The
purchaser shall specify the final component
arrangement. The fitting of a separate hydrant riser
shut-off valve is not a requirement of this publication.
3.2 MANDATORY REQUIREMENTS
3.2.1 Dimensions and hydrant coupler/hydrant
pit valve assembly mating
The interface dimensions of the outlet adapter of the
hydrant pit valve assembly and the hydrant coupler
shall be in accordance with Figures 3A and 4A and 3B
and 4B (US Customary Units). The sealing surface as
indicated on Figures 3A and 3B shall be 1,6 micrometre
(63 micro-inches) circular finish maximum. The outlet
adapter poppet, including activation of the pressure
relief equalising valve, shall allow a coupler poppet
travel of 50,8 +1,588/-0,000 mm (2 +0,0625/-0,000 in.)
measured from the sealing surface as identified on
Figures 3A and 3B.
A static seal shall be achieved automatically
between the coupler and outlet adapter during the
coupling and locking operations and before the adapter
is actuated to open. The static seal shall be designed sothat it cannot be broken until the outlet adapter and
coupler are closed. Leakage in excess of 30 ml (1 fluid
ounce) through the static seal shall not occur at any time
during the coupling, fuelling, and uncoupling operation,
regardless of system pressure. See 4.11 for test details.
3.2.2 Outlet adapter actuation
The opening of the hydrant coupler poppet shall cause
the outlet adapter poppet to open. The outlet adapter
poppet shall close automatically whenever the coupler
is closed or removed. In manual operation, the outletadapter and hydrant coupler when coupled together
shall be capable of being opened and closed by one
operator applying a maximum force of 110 N (25 lbf).
To function properly, the force shall be applied for a
maximum of 5 seconds to hold the equalisation valve
open and allow the pressure to equalise on both sides of
the outlet adapter poppet.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
8
Hydrant coupler with deadman and pressure control
Air to pilot device (if air-operated)
Outlet adapter
Fuel sense
Deadman air
Lanyard attachment point
Pilot device and override
Hydrant pit valve assembly
Hydrant pit box
Stoneguard
Coupler poppet operator
Pit box seal
Hydrant riser
Standard hydrant coupler
Outlet adapter
Fuel sense
Deadman air
Lanyard attachment point
Pilot device and override
Hydrant pit valve assembly
Stoneguard
Coupler poppet operator
Hydrant pit box
Pit box seal
Hydrant riser
Figure 1 - Typical arrangement of hydrant pit equipment
(deadman and pressure regulating valve in coupler)
Figure 2 - Typical arrangement of hydrant pit equipment
(deadman and pressure regulation in pit valve)
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9
±0,127165,100
6,3
Sealin
surfacC
±0,127146,050
±0,1101,6
±0,127152,400
±0,127133,350
±0,1271,588
F
C BG
A
Fixed product selectionposts located as shownunnumbered 2 places
Movable product selection postslocated as shown; 4,763 mm indexnumerals shall be permanentlylocated
A minimum clearance of 134,62 mm between hydrant pit valvecenter and fuel sense/air reference adapter coupledwith mating socket. (Refer to Figure 5A for more details).
Fuel/air referenceadapter
Outer surfaceof matingfuel/air socket
212,725 dia.BSC
6
5
4
3
2
1
Sealinsurfac
Notes:
1.
BSC = basic dimension; min. = minimum; max. = mhex. = hexagonal; dia. = diameter.
All dimensions are in millimetres.
2. The breaking of all corners is required, not toexceed 3,175 millimetre radius.
3. The details of adapter body valve head and intshown in dashed lines are to be determined b
manufacturer.4. Pressure equalizing valve stem on valve head
extend beyond sealing surface.
5. Sealing surface must be machined to 1,6 micr
6. Couplers must be capable of mating with maxdimensions shown.
Pr(1/he
Refer to Figure 5Afor detail
40,5BSC
54BSC
40,5BSC
5 placesBSC
45
45
4
Figure 3A - API standard hydrant pit outlet adapter, SI measurements
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1 0
±0,0056,500
6,3
Sealin
surfacC
±0,0055,750
±0,04,00
±0,0056,000
±0,0055,250
±0,0050,062 5
F
C BG
A
Fixed product selectionposts located as shownunnumbered 2 places
Movable product selection postslocated as shown; 3/16 inch indexnumerals shall be permanentlylocated
Notes:
1. All dimensions are in inches.
BSC = basic dimension; min. = minimum; max. = mhex. = hexagonal; dia. = diameter.
2. The breaking of all corners is required, not toexceed 0,125 inch radius.
3. The details of adapter body valve head and inshown in dashed lines are to be determined by
manufacturer.4. Pressure equalizing valve stem on valve head
extend beyond sealing surface.
5. Sealing surface must be machined to 63 micro
6. Couplers must be capable of mating with maxdimensions shown.
A minimum clearance of 5,30 in. between hydrant pit valvecenter and fuel sense/air reference adapter coupledwith mating socket. (Refer to Figure 5B for more details).
Fuel / air referenceadapter
Refer to Figure 5Afor detail
Outer surfaceof matingfuel/air socket
8,375 dia.BSC
6
5
4
3
2
1
Sealin
surfac
40,5BSC
54BSC
40,5BSC
5 placesBSC
45
45
4
Figure 3B - API standard hydrant pit outlet adapter, customary measurements
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GENERAL ARRANGEMENTS AND FEATURES
11
C
C Valve min.
D
245,008
Valve max.
Coupler max.
D
G
MP
L
H
Seal surface - ref.
Outside of coupler
including bump ring
Coupler
Max.68,580
HValve
Min.69,850
2,032 max.Under pressure
Groove depth^
^ 1,651 min. At no pressure
250,088
0,508
2,032 min.Under pressure
Coupler min.
264,160
259,080
264,160
269,240
Notes: Dimensions are in millimetres;max. = maximum; min. = minimum; ref. = reference; hex. = hexagonal; dia. = diameter.
Pressureequalizing valvetop surface must notextend beyond sealingsurface
Coupler poppetmax. diameter 100,5
Product selectivity
set bolt (12,700 min.tall, 15,875 max.hex. or dia.)
1,52445,974
±57,150 min.
C
C Valve min.
D9,646
Valve max.
Coupler max.
D
G
MP
Pressureequalizing valvetop surface must notextend beyond sealing
L
H
Seal surface - ref.
Outside of coupler
including bump ring
Coupler
Max.2,700
HValve
Min.2,750
0,080 max.Under pressure
Groove depth^
^ 0,065min. At no pressure
9,846
0,020
0,080 min.Under pressure
Coupler min.
Coupler poppetmax. diameter 3,956
10,40
10,20
10,40
10,60
Notes: Dimensions are in inches; max. = maximum; min. = minimum; ref. = reference; hex. = hexagonal; dia. = diameter.
surface
0,0601,81
±2,25 min.
Product selectivityset bolt (1/2" min.tall, 5/8" max.hex. or dia.)
Figure 4A - Outlet adapter and coupler interface dimensions, SI measurements
Figure 4B - Outlet adapter and coupler interface dimensions, customary measurements
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
12
3.2.3 Coupling action
The coupling action shall be of the push type with
provision for locking without rotating the coupler body.On systems requiring product selection, rotation of the
coupler collar to mate with the appropriate hydrant pit
valve assembly product selection device is permitted.
The coupling range shall permit coupling to the outlet
adapter in any position around the hydrant pit valve
assembly, without interference with the hydrant pit
walls, apron surface, or components.
The hydrant coupler shall incorporate an interlock
system to prevent opening of the coupler’s poppet (and
thus the hydrant pit valve assembly poppet) before
being locked in position, and to prevent unlocking and
disconnecting before the coupler poppet is closed. Thehydrant coupler design shall prevent its ejection in the
event of outlet adapter sealing failure or non-closure of
the poppet with the pilot device in the open position.
3.2.4 Hydrant pit arrangement and mounting
Hydrant pit components should normally be designed
so that they can be installed and maintained in a pit that
has a minimum internal diameter of 460 mm (18 in.).
However, manufacturers should be aware that some old
pit boxes have a diameter as small as 300-330 mm (12-
13 in.) with 100 mm (4 in.), 75 mm (3 in.) or other special riser flanges and may wish to design their valves
to be accommodated in these small pit boxes (see
Annex B). Hydrant pit components may be installed in
a central or offset position within the pit; however, the
overall pit box size and component spacing shall permit
easy access for operation and maintenance. In the
design, allowance shall be made for the operation of
levers and switches within the pit using industrial type
gloves and without the need for special tools. The
arrangement of the pit equipment shall also allow for
unobstructed (non-fouling) lanyard operation.
Hydrant system riser pipe flanges shall be in
accordance with the latest edition of ASME B.16.5,
Class 300 pattern for 150 mm (6 in.) flanges and Class
150 for 100 mm (4 in.) flanges. All hydrant pit
equipment flanges shall also be in accordance with
ASME B.16.5 for assembly compatibility. This applies
for stoneguards, pilot-operated valves and the inlet side
of the hydrant pit valve assembly.
All components shall be as compact as practicable.
The overall height of the hydrant pit valve assembly,
measured from the face of the inlet flange to the top of
the outlet adapter, not including the dust cap, shall be:
(a) For valves with either a 100 mm (4 in.) or 150 mm
(6 in.) ASME Class 150 inlet flange:
290 mm to 415 mm (11,5 in. to 16,34 in.)
(b) For valves with a 150 mm (6 in.) ASME Class 300 pattern inlet flange:
406 mm to 415 mm (16 in. to 16,34 in.)
Manufacturers who offer a valve with dimensions
shorter than those above should be able to provide
spool pieces or adapters to accommodate any difference
in the dimensions of the riser flange and the inlet flange
of the valve and to bring their valve within the
dimensional range in (b) if requested.
Note: The dimensions quoted in (b) and the
provision for spools and adapters will ensure that valves
offered by different manufacturers are freelyinterchangeable.
The pit valve assembly shall be installed within the
pit box so that there is a clearance of not more than 100
mm (4 in.) and not less than 75 mm (3 in.) between the
hydrant pit valve assembly outlet adapter sealing
surface and the top of the hydrant pit box. This setting
is necessary to ensure that when a coupler is attached to
the pit valve, the underside of the elbow does not touch
the top of the pit box. When a hydrant coupler fitted
with a carriage assembly is attached to the hydrant pit
valve outlet adapter, the carriage assembly shall be
clear of the ground when in the folded up position.
3.2.5 Fuel sense and air reference lines
The pressure/flow control and/or excess flow control, if
fitted, shall be included either on the hydrant coupler or
on the hydrant pit valve assembly. However, as a
minimum, there shall be a deadman function installed
either on the hydrant pit valve or the hydrant coupler
upstream of the inlet hose or boom assembly.
Where fitted, these controls shall be provided with
air reference, and in the case of pressure/flow control
and/or excess flow control, fuel reference pressures, to
enable them to function. The connection of the lines to
provide such pressures may be permanent (in the case
of the hydrant coupler) or may be fitted to either the
hydrant pit valve assembly or hydrant coupler by means
of a quick coupling. Figures 3A and 3B, 4A and 4B,
and 5A and 5B provide the interface dimensions,
including product selectivity to ensure complete
interchangeability, where both fuel and air lines are
required. If used, this accommodation or any other such
device shall be located so that it will not interfere with
the operation of the other components.
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GENERAL ARRANGEMENTS AND FEATURES
13
An interlock feature capable of prohibiting accidental
un-coupling that is compatible with the design shown in
Figures 5A and 5B is desirable.
On air-operated pilot devices, an air reference
pressure line from the hydrant dispenser is required tocontrol the opening and closing of the hydrant pit valve.
This connection should be a "quick disconnect" type
connection. Any standard, through-flow connection
may be used. The self-sealing quick disconnect fitted to
the pilot device shall be of the leaky type to ensure that
no air is trapped within the pilot after disconnecting the
mating half from the hydrant dispenser air system.
3.2.6 Flow rate
3.2.6.1 Hydrant pit valve assembly
The hydrant pit valve assembly shall be designed inaccordance with the following rates:
(a) rated flow: 4 500 lpm (1 200 USGPM)
(b) catastrophic excess flow: 11 000 lpm (2 900
USGPM)
3.2.6.2 Hydrant couplers
Hydrant couplers shall be designed in accordance with
the following rates:
(a) for 4 in. inlet by 4 in. outlet (either pressure
controlled or standard coupler): 4 500 lpm (1 200USGPM)
(b) for 4 in. inlet by 3 in. outlet (either pressure
controlled or standard coupler): 3 000 lpm (800
USGPM)
3.2.7 Pressure rating
3.2.7.1 Hydrant pit valve assembly
The hydrant pit valve assembly shall be designed in
accordance with the following pressure ratings, all at
70 EC (158 EF):
(a) design pressure: 1 900 kPa (275 psi)
(b) operating pressure: -10 to 1 400 kPa (-1,5 to 200
psi)
(c) proof pressure: 2 850 kPa (415 psi) minimum
(d) burst pressure: 5 690 kPa (825 psi) minimum
3.2.7.2 Hydrant couplers
As the coupler shall be capable of being handled,
coupled and uncoupled by one operator, the
recommended weight of a coupler in all configurations
should be not more than 17 kg (37 lbs).
Hydrant couplers, either connected to a hydrant pit
valve assembly or disconnected and closed, shall be
designed in accordance with the following pressure
ratings, all at 70 ºC (158 ºF):
(a) design pressure: 1 900 kPa (275 psi)
(b) operating pressure: -10 to 1 400 kPa (-1,5 to 200
psi) minimum
(c) proof pressure:
(i) uncoupled, closed: 1 830 kPa (265 psi)
minimum
(ii) coupled, open: 2 850 kPa (415 psi) minimum
(d) burst pressure:
(i) uncoupled, closed: 2 740 kPa (400 psi)
minimum
(ii) coupled, open: 5 690 kPa (825 psi) minimum
3.2.8 Pilot device actuation
3.2.8.1 Manual operation
The pilot device shall have two separate actions for
opening and closing. The open or close force at
maximum operating pressure shall not exceed 110 N
(25 lbf). The close actuator shall have a fitting to allow
the attachment of a lanyard to achieve the closing
function from a remote distance. The fitting and the
lanyard shall not be able to foul on any hydrant pit
equipment and shall be effective at any angle or
direction of pull.
3.2.8.2 Air operation
The pilot device is operated by the application of an
externally supplied air pressure. Control air supply shall
be a minimum of 240 kPa (35 psi) to the pilot device to
control opening. The application of the air supply shall
be via a deadman type valve system on the hydrant
dispenser.
3.2.8.3 Lanyard connection
It shall be possible to connect a lanyard to an air-
operated pilot device to enable remote closing of the
pilot valve.
Note 1: The requirement in 3.2.8.3 applies to those
areas where legislation and/or safe practices require a
dual operation, for example, if it is envisaged that air
may fail to exhaust due to a system failure or restriction
resulting from a vehicle collision. It does not apply to
those areas where a lanyard has, traditionally, not been
used.
Note 2: See Annex D for a list of advantages in
using air-operated pilot devices.
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1 4
6,350min
2,286
Fuel pressure sense ports1,905 - 2,108 dia. hole, 6 placesequally spaced. All sharp edgesto be removed. Radial locationoptional.
Air reference pressure port1,905 - 2,108 dia. hole. All sharpedges to be removed. Radiallocation optional.
3,302 radius
1,524 radius
A1516
12,59812,548
dia.
43,05346,101
23,87625,400
9,52511,049
55,626dia.max.
20,828basic
1
8,331 basic
Wh3,1aboas anyas
14,046basic
AF
C B
4,674 - 4,826 dia. 8,89 deep
Notes: Dimensions are in millimetres; min. = minimum; dia. = diameter; max. = maximu
Figure 5A - API standard fuel sense and air reference lines accommodation for regulating type hydrant valves (valv
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1 5
0,25
min
0,090
Fuel pressure sense ports0,075 -0,083 dia. hole, 6 placesequally spaced. All sharp edgesto be removed. Radial locationoptional.
Air reference pressure port0,075 - 0,083 dia. hole. All sharpedges to be removed. Radiallocation optional.
0,13 radius
0,06 radius
A1516
0,4960,494
dia.
1,6951,815
0,9401,000
0,3750,435
2,190dia.
max.
0,820basic
0,328 basic
W0,abasanas
0,553basic
AF
C B
0,184 - 0,190 dia. 0.35 deep
Notes: Dimensions are in inches; min. = minimum; dia. = diameter; max. = maximum
Figure 5B - API standard fuel sense and air reference lines accommodation for regulating type hydrant valves (valve in
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
16
3.2.9 Operating temperature range
The hydrant components covered by this publication
shall meet all the design requirements within thetemperature range of !40 EC to +70 EC (!40 EF to
+158 EF).
3.2.10 Pilot-operated valve closing and opening
times
The requirements for opening and closing times are
those for carrying out acceptance and approval testing
on a test rig. Opening and closing of the pilot-operated
valve shall be even and progressive. The method of
testing is defined in 4.6.
Note: As the design of the hydrant dispenser control system may influence opening and closing
times, users should ensure that their systems will
achieve these opening and closing times in the field.
3.2.10.1 Closing time
Pilot-operated valve closure shall be caused by
actuation of the lanyard or air-operated pilot device.
The valve shall fully close from rated flow within 2 to
5 seconds measured from the time that the closing
mechanism is operated until flow ceases.
3.2.10.2 Opening timeThe pilot-operated valve assembly shall open from the
fully closed position in normal operation such that the
following flow conditions are satisfied. These
conditions shall apply for both manual or air pilot-
operated control:
(a) 90 % of rated flow shall be achieved in not less
than 5 seconds and no more than 20 seconds from
the time of activation of the opening mechanism.
(b) Full (100 %) of rated flow shall be achieved in not
more than 30 seconds measured as in (a).
3.2.11 Deadman control
There is a major difference in the practices observed in
some countries, such as the United States of America
(USA), and other locations, particularly in European
operations. For example, in the USA it is common
practice to have the deadman function provided by the
air-operated pilot device with an additional, in-line
control valve installed in the vehicle pipework. This
valve is outside the scope of this publication. Mainly,
European practice is to have the deadman control fitted
in the hydrant pit coupler with a lanyard operated pit
valve pilot device, although air-operated pilots are not
excluded.
Upon actuation, the deadman control shall open or
close a valve, either as a part of the hydrant pit valveassembly or hydrant coupler, or both. The deadman
valve performance characteristics shall comply with
3.2.10.1 and 3.2.10.2. If the deadman valve is in the
hydrant pit, the deadman valve shall be the pilot-
operated valve.
A deadman fitted in the hydrant coupler shall open
to full flow in not less than 5 seconds and close to no
flow in not less than 2 seconds nor more than 5
seconds. Overshoot shall not exceed 200 litres (53
USG) or 5 % of flow in areas where this limit applies.
Air supply shall meet the following requirements:
(a) For an air-operated deadman valve provided in the
hydrant coupler and hydrant pit valve assembly,
with the hydrant pit valve assembly equipped also
with a lanyard, a common air supply may be
provided.
(b) For a hydrant pit valve provided with an air-
operated deadman but no lanyard and with an air-
operated deadman provided in the hydrant coupler,
independent air supplies with no common
components shall be provided.
(c) For an air-operated deadman provided in the
hydrant pit valve, with no lanyard attachment and
no deadman in the hydrant coupler, a single air
supply is satisfactory.
3.2.12 Overshoot
Overshoot during closing of the pilot-operated valve
shall not exceed 200 litres (53 USG) at all flow rates up
to rated flow. Under catastrophic excess flow
conditions, as defined in 3.2.16, overshoot shall not
exceed 300 litres (80 USG). Note: In areas where a more stringent overrun limit
is imposed, that condition shall apply.
3.2.13 Pressure loss
3.2.13.1 Hydrant pit valve assembly
The pressure loss at rated flow, unless otherwise stated,
across a non-regulating hydrant pit valve assembly
without an intermediate strainer but with a stoneguard
in place, and assembled with a 4 in. straight hose unit
in accordance with API RP 1004, shall be as follows
from point A to B in Figure 6:
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GENERAL ARRANGEMENTS AND FEATURES
17
Test fluid tank
Straight pipe
Meter
100 mm (4 in.)or 150 mm (6 in.)pipe
1 m (3 ft)
1 m
100 mm
(4 in.) pipe
1 m (3 ft) min.
Pressuretest point A
Pressuretest point B
Pump
Z
X
Pit valve& coupler under testY
Alternate meter position
Note: m = metres; in. = inch; min. = minimum
(3 ft)
(a) for 150 mm (6 in.) inlet valve, with 100 mm (4 in.)
inlet by 100 mm (4 in.) outlet coupler - 135 kPa
(19,6 psi) maximum.
(b) for 100 mm (4 in.) inlet valve, with 100 mm (4 in.)
inlet by 100 mm (4 in.) outlet coupler - 165 kPa(24 psi) maximum.
(c) for 150 mm (6 in.) inlet valve, with 100 mm (4 in.)
inlet by 75 mm (3 in.) outlet coupler - 138 kPa (20
psi) maximum at 3 000 lpm (800 USGPM) flow.
(d) for 100 mm (4 in.) inlet valve, with 100 mm (4 in.)
inlet by 75 mm (3 in.) outlet coupler - 152 kPa (22
psi) maximum at 3 000 lpm (800 USGPM) flow.
3.2.13.2 Hydrant pit valve assembly with a standard
regulating 90E coupler
The pressure loss at rated flow across the hydrant pit
valve assembly without an intermediate strainer butwith a stoneguard in place and assembled with a
regulating 90E hydrant coupler (fully open) shall be as
follows from point A to B as defined in Figure 6:
(a) for 150 mm (6 in.) inlet valve, with 100 mm (4 in.)
inlet by 100 mm (4 in.) outlet coupler - 193 kPa
(28 psi) maximum.
(b) for 100 mm (4 in.) inlet valve, with 100 mm (4 in.)
inlet by 100 mm (4 in.) outlet coupler - 245 kPa
(35,5 psi) maximum.(c) for 150 mm (6 in.) inlet valve, with 100 mm (4 in.)
inlet by 75 mm (3 in.) outlet coupler - 145 kPa (21
psi) maximum at 3 000 lpm (800 USGPM).
(d) for 100 mm (4 in.) inlet valve, with 100 mm (4 in.)
inlet by 75 mm (3 in.) outlet coupler - 162 kPa
(23,5 psi) maximum at 3 000 lpm (800 USGPM).
3.2.14 Pilot-operated valve leakage
The allowed leakage downstream of a closed pilot-
operated valve, under maximum operating pressure,
shall be such that the 'well' (see Figures 4A and 4B,dimension M) formed on the top of the outlet adapter
poppet and the upper sealing surface shall not fill in less
than one minute with the pressure equalizing valve
depressed.
Figure 6 - Schematic of test rig to be used for pressure loss, opening and closing times and overshoot
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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3.2.15 Vacuum testing
During operation and/or maintenance of a hydrant
system, vacuum conditions may occur. The hydrant pit
valve assembly, with and without a hydrant coupler attached, shall be designed to withstand a -10 kPa (-1,5
psi) vacuum without admitting air or water into the
system. See 4.7 for test details.
3.2.16 Catastrophic excess flow
The lanyard or deadman control shall be designed to
cause the pilot-operated valve to close under all normal
and abnormal system excess flow rates up to and
including 11 000 lpm (2 900 USGPM). See 4.10 for test
details.
3.2.17 Materials of construction
All materials shall be chemically compatible with all
aviation turbine fuels. All metal parts in contact with
the fuel shall be free of zinc, cadmium, copper, and
their alloys; however, an aggregate amount of 3 %
maximum may be present as alloying elements. All
non-metal gaskets, O-rings, or other seals or elastomers
in contact with the fuel are to be made of materials
suitable for use with aviation turbine fuels containing
up to 30 % volume aromatics, 5 % volume olefins, and
3 % volume naphthalenes.All external surfaces shall be resistant to corrosion
caused by atmospheric exposure and water immersion.
Note: this could be achieved by using a corrosion
resistant material or by applying a suitable coating.
Care should be taken in the design of the equipment to
reduce failures caused by wear from the equipment
being dragged across the apron surface. Anticipated
vulnerable points should be protected by wear pads,
brackets or guards.
3.2.18 Serviceability
Maintenance requirements of the hydrant pit valve
assembly shall be minimal, but the hydrant pit valve
shall be designed such that all parts of the assembly,
except the pilot-operated valve portion, are removable
from the pit for maintenance or replacement of seals.
This should be possible without depressurising the
hydrant line. In addition, seals and sealing surfaces
should be protected from mechanical damage.
3.2.19 Decoupling spillage
Spillage shall be minimal when the coupler is
disconnected from the outlet adapter after aircraft
fuelling. The limit for spillage into the pit box is nomore than 30 ml (1 fluid ounce). See 4.11 for test
details.
3.2.20 Stoneguard
A stoneguard of robust construction and with an
opening equivalent to 6 mm (¼ in.) mesh, shall be
located upstream of the hydrant pit valve assembly.
The stoneguard may be a part of, or furnished as a
separate item to, the hydrant pit valve assembly. It shall
be designed and proved to withstand a flow rate of
11 000 lpm (2 900 USGPM) without becomingdislodged or deforming to a point where it would
become ineffective or would interfere with the closing
of the pilot-operated valve.
The stoneguard will not receive maintenance or
cleaning under normal operating conditions and should
be designed accordingly.
3.2.21 Wear gauges
Manufacturers shall provide, for their own hydrant
coupler and hydrant pit valve assembly equipment, a
simple wear gauge or gauges. The wear gauge(s) shall be suitable for accurate wear measurement on
operationally critical faces. It shall be possible to
routinely assess wear using the gauge(s) without
requiring equipment disassembly.
The wear gauges shall be permanently and legibly
marked to show to which piece of equipment they
apply. Manufacturers should define which parts and
accessories require to be checked with these gauges.
The results of the wear measurements shall indicate
whether closer inspection of individual components is
required. Manufacturers shall provide limits of wear
beyond which repair is required.
3.2.22 Pilot device override
The hydrant pit valve assembly shall include a manually
operated mechanism which, when actuated to the closed
position, will cause the pilot-operated valve to close and
remain closed until the pilot device override is opened.
The actuation of the pilot device override shall be easily
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GENERAL ARRANGEMENTS AND FEATURES
19
operable. Whilst the removal of the adapter and/or pilot
device when the hydrant is still under pressure is not
recommended, manufacturers shall demonstrate that
removal of these components is possible with hydrant
inlet pressure up to 1 380 kPa (200 psi). See 4.8 for testdetails.
Note: The purpose of the pilot device override is to
allow limited servicing of the outlet adapter and pilot
device sections of the hydrant pit valve assembly,
without the removal of the hydrant pit valve assembly
from the system or the depressurizing of the upstream
hydrant system.
3.2.23 Dust covers
Dust covers shall be provided to protect the outlet of the
hydrant pit valve assembly and the inlet of the hydrantcoupler from dust, rain, snow, or ice. In the case of the
hydrant coupler, the dust cover may be made a
permanent part of the hydrant dispenser.
3.3 OPTIONAL ITEMS
3.3.1 Reverse flow
Reverse flow through a hydrant pit valve assembly and
hydrant coupler assembly is not recommended. If a
manufacturer offers an option for reverse flowcapability, the maximum pressure drop from Point B to
Point A in Figure 6, for a reverse flow of 750 lpm (200
USGPM) shall be 105 kPa (15 psi).
3.3.2 Intermediate strainer
It is recommended that an intermediate strainer should
not be included in the hydrant pit valve, as debris
trapped by the strainer may, on termination of flow, fall
into the pilot-operated valve impairing its performance.
If a manufacturer offers this option, it should be
made of 10 or 20 mesh (2,5 or 1,25 mm) material and
shall be mounted such that it is easily removed for
cleaning. The strainer shall provide coverage of 100 %
of the flow path in which it is mounted.
3.3.3 Automatic excess flow control
If specified by the purchaser, the hydrant pit valve
assembly or hydrant coupler shall have a device, or
devices, that provides automatic excess flow control at
predetermined flow rates. The single position unit
should be adjustable over a flow range of from 3 200 to
4 500 lpm (845 to 1 200 USGPM). The dual position
unit should be adjustable within two flow ranges. When
set in low flow position, it shall cover a flow range
from 2 000 to 2 900 lpm (580 to 765 USGPM). When
set in the high flow position, the flow range shall befrom 3 200 to 4 500 lpm (845 to 1 200 USGPM).
3.3.4 Secondary breakaway features
A secondary means to prevent damage to the pilot-
operated valve housing, such as a frangible adapter or
a shear section, is permitted. This feature shall not
interfere with the ability of the pilot-operated valve
assembly to withstand the steady load force of 40 000
N (9 000 lbf) as required in 4.9.4.
3.3.5 Product selectivity
Product selectivity may be achieved either using the
pilot device (if pneumatic), or the hydrant coupler (or
both).
Outlet adapters and hydrant couplers may have
capability of up to six-product selectivity, via either a
pilot selectivity device of the type, or equivalent, shown
in Figures 3A and 3B and 5A and 5B, or by using
coupler selectivity. Coupler selectivity would involve
designing the hydrant coupler and outlet adapter to
mate uniquely for a particular grade of product only,
physically preventing connection of a hydrant coupler which services a different grade of product.
3.3.6 Pressure control (regulation)
If a pressure control (regulating) valve is located within
the hydrant coupler or hydrant pit valve assembly, it
shall be capable of being adjusted. For all hydrant
supply pressures up to the system design pressure, the
pressure-regulating valve shall, at any flowrate or inlet
pressure, maintain the corresponding control pressure
stable and repeatable within +/- 14 kPa (2 psi).
3.3.7 Other mechanical means of closing the
pilot-operated valve
Other mechanical means of causing the closure of the
pilot-operated valve, such as detecting the upward
movement of the outlet adapter poppet valve, may be
offered. Such a device is considered to be an additional
safety measure if the coupler is separated from the
hydrant pit valve assembly due to impact. Any such
device shall not interfere with the normal operation of
the hydrant pit valve assembly.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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21
4
PERFORMANCE CRITERIA AND
TESTING PROCEDURES
4.1 MECHANICAL STRENGTH
All components of the hydrant pit valve assembly
(including any adapters, spools and/or associated
fittings) and hydrant coupler shall be capable of
withstanding severe handling, strain and shocks from
external sources. Components shall maintain functionaland structural integrity when subjected to the forces
specified within this Section.
4.2 TEST FLUID
The test fluid shall be Jet A, Jet A-1 or hydrocarbons
with similar density and viscosity properties. Water
may be used for all tests except pressure loss, opening
and closing times, overshoot or pressure regulation/
deadman testing. Wide-Cut Jet fuel and aviation
gasoline shall not be used. Note: Manufacturers are encouraged to adopt
suitable safety procedures when carrying out testing.
4.3 DIMENSIONAL CHECKS
All dimensions of areas that mate the hydrant coupler,
inlet flange, and other envelope dimensions shall be
inspected and recorded against the requirements of
Section 3 to ensure full compatibility.
4.4 PROOF AND BURST PRESSURE
Components shall meet the requirements in 4.4.1 and
4.4.2.
4.4.1 Proof pressure
(a) The complete hydrant pit valve assembly, (coupler,
pilot-operated valve, and outlet adapter), all set to
the open position, shall withstand a hydrostatic test
pressure of 2 850 kPa (415 psi). The pressure shall
be applied to the inlet of the valve and held for 10
minutes, without causing leakage, distortion, or
breakage.
(b) With the outlet adapter poppet open or removed
and the pilot-operated valve set to the closed
position, the pilot-operated valve shall withstand a
hydrostatic test pressure of 2 850 kPa (415 psi),applied to the hydrant pit valve assembly inlet and
held for 10 minutes, without leakage, distortion, or
breakage. Following this test, the unit shall be fully
operational and used for other tests required in this
Section.
(c) The hydrant coupler shall be individually tested
with the coupler poppet closed. The valve shall
withstand a full body internal hydrostatic test
pressure of 1 830 kPa (265 psi), applied to the
coupler outlet and held for 10 minutes, without
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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leakage, distortion or breakage. The coupler shall
remain serviceable on completion of the test.
4.4.2 Burst pressure
The requirement of this test is to establish the minimum
pressure above which structural failure can occur.
(a) This test shall be conducted on the complete
hydrant pit valve/hydrant coupler assembly with
the poppets set to the open position. The assembly
shall be hydrostatically tested to 5 690 kPa (825
psi) minimum for 5 minutes without leakage or
breakage. Damage or distortion that makes the
valve non-operational is allowable.
(b) The hydrant coupler shall be tested, not coupled tothe pit valve outlet adapter and without a hose
connected, with the coupler poppet closed. The
valve shall withstand a full body internal
hydrostatic burst test pressure of 2 740 kPa (400
psi) held for 5 minutes without leakage or
breakage. Damage or distortion that makes the
coupler non-operational is allowable.
Components tested to (a) and (b) shall not be delivered
to users and should be limited to testing of prototype or
production valves that subsequently will be destroyed.
4.5 PRESSURE LOSS
The pressure loss tests require a test rig that is capable
of circulating a flow rate of 4 500 lpm (1 200 USGPM)
through the unit. The test rig shall be in accordance
with Figure 6. Pressure pickup points may be of a
multiple point type as recommended in SAE ARP
868A. The test specimen shall be mated to a straight
hose unit or to a standard 90º elbow hydrant coupler
with a 100 mm (4 in.) outlet as specified in 3.2.13. The
test unit and coupler may be placed on its side during
this test.
For 100 mm (4 in.) inlet by 75 mm (3 in.) outlet
hydrant couplers, the circulating flow rate shall be
3 000 lpm (800 USGPM) through the unit.
The density (or specific gravity), viscosity, (in
centistokes) and the temperature of the test fuel used
shall be reported with the results.
During the test, 100 mm (4 in.) hydrant pit valve
assemblies shall be tested with 100 mm (4 in.) inlet
pipework, and 150 mm (6 in.) units shall use 150 mm
(6 in.) inlet pipework. The valve configuration tested
shall be the same configuration as that used in service,
(e.g. if a 100 mm (4 in.) valve is used with a spool
assembly to meet the 150 mm (6 in.) valve requirement,
the valve shall be tested in both the 100 mm (4 in.) and
150 mm (6 in.) configurations.)The pressure loss (difference between test points A
and B in Figure 6) shall be recorded for flow rates from
375 to 4 500 lpm (100 to 1 200 USGPM) in
approximate increments of 375 lpm (100 USGPM). The
results shall be plotted on log-log graph paper to
illustrate the characteristics of the unit.
The resultant pressure drop shall meet the
requirements of 3.2.13.
4.6 OPENING AND CLOSING TIMES AND
OVERSHOOT
For the following tests, the unit under test shall be
mounted vertically in the test rig and tested under the
following conditions:
(a) 1 200 kPa (175 psi) at no flow and 1 000 kPa (150
psi) minimum at 4 500 lpm (1 200 USGPM); and
(b) 600 kPa (87 psi) at no flow with 500 kPa (72,5 psi)
minimum at 3 500 lpm (925 USGPM).
The valve shall be mated with a standard 90E elbow
coupler for these tests. The above flow and pressureconditions shall be controlled by use of a combination
of valves (labelled "X", "Y" or "Z" in Figure 6). The
valve under test shall be opened, either by use of the
manual or air-operated pilot valve. The inlet pressure,
flow rate, pilot actuation point, and opening time shall
be electronically monitored and recorded. Data shall be
recorded until full rated flow is achieved for at least 1
minute. Opening time, which shall be even and
progressive, shall be in accordance with 3.2.10.2.
The pilot device shall be actuated to signal the
valve to close. This point shall be recorded on a data
chart or data record. The data shall be recorded until the
flow through the valve has stopped. The closing time,
which shall be even and progressive, shall be in
accordance with 3.2.10.1.
Under no flow conditions, with the pilot device in
the open position, the pilot-operated valve shall move
to the closed position.
The test shall be repeated under conditions as in (b)
above.
The overshoot shall be measured during the closure
of the pilot-operated valve. The maximum overshoot
shall be 200 litres (53 USG) at both flow rates.
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PERFORMANCE CRITERIA AND TESTING PROCEDURES
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Legislation or local requirements may limit overshoot
to a maximum of 5 % of flow. See 3.2.12.
If the coupler used in the test is equipped with a
deadman function, the above tests shall also be
conducted using a hydrant pit valve assembly withouta control function. The deadman control shall be used
to start and stop the flow through the valve. This is
necessary to ensure that the pilot-operated valve cannot
influence the amount of overrun.
4.7 VACUUM TEST
A hydrant coupler shall not be fitted for the first of
these tests. With the hydrant pit valve assembly poppet
valve closed and the pilot operator closed, a vacuum of
-10 kPa (-1,5 psi) shall be applied to the inlet of the pitvalve. The poppet shall remain closed and not permit
leakage of air in the reverse direction.
The test shall be repeated with a coupler fitted to
the pit valve. The hydrant pit valve and coupler
assembly shall be installed in a vertical position, with
the outlet adapter poppet and coupler poppet open and
the coupler outlet plugged. A vacuum of -10 kPa (-1,5
psi) shall be applied to the inlet of the valve. The
assembly integrity shall not allow leakage of air in the
reverse direction.
4.8 PILOT DEVICE OVERRIDE TEST
The test unit shall be set up with the outlet adapter
poppet closed and not connected to a hydrant coupler.
The pilot-operated valve and the pilot device override
shall be in the open position. Using test fluid, the
maximum operating pressure shall be applied to the
inlet side of the hydrant pit valve assembly. Once the
pressure has stabilized, the pilot device override shall
be set to the closed position. Any residual pressure from
the outlet adapter section of the hydrant pit valve
assembly shall be released through the equalising valve,
taking care to contain any spillage. After the initial
surge, the flow through the equalising valve shall not
exceed that as in 3.2.14.
The integrity of the pilot device override shall be
demonstrated by performing the following tests:
(a) With the test pressure still applied, repeatedly
attempt to open the pilot-operated valve by means
of all available actuators. Confirm quantitatively
that the pressure downstream of the pilot-operated
valve does not change; then
(b) Demonstrate that the outlet adapter and pilot
device can be removed safely from, and replaced
onto, the hydrant pit valve assembly while the
pilot-operated valve is under test pressure.
4.9 EXTERNAL LOAD RESISTANCE AND
FAILURE MODE
The hydrant coupler assembly shall withstand the shock
loading typically experienced when falling onto the
concrete apron, and when run over by a vehicle. The pit
valve assembly shall withstand the pulling effect of a
fuelling vehicle being driven away with the coupler
attached and the shock of a vehicle impact of the
magnitude defined in 4.9.3.
The external load capacity or strength of components and the required mode of assembly failure
shall be demonstrated by conducting the tests in 4.9.1 to
4.9.4.
4.9.1 Hydrant coupler shock resistance test
The hydrant coupler and fuelling hose shall be
pressurised to 100 kPa (15 psi) during the test. The
coupler shall then be dropped on three different axes
from the test heights specified in (a) and (b) below on
to a concrete surface similar to that found on an airport
apron. During the tests, there shall be no cushioningeffect by the hose on the shock applied to the coupler.
(a) Drop the coupler from a height of 1 m (3 ft). The
coupler shall remain fully functional and usable
following the test.
(b) Drop the coupler from a height of 2 m (6 ft). The
coupler may be distorted but it shall hold design
pressure following this test.
4.9.2 Hydrant coupler run-over resistance test
When placed on a concrete surface similar to that found
on an airport apron, the hydrant coupler, either attached
to a hose, or plugged with a test adapter, and with an
internal pressure of 100 kPa (15 psi), shall be run over
twice under the conditions specified below.
(a) Minimum loading: Vehicle total axle weight shall
be 2 860 kg (6 300 lbs), equally distributed on
either side on dual wheels with a minimum rolling
diameter of 700 mm (28 in.); and
(b) Maximum vehicle speed; 3,2 kph (2,0 mph).
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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The coupler should remain in a serviceable condition
following this test.
Note: The above weight/force conditions are
intended to simulate a vehicle driving over the coupler
on the apron.
4.9.3 Hydrant coupler breakaway test
During this test, the hydrant pit valve assembly shall
not suffer structural damage that will allow leakage.
Testing shall be conducted to ensure that under impact
or excessive strain, the hydrant coupler will break away
as cleanly as possible from the pit valve outlet adapter.
Such breakaway shall occur prior to partial or complete
failure of any other system component and without
damaging or interfering with the hydrant pit valve
assembly and its fuel shut-down system. The resultingautomatic closure of the outlet adapter poppet shall
reduce to a minimum fuel spillage from the hydrant pit
valve assembly under all design pressures and flow
rates.
Note: Zero leakage cannot be guaranteed, as it is
possible that a small piece of debris may be caught
between the poppet and the adapter head.
The two series of tests, in 4.9.3.1 and 4.9.3.2 shall
be performed.
— Steady load test in which an external load or pull
imposed via the coupler hose simulates, for example, a fuelling vehicle drive-away and causes
breaking at a defined load range; and
— Impact load test in which an external load or
impact imposed directly on the hydrant coupler
simulates, for example, impact from a vehicle that
causes coupler breakaway.
Note: Users of equipment covered by this
publication should be aware of the potential for damage
to the hydrant risers following coupler impact. See
Annex C.
4.9.3.1 Steady load test
The test shall be conducted with the hydrant pit valve
assembly and the hydrant coupler under a pressure of
1 900 +/-100 kPa (275 +/-15 psi) and set up as in Figure
7. Both the hydrant pit valve assembly and hydrant
coupler poppets shall be open, the pilot-operated device
set to the open position and air bled from the coupler.
The test shall be carried out with the hydrant
coupler connected to the hydrant pit valve assembly.
A gradually increasing horizontal force shall be applied
to the centreline of the outlet of the coupler. The test
shall be performed in four 90E opposed directions.
Tests in fewer than four, but not less than two,
directions may be performed if symmetry can be
demonstrated. At least one of the tests shall be carriedout in a direction which, from visual and dimensional
analysis, would cause the weakest part to be stressed
the most.
No failure shall occur at any applied force up to
17 800 N (4 000 lbf). Separation and clean breakaway
shall occur at a force greater than 17 800 N (4 000 lbf)
and not greater than 22 240 N (5 000 lbf).
Note: Leakage from the coupler to pit valve adapter
seal may be experienced as the seal is being stressed.
4.9.3.2 Impact load test
The test shall be conducted with the hydrant pit valveassembly and the hydrant coupler at a flow rate, using
water as the test medium, which gives the equivalent
amount of energy as that given by using jet fuel at
4 000 lpm. A flow rate of 3 200 lpm (845 USGPM) is
suggested.
The test shall be carried out on a hydrant coupler
attached to the hydrant pit valve assembly.
An impact load sufficient to cause the hydrant
coupler to separate cleanly from the hydrant adapter
shall be applied. The load shall be applied at the
centreline of the outlet of the hydrant coupler in three
directions (excluding the outlet end) or in a minimum of two directions if symmetry can be shown.
One suggested method of conducting this test is to
use a loaded pendulum type test rig (see Figure 8). If
used, the end of the pendulum impacting the coupler
elbow shall consist of a 75 mm (3 in.) or 100 mm (4 in.)
horizontal solid carbon steel bar. The test rig pendulum
arm length, weight and swing angle shall be sufficient
to guarantee breakaway. A suggested test rig set-up is
to have a pendulum arm length of 1,5 m (60 in.), a
pendulum mass of 300 kg (660 lbs) with a swing angle
of 90E. The weight of the arm measured at the end may
be incrementally increased (or decreased) to suit, with
repeated pendulum swings until breakaway of the
coupler assembly is achieved.
The hydrant coupler shall separate cleanly from the
hydrant pit valve outlet adapter which shall close to
prevent further liquid discharge. The pit valve outlet
adapter and poppet should not suffer damage that will
allow liquid flow to continue.
Note: For the hydrant coupler to survive this test is
not a requirement of this publication: it may suffer
structural damage.
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PERFORMANCE CRITERIA AND TESTING PROCEDURES
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Test pressure
Fix point
100 mm (4 in.) API outlet adapter
Steady load force
Test rig riser flange
Hydrant Coupler or Load Test Adapter (according to test
requirements)
Hydrant pitvalve
assembly
Figure 7 - Steady load test set-up (hydrant couplers and pit valve assemblies)
4.9.4 Hydrant pit valve assembly - Steady load
test
A hydrant pit valve assembly, fitted with a suitable load
test assembly, not a hydrant coupler, shall be subjected
to a steady horizontal load. The load test assembly shall
be connected to the pit valve adapter in such a way that
it will not break away during the test when set up as in
Figure 7.
The horizontal load shall be applied via the load
test assembly that fully reflects a hydrant coupler in the
way that it applies the load to the hydrant pit valve
assembly. The force shall be applied at right angles to
the hydrant pit valve axis so that the maximum bending
moment component around the riser flange fixed point
is applied.
Considering the riser flange as a fixed point, the
hydrant pit valve assembly shall be designed to
withstand, without structural failure, a gradually
increasing steady horizontal load up to 40 000 N (9 000
lbf).
Note: Testing to failure beyond this point is not a
requirement of this publication.
The test shall be carried out in four 90E opposed
directions. Tests in less than four but not less than two
directions may be performed if symmetry can be
demonstrated. At least one of the tests shall be carried
out in a direction which, from visual and dimensional
analysis, would cause the weakest part to be stressed
the most. At the completion of the load tests, there shall
be no damage to, or failure of, any component of the
hydrant pit valve and associated fittings.
4.10 CATASTROPHIC EXCESS FLOW
The hydrant pit valve assembly, with the outlet adapter
poppet removed and the stoneguard installed, shall be
mounted in such a manner as to afford a safe condition
when the test is being run. Test fluid may be water and
the valve may be inverted over a receiving vessel.
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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Rigid, secure mounted 'A' frameor similar suitablesupporting structure
75 mm (3 in.) or 100 mm (4 in.) horizontal carbon
steel bar suggested pendulum mass 300 kg (660 lbs.)
Nominal ground level
Test rig r iser flange
Fix point
Hydrant pit valveþassembly
Open coupler
Pivot
c of
Coupler
L
1,5 m (60 in.)
Devices that may restrict the ability to achieve test flow
conditions shall be removed. The hydrant pit valve
assembly shall be subjected to a flow rate as specified
in 3.2.16 for a sufficient length of time to show that the
pilot-operated valve will close under these conditions.Inlet pressures, flow rate, overshoot, and closing times
shall be recorded during the tests. The overshoot shall
not exceed 300 litres (80 USG) or 6,5 % where
percentage of flow limits are imposed.
For further information see Annex A.
4.11 DECOUPLING SPILLAGE
The hydrant pit valve assembly shall be mounted
horizontally and filled with test fluid at 100 kPa (15
psi). The hydrant coupler shall be coupled to the
hydrant pit valve assembly, the coupler poppet cycled
open/close, and the hydrant coupler uncoupled from the
hydrant pit valve assembly no less than ten times. The
valve shall be repressurised before each open/close
cycle.The decoupling spillage shall be collected in a
container that is suitable for measuring the small
quantities allowed. The average decoupling spillage for
each cycle shall be no more than 30 millilitres (1 fluid
ounce).
4.12 PRESSURE, SURGE AND FLOW
CONTROL
Purchasers may require additional tests. These shall be
agreed between the manufacturer and the purchaser.
Figure 8 - Suggested impact load test rig
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5
TYPE APPROVAL TESTING AND
QUALITY ASSURANCE
5.1 QUALITY ASSURANCE
The manufacturer shall be able to demonstrate that the
equipment meets the requirements of the type approval
tests in Section 4 and that a satisfactory quality
assurance and inspection system is followed (e.g. API
Q1, ISO 9000, ISO 10012-1). Purchasers, at their discretion, may wish to satisfy themselves that the
manufacturer’s quality system is comparable to the
relevant ISO 9000 standard or equivalent National
standards.
5.2 APPROVAL TESTING
At the request of the purchaser , the
manufacturer/vendor shall supply copies of test reports
showing the results of the tests on a sample of
equipment meeting the requirements of this publication.All production models shall conform to the
requirements of this publication.
The test reports should include performance data
obtained by suitable instrumentation that will produce
traces of data (copies of which can be reproduced)
taken during opening, closing, and other appropriate
tests.
It is recommended that videotape - or other visually
reproducible media - of at least the tests conducted to
demonstrate compliance with 4.9 should be made
available to the purchaser upon request.
5.3 DOCUMENTATION AND INSTRUCTION
In addition to the data required in 5.2, the manufacturer
shall supply the purchaser with the following
information as a minimum:
— Instal lation, servicing and maintenance
instructions.
— Any precautions to be observed in using the
equipment to ensure safety to personnel. — Information regarding modifications that may
apply after the user has taken delivery of the
equipment. This may be in the form of bulletins
and notices issued to known purchasers/users.
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ANNEX A
CATASTROPHIC EXCESS FLOW
In 1988 doubts were raised about the ability of the then
current type of hydrant pit valve assembly to close at
excessive flow rates. Such flow rates could occur
following damage to the top end of the valve that
results in complete removal of the outlet poppet valve.
The concern was that the velocity and therefore the
pressure at the pick up point for fuel flow via the pilotdevice might inhibit the closing of the main valve.
The IP contracted Delft Hydraulics, Holland, to
perform high flow testing of the valves manufactured
by Avery Hardoll, J C Carter, Thiem-Whittaker and
Zenith, to determine if they would close under such
conditions when the lanyard was pulled. Due to safety
considerations it was agreed that the test medium
should be water.
A full report was issued by Delft Hydraulics in
January 1990 5 and an article summarising the test and
results was published 6.
The permitted operating pressure in this third
edition of API/IP 1584 has been raised to 1 380 kPa
(200 psi). Flows in excess of 11 000 lpm (2 900
USGPM) may therefore be experienced following
severe damage to the pit valve assembly. Further testing
is not considered necessary as the Delft trials showedthe valves close more quickly as flow increases. It
should suffice for manufacturers to show that this trend
exists rather than to reach a flow rate corresponding
with 1 380 kPa (200 psi) inlet pressure. However, this
is only applicable if manufacturers do not radically alter
their designs. If this does occur, the manufacturer will
be required to demonstrate that the design change will
not affect the ability of the valve to close under these
excess flow conditions.
5. The closure behaviour of hydrant pit valves (1990).
6. Sanderson, T.A. and Simpson, R.A., Excess flow testing of hydrant pit valves, Petroleum Review, May 1990.
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ANNEX B
HYDRANT PIT VALVE ASSEMBLIES IN
SMALL PIT BOXES
The preferred arrangement for new works and
extensions to existing works is to use 150 mm (6 in.)
riser flanges and a pit box of at least 460 mm (18 in.)
diameter. Older systems may still have pit boxes as
small as 300-330 mm (12-13 in.) in diameter, less depth
than current models and 100 mm (4 in.), 75 mm (3 in.)
or other special riser flanges. It is recognised that it isnot always practical to replace small pit boxes with
larger diameter ones.
To be installed in the small boxes, the pit valve
assembly has to be fitted with a 100 mm (4 in.) base
flange and be not longer than 305 mm (12 in.). Valves
that meet the performance requirements of this
publication can be used in the larger boxes with 150
mm (6 in.) riser flanges by using spool pieces.
When valves with a 100 mm (4 in.) base flange are
fitted to 75 mm (3 in.) riser flanges using an adapter,
the assembly should be fitted with steady bars to
stabilise the valve body against the inside of the box, to provide extra support when using equipment heavier
than before, and to withstand impact by a vehicle.
The arrangement of components is intended to
ensure safety in operation consistent with equipment
simplicity within the pit. It is unlikely that devices for
pressure control and deadman operation can be
accommodated in the pit.
The components to be installed within the pit are
similar to those for standard pit boxes.
A spool or adapter assembly to mate the pit valve
assembly inlet flange to the hydrant riser flange may be
required. The purchaser shall specify what riser flange
will be used.
When the valve is fitted in these pit boxes, there is
little clearance between the valve and the inside of the
box. It is essential therefore that:
(a) All external edges are properly radiused andotherwise prepared to minimise the risk of personal
injury when the valve is being installed or
removed.
(b) Where necessary, valve manufacturers supply
special tools to facilitate installation and
maintenance of the valve and in particular,
specially designed tools to make the base flange
nuts easily accessible.
Flanges used for attaching the valve assembly to
existing pit box components shall normally be designedwith a raised face. The purchaser shall specify
machining to flat face if required.
In order to maintain the widest application for
installation in existing systems it is recommended that
the basic valve height (excluding adapters/spool pieces
used) is no more than 305 mm (12 in.) although longer
valves will not be excluded.
Adapters and spool pieces may then be used to suit
individual installations if necessary.
Due to variations in ground levels and settlement,
different riser flanges and their eccentricity within the
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FOUR-INCH HYDRANT SYSTEM COMPONENTS AND ARRANGEMENTS
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pit and misalignment, the purchaser shall specify
installation details.
If, on the pilot device, an extension cable is used to
which the lanyard is attached, the cable should be of
such a length that the lanyard itself cannot becomesnagged on the pit valve components. It shall also be
easily replaceable when in situ.
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ANNEX C
HYDRANT RISER STRESS DURING
IMPACT OF THE HYDRANT PITVALVE/HYDRANT COUPLER
ASSEMBLY
POST IMPACT RECOMMENDATIONS
During the development of this publication the potential
for damage to hydrant risers during impact to hydrant
couplers was considered. The IP contracted Air BP to
co-ordinate a stress analysis study by Cranfield
Aerospace Limited, to determine the extent of this
perceived problem.
The results of the testing and analysis of results are
contained in IP Report Fuel hydrant riser pipe stress
analysis due to accidental impact loads.7
In summary it was shown that for a riser installed
and backfilled in the manner as that in the study, the
breakaway force specified in this publication is
satisfactory. It was established that the length of the
riser could be critical, and short risers (<0,4 m; 15,7 in.)
are more prone to damage. Medium risers (0,4 m - 1,5
m; 15,7 in. - 59 in.) length have highest pipe stress; 0,6
m to 0,8 m (23,6 in. - 31,5 in.) produces peak stress,
and long risers (>1,5 m; 59 in.) are least likely to be
damaged. Beyond 1,5 m (59 in.) the backfill support
does not change appreciably. The calculated stresses
were determined for impact at 76 cm (30 in.) and 94 cm
(37 in.) above the bottom of the hydrant pit valve
flange; i.e. impact at the centreline of a hydrant coupler
and impact at the top of the hydrant coupler. The 94 cm
(37 in.) impact produced higher stress than the 76 cm
(30 in.) impact.
Results obtained during testing, and the following
conclusions, are only valid for risers that are installed
and backfilled as in the study.
Conclusions
— The 22 240 N (5 000 lbf) maximum hydrant
coupler break-away load was found to be
acceptable.
— Foundation support increases with depth to 1,5 m
(59 in.).
— 94 cm (37 in.) impact is worse than 76 cm (30 in.)
— Short risers (<0,4 m; 15,7 in.) are most vulnerable
to base cracking.
— Medium risers (0,4 m - 1,5 m; 15,7 in. - 59 in.)
have highest pipe stress. Riser lengths 0,6 m -
0,8 m (23,6 in. - 31,5 in.) produce peak stress.
— Long risers (>1,5 m; 59 in.) are least likely to be
damaged.
— Fuel hydrant design specifications should include
a minimum depth for risers of 1,5 m (59 in.).
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Recommended post-impact actions
— Determine nature/scale of impact and likely
severity.
— Assess damage to hydrant coupler/pit valve/riser8
. — Determine fuel hydrant and riser construction
details.
— Determine design depth of hydrant main and nature
of riser (direct or spur).
— Carry out Non Destructive Testing if possible,
including a pressure test. If such a system is
installed, carry out a leak detection test.
— Excavate to expose riser to hydrant joint if
considered to be appropriate. If the riser is classed
as short (<0,4 m; 15,7 in.) then damage to the
riser/hydrant main joint is probable if impact was
severe.
7. Available in the IP Library, 61 New Cavendish Street, London, W1G 7AR, UK.
8. It is considered to be a mandatory requirement to remove the pit valve involved for thorough examination and test. Inspection
in situ is not sufficient.
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ANNEX D
AIR-OPERATED PILOT DEVICES
Air-operated pilot devices have certain advantages over
those that are manually operated. Some advantages are:
— The pilot-operated valve will fail close under
spring pressure in the case of an air line rupture.
Air line rupture may be caused for example by fire,
or impact from a vehicle on the hydrant coupler assembly.
— The pilot-operated valve will close if the deadman
device is not kept active.
— The pilot-operated valve can be more easily
opened and closed repeatedly at a remote distance
from the hydrant pit. This feature may be useful in
conditions where the fuelling operator is working
from an elevated platform at the aircraft fuel panel
controls.
— Air-operated pilot devices afford a dual closure.
When the air pressure is released, the pilot-
operated valve closes, and remains closed, and
removal of the hydrant coupler closes the adapter poppet. With a lanyard-operated pilot device,
unless the lanyard is pulled before removal of the
hydrant coupler, the pilot-operated valve is not
prevented from opening, thus a 'hot hydrant'.
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37
ANNEX E
THE INSPECTION AND TESTING OF
AIRPORT HYDRANT PIT VALVES
E.1 INTRODUCTION AND SCOPE
This Annex is intended to give guidance in developing
procedures for the inspection and testing of hydrant pit
valves in service. The guidance given in this Annex
supersedes that previously published by the IP in The
inspection and testing of airport hydrant pit valves,
which has been withdrawn.
The recommended procedures set out in this Annexcover static inspection and testing and dynamic testing
of hydrant pit valves when in service. In addition
normal hydrant pit cleaning should be carried out.
E.2 STATIC TESTING/INSPECTION -
ALL VALVES
E.2.1 Weekly
All valves should be inspected for integrity of the
operating mechanism. A checklist for each type of valve installed should be prepared by the hydrant
operating company at each location, and should
include:
(a) Visual examination of operating handle, lanyard
and air pilot connections;
(b) Inspection of hydrant pit box for cleanliness, water
and product;
(c) Presence and condition of dust cap and tether;
(d) Hydrant pit lid condition, seal, tether, pit number
and grade marking where applicable;
(e) Condition of jacking screws where fitted;
(f) Condition of pit lining;
(g) Ensuring valve and components are free from
product leaks.
E.2.2 Four weekly
Every fourth weekly inspection should include an
additional check to ensure that the operating mechanismis free, that the main valve is closed and that the main
seal is not leaking beyond an acceptable level. Again a
procedure to cover all types of valve installed at the
location should be developed by the hydrant operating
company taking into account the manufacturer’s
accepted leak rate.
The only method of determining the integrity of the
main valve seal in situ is to depress the pressure
equalising valve in the main poppet, or the poppet itself.
This generally results in a fuel spray, even if of small
volume. Therefore, for health and safety reasons, it is
recommenced that a device either to contain or deflectany fuel spray be fitted to the valve when carrying out
the test.
As an alternative to the above four weekly test,
some locations may find it beneficial to conduct a test
during refuelling. The test procedure would be to
initiate flow to the highest practical level for the
aircraft/pit valve and to pull the lanyard. The deadman
control should remain in the operating position and note
taken that flow ceases.
It is important to prevent a vacuum being created
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when carrying out the test in this manner. After flow
ceases and the test is completed, before re-opening the
pit valve, the deadman should be closed and all fuelling
valves in use at the time of the test left open.
This alternative method should be used with duecaution. If excessive hose evacuation leading to surge
pressures on re-opening is noted, then this type of
testing should not be used.
In addition, this type of test is not suitable if a
boost pump is in use on the hydrant dispenser and it
should not be carried out. The static test should be
carried out.
E.3 DYNAMIC TESTING
E.3.1 Without deadman control
If the hydrant pit valve is equipped for lanyard closing
only, and the inlet coupler used with it is not equipped
with a deadman function, testing should be carried out
QUARTERLY. The test may be carried out during
refuelling, preferably at the beginning of the operation,
or by using a servicing vehicle, at the discretion of local
management. The test is limited to closure time only
and the valve should close between 2 to 5 seconds from
the time that the lanyard is pulled.
The precautions regarding the creation of a
vacuum, noted above in four weekly testing, should beobserved if the test is carried out during refuelling.
The results of the test may be recorded in a simple
manner, e.g. a tick to denote satisfactory, or a cross to
denote unsatisfactory, operation. Any corrective action
should be documented.
E.3.2 With deadman control
If the hydrant pit valve OR the hydrant coupler used is
fitted with a deadman control then testing may be
carried out on a SIX MONTHLY schedule. Testing
may be carried out during refuelling, or by the use of a
servicing vehicle, at the discretion of local
management. The test procedure, recording and
reporting requirements are the same as those in E.3.1.
In both cases there is no requirement to measure
overrun.
Note: Valves which incorporate a butterfly or
flapper valve should not be tested under flow
conditions, only static testing/inspection should be
carried out. Such valves will not meet the requirements
of this Annex.
E.4 TESTING AFTER REPAIR OR
OVERHAUL
After repair or overhaul, the valve should be fully tested
to its manufacturing standard, preferably on a test rig,so that the fullest flow rate to which the valve will
operate in service may be achieved.
Not all valves will seal completely and an
acceptable rate of leak, in line with manufacturer’s data,
should be decided on. This is particularly relevant with
those valves that have a metal to metal seal.
Note: Valves that do not seal completely may not
meet the requirements of this publication.
At all locations an effective defect reporting and
remedial action procedure should be established and
maintained.
E.5 SUGGESTED METHODS OF
CONTAINING FUEL SPRAY
Devices may range from a simple "shoe" which is fitted
with a screw-down device to depress the equalising
valve and/or the main poppet and which slides on to the
valve adapter, to a "coupler", blanked and fitted with a
pressure gauge and bleed valve. The latter device would
indicate a leaking valve by a pressure increase within
the coupler whilst the former deflects any fuel flow into
the pit whence it may be recovered.As stated previously, each hydrant operator should
develop their own procedures for conducting the four
weekly test but the following are offered as suggestions.
If using a shoe:
(a) Wipe clean the top of the outlet adapter face and
poppet;
(b) Fit shoe;
(c) Depress equalising valve.
Note: If fuel fills the well in substantially less
than 1 minute, this will indicate a failure. If it is
apparent that the well will not fill there is no need
to wait the full minute.
If using a blanked hydrant coupler:
(a) Wipe clean the top of the outlet adapter face and
poppet then connect blank hydrant coupler to pit
valve;
(b) Open coupler poppet to open hydrant valve poppet;
(c) Operate pilot to set the main valve to open;
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ANNEX E
(d) Bleed blank coupler to fill it with fuel and expel
air;
(e) Operate pilot to close main valve;
(f) Open bleed valve to release pressure.
Note: Normally, a pass or fail result will beclearly observable and leak rate does not need to be
measured. For comparison: The allowed maximum
leak rate for a new valve is approximately
15 ml/min.