IPS-E-PR-750(1)
FOREWORD
The Iranian Petroleum Standards (IPS) reflect
the views of the Iranian Ministry of Petroleum
and are intended for use in the oil and gas
production facilities, oil refineries, chemical and
petrochemical plants, gas handling and
processing installations and other such facilities.
IPS is based on internationally acceptable
standards and includes selections from the items
stipulated in the referenced standards. They are
also supplemented by additional requirements
and/or modifications based on the experience
acquired by the Iranian Petroleum Industry and
the local market availability. The options which
are not specified in the text of the standards are
itemized in data sheet/s, so that, the user can
select his appropriate preferences therein.
The IPS standards are therefore expected to be
sufficiently flexible so that the users can adapt
these standards to their requirements. However,
they may not cover every requirement of each
project. For such cases, an addendum to IPS
Standard shall be prepared by the user which
elaborates the particular requirements of the
user. This addendum together with the relevant
IPS shall form the job specification for the
specific project or work.
The IPS is reviewed and up-dated approximately
every five years. Each standards are subject to
amendment or withdrawal, if required, thus the
latest edition of IPS shall be applicable
The users of IPS are therefore requested to send
their views and comments, including any
addendum prepared for particular cases to the
following address. These comments and
recommendations will be reviewed by the
relevant technical committee and in case of
approval will be incorporated in the next revision
of the standard.
Standards and Research department
No.19, Street14, North kheradmand
Karimkhan Avenue, Tehran, Iran .
Postal Code- 1585886851
Tel: 88810459-60 & 66153055
Fax: 88810462
Email: Standards@nioc.org
‫ﭘﻴﺶ ﮔﻔﺘﺎر‬
‫( ﻣﻨﻌﻜﺲ ﻛﻨﻨﺪه دﻳﺪﮔﺎﻫﻬﺎي‬IPS) ‫اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ اﻳﺮان‬
‫وزارت ﻧﻔﺖ اﻳﺮان اﺳﺖ و ﺑﺮاي اﺳﺘﻔﺎده در ﺗﺄﺳﻴﺴﺎت ﺗﻮﻟﻴﺪ‬
‫ واﺣﺪﻫﺎي ﺷﻴﻤﻴﺎﻳﻲ و‬،‫ ﭘﺎﻻﻳﺸﮕﺎﻫﻬﺎي ﻧﻔﺖ‬،‫ﻧﻔﺖ و ﮔﺎز‬
‫ ﺗﺄﺳﻴﺴﺎت اﻧﺘﻘﺎل و ﻓﺮاورش ﮔﺎز و ﺳﺎﻳﺮ ﺗﺄﺳﻴﺴﺎت‬،‫ﭘﺘﺮوﺷﻴﻤﻲ‬
.‫ﻣﺸﺎﺑﻪ ﺗﻬﻴﻪ ﺷﺪه اﺳﺖ‬
‫ ﺑﺮاﺳﺎس اﺳﺘﺎﻧﺪاردﻫﺎي ﻗﺎﺑﻞ ﻗﺒﻮل‬،‫اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ‬
‫ﺑﻴﻦاﻟﻤﻠﻠﻲ ﺗﻬﻴﻪ ﺷﺪه و ﺷﺎﻣﻞ ﮔﺰﻳﺪهﻫﺎﻳﻲ از اﺳﺘﺎﻧﺪاردﻫﺎي‬
‫ ﻫﻤﭽﻨﻴﻦ ﺑﺮاﺳﺎس ﺗﺠﺮﺑﻴﺎت‬.‫ﻣﺮﺟﻊ در ﻫﺮ ﻣﻮرد ﻣﻲﺑﺎﺷﺪ‬
‫ﺻﻨﻌﺖ ﻧﻔﺖ ﻛﺸﻮر و ﻗﺎﺑﻠﻴﺖ ﺗﺄﻣﻴﻦ ﻛﺎﻻ از ﺑﺎزار داﺧﻠﻲ و ﻧﻴﺰ‬
‫ ﻣﻮاردي ﺑﻄﻮر ﺗﻜﻤﻴﻠﻲ و ﻳﺎ اﺻﻼﺣﻲ در اﻳﻦ‬،‫ﺑﺮﺣﺴﺐ ﻧﻴﺎز‬
‫ ﻣﻮاردي از ﮔﺰﻳﻨﻪﻫﺎي ﻓﻨﻲ ﻛﻪ در‬.‫اﺳﺘﺎﻧﺪارد ﻟﺤﺎظ ﺷﺪه اﺳﺖ‬
‫ﻣﺘﻦ اﺳﺘﺎﻧﺪاردﻫﺎ آورده ﻧﺸﺪه اﺳﺖ در داده ﺑﺮگﻫﺎ ﺑﺼﻮرت‬
‫ﺷﻤﺎره ﮔﺬاري ﺷﺪه ﺑﺮاي اﺳﺘﻔﺎده ﻣﻨﺎﺳﺐ ﻛﺎرﺑﺮان آورده ﺷﺪه‬
.‫اﺳﺖ‬
‫ ﺑﺸﻜﻠﻲ ﻛﺎﻣﻼً اﻧﻌﻄﺎف ﭘﺬﻳﺮ ﺗﺪوﻳﻦ ﺷﺪه‬،‫اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ‬
.‫اﺳﺖ ﺗﺎ ﻛﺎرﺑﺮان ﺑﺘﻮاﻧﻨﺪ ﻧﻴﺎزﻫﺎي ﺧﻮد را ﺑﺎ آﻧﻬﺎ ﻣﻨﻄﺒﻖ ﻧﻤﺎﻳﻨﺪ‬
‫ﺑﺎ اﻳﻦ ﺣﺎل ﻣﻤﻜﻦ اﺳﺖ ﺗﻤﺎم ﻧﻴﺎزﻣﻨﺪيﻫﺎي ﭘﺮوژه ﻫﺎ را‬
‫ در اﻳﻦ ﮔﻮﻧﻪ ﻣﻮارد ﺑﺎﻳﺪ اﻟﺤﺎﻗﻴﻪاي ﻛﻪ ﻧﻴﺎزﻫﺎي‬.‫ﭘﻮﺷﺶ ﻧﺪﻫﻨﺪ‬
‫ اﻳﻦ‬.‫ﺧﺎص آﻧﻬﺎ را ﺗﺄﻣﻴﻦ ﻣﻲﻧﻤﺎﻳﺪ ﺗﻬﻴﻪ و ﭘﻴﻮﺳﺖ ﻧﻤﺎﻳﻨﺪ‬
‫ ﻣﺸﺨﺼﺎت ﻓﻨﻲ آن ﭘﺮوژه‬،‫اﻟﺤﺎﻗﻴﻪ ﻫﻤﺮاه ﺑﺎ اﺳﺘﺎﻧﺪارد ﻣﺮﺑﻮﻃﻪ‬
.‫و ﻳﺎ ﻛﺎر ﺧﺎص را ﺗﺸﻜﻴﻞ ﺧﻮاﻫﻨﺪ داد‬
‫اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ ﺗﻘﺮﻳﺒﺎً ﻫﺮ ﭘﻨﺞ ﺳﺎل ﻳﻜﺒﺎر ﻣﻮرد ﺑﺮرﺳﻲ‬
‫ در اﻳﻦ ﺑﺮرﺳﻲﻫﺎ ﻣﻤﻜﻦ اﺳﺖ‬.‫ﻗﺮار ﮔﺮﻓﺘﻪ و روزآﻣﺪ ﻣﻲﮔﺮدﻧﺪ‬
‫اﺳﺘﺎﻧﺪاردي ﺣﺬف و ﻳﺎ اﻟﺤﺎﻗﻴﻪاي ﺑﻪ آن اﺿﺎﻓﻪ ﺷﻮد و ﺑﻨﺎﺑﺮاﻳﻦ‬
.‫ﻫﻤﻮاره آﺧﺮﻳﻦ وﻳﺮاﻳﺶ آﻧﻬﺎ ﻣﻼك ﻋﻤﻞ ﻣﻲ ﺑﺎﺷﺪ‬
‫ درﺧﻮاﺳﺖ ﻣﻲﺷﻮد ﻧﻘﻄﻪ ﻧﻈﺮﻫﺎ و‬،‫از ﻛﺎرﺑﺮان اﺳﺘﺎﻧﺪارد‬
‫ﭘﻴﺸﻨﻬﺎدات اﺻﻼﺣﻲ و ﻳﺎ ﻫﺮﮔﻮﻧﻪ اﻟﺤﺎﻗﻴﻪاي ﻛﻪ ﺑﺮاي ﻣﻮارد‬
‫ ﻧﻈﺮات و‬.‫ ﺑﻪ ﻧﺸﺎﻧﻲ زﻳﺮ ارﺳﺎل ﻧﻤﺎﻳﻨﺪ‬،‫ﺧﺎص ﺗﻬﻴﻪ ﻧﻤﻮدهاﻧﺪ‬
‫ﭘﻴﺸﻨﻬﺎدات درﻳﺎﻓﺘﻲ در ﻛﻤﻴﺘﻪﻫﺎي ﻓﻨﻲ ﻣﺮﺑﻮﻃﻪ ﺑﺮرﺳﻲ و در‬
‫ﺻﻮرت ﺗﺼﻮﻳﺐ در ﺗﺠﺪﻳﺪ ﻧﻈﺮﻫﺎي ﺑﻌﺪي اﺳﺘﺎﻧﺪارد ﻣﻨﻌﻜﺲ‬
.‫ﺧﻮاﻫﺪ ﺷﺪ‬
‫ ﻛﻮﭼﻪ‬،‫ ﺧﺮدﻣﻨﺪ ﺷﻤﺎﻟﻲ‬،‫ ﺧﻴﺎﺑﺎن ﻛﺮﻳﻤﺨﺎن زﻧﺪ‬،‫ ﺗﻬﺮان‬،‫اﻳﺮان‬
19 ‫ ﺷﻤﺎره‬،‫ﭼﻬﺎردﻫﻢ‬
‫اداره ﺗﺤﻘﻴﻘﺎت و اﺳﺘﺎﻧﺪاردﻫﺎ‬
1585886851 : ‫ﻛﺪﭘﺴﺘﻲ‬
66153055 ‫ و‬88810459 - 60 : ‫ﺗﻠﻔﻦ‬
88810462 : ‫دور ﻧﮕﺎر‬
Standards@nioc.org
:‫ﭘﺴﺖ اﻟﻜﺘﺮوﻧﻴﻜﻲ‬
: ‫ﺗﻌﺎرﻳﻒ ﻋﻤﻮﻣﻲ‬
General Definitions:
Throughout this Standard
definitions shall apply.
the
following
Company :
Refers to one of the related and/or affiliated
companies of the Iranian Ministry of Petroleum
such as National Iranian Oil Company, National
Iranian
Gas
Company,
and
National
Petrochemical Company etc.
Purchaser :
Means the “Company" Where this standard is
part of direct purchase order by the “Company”,
and the “Contractor” where this Standard is a part
of documents.
Vendor And Supplier:
Refers to firm or person who will supply and/or
fabricate the equipment or material.
Contractor:
Refers to the persons, firm or company whose
tender has been accepted by the company.
Executor :
Executor is the party which carries out all or part
of construction and/or commissioning for the
project.
Inspector :
The Inspector referred to in this Standard is a
person/persons or a body appointed in writing by
the company for the inspection of fabrication and
installation work
Shall:
Is used where a provision is mandatory.
Should
Is used where a provision is advisory only.
Will:
Is normally used in connection with the action
by the “Company” rather than by a contractor,
supplier or vendor.
May:
Is used where a provision is completely
discretionary.
.‫در اﻳﻦ اﺳﺘﺎﻧﺪارد ﺗﻌﺎرﻳﻒ زﻳﺮ ﺑﻪ ﻛﺎر ﻣﻲ رود‬
: ‫ﺷﺮﻛﺖ‬
‫ﺑﻪ ﺷﺮﻛﺖ ﻫﺎي اﺻﻠﻲ و واﺑﺴﺘﻪ وزارت ﻧﻔﺖ ﻣﺜﻞ ﺷﺮﻛﺖ ﻣﻠﻲ‬
‫ ﺷﺮﻛﺖ ﻣﻠﻲ ﺻﻨﺎﻳﻊ‬،‫ ﺷﺮﻛﺖ ﻣﻠﻲ ﮔﺎز اﻳﺮان‬، ‫ﻧﻔﺖ اﻳﺮان‬
.‫ﭘﺘﺮوﺷﻴﻤﻲ و ﻏﻴﺮه اﻃﻼق ﻣﻴﺸﻮد‬
:‫ﺧﺮﻳﺪار‬
‫ﻳﻌﻨﻲ "ﺷﺮﻛﺘﻲ" ﻛﻪ اﻳﻦ اﺳﺘﺎﻧﺪارد ﺑﺨﺸﻲ از ﻣﺪارك ﺳﻔﺎرش‬
‫ﺧﺮﻳﺪ ﻣﺴﺘﻘﻴﻢ آن "ﺷﺮﻛﺖ" ﻣﻴﺒﺎﺷﺪ و ﻳﺎ "ﭘﻴﻤﺎﻧﻜﺎري" ﻛﻪ اﻳﻦ‬
. ‫اﺳﺘﺎﻧﺪارد ﺑﺨﺸﻲ از ﻣﺪارك ﻗﺮارداد آن اﺳﺖ‬
:‫ﻓﺮوﺷﻨﺪه و ﺗﺎﻣﻴﻦ ﻛﻨﻨﺪه‬
‫ﺑﻪ ﻣﻮﺳﺴﻪ و ﻳﺎ ﺷﺨﺼﻲ ﮔﻔﺘﻪ ﻣﻴﺸﻮد ﻛﻪ ﺗﺠﻬﻴﺰات و ﻛﺎﻻﻫﺎي‬
. ‫ﻣﻮرد ﻟﺰوم ﺻﻨﻌﺖ را ﺗﺎﻣﻴﻦ ﻣﻴﻨﻤﺎﻳﺪ‬
:‫ﭘﻴﻤﺎﻧﻜﺎر‬
‫ ﻣﻮﺳﺴﻪ وﻳﺎ ﺷﺮﻛﺘﻲ ﮔﻔﺘﻪ ﻣﻴﺸﻮد ﻛﻪ ﭘﻴﺸﻨﻬﺎدش‬، ‫ﺑﻪ ﺷﺨﺺ‬
.‫ﺑﺮاي ﻣﻨﺎﻗﺼﻪ وﻳﺎ ﻣﺰاﻳﺪه ﭘﺬﻳﺮﻓﺘﻪ ﺷﺪه اﺳﺖ‬
: ‫ﻣﺠﺮي‬
‫ﻣﺠﺮي ﺑﻪ ﮔﺮوﻫﻲ اﺗﻼق ﻣﻲ ﺷﻮد ﻛﻪ ﺗﻤﺎم ﻳﺎ ﻗﺴﻤﺘﻲ از‬
.‫ﻛﺎرﻫﺎي اﺟﺮاﻳﻲ و ﻳﺎ راه اﻧﺪازي ﭘﺮوژه را اﻧﺠﺎم دﻫﺪ‬
:‫ﺑﺎزرس‬
‫در اﻳﻦ اﺳﺘﺎﻧﺪارد ﺑﺎزرس ﺑﻪ ﻓﺮد ﻳﺎ ﮔﺮوﻫﻲ اﺗﻼق ﻣﻲ ﺷﻮد ﻛﻪ‬
‫ﻛﺘﺒﺎً ﺗﻮﺳﻂ ﻛﺎرﻓﺮﻣﺎ ﺑﺮاي ﺑﺎزرﺳﻲ ﺳﺎﺧﺖ و ﻧﺼﺐ ﺗﺠﻬﻴﺰات‬
.‫ﻣﻌﺮﻓﻲ ﺷﺪه ﺑﺎﺷﺪ‬
:‫ﺑﺎﻳﺪ‬
.‫ﺑﺮاي ﻛﺎري ﻛﻪ اﻧﺠﺎم آن اﺟﺒﺎري اﺳﺖ اﺳﺘﻔﺎده ﻣﻴﺸﻮد‬
:‫ﺗﻮﺻﻴﻪ‬
.‫ﺑﺮاي ﻛﺎري ﻛﻪ ﺿﺮورت اﻧﺠﺎم آن ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد‬
:‫ﺗﺮﺟﻴﺢ‬
‫ﻣﻌﻤﻮﻻً در ﺟﺎﻳﻲ اﺳﺘﻔﺎده ﻣﻲﺷﻮد ﻛﻪ اﻧﺠﺎم آن ﻛﺎر ﺑﺮاﺳﺎس‬
.‫ﻧﻈﺎرت "ﺷﺮﻛﺖ" ﺑﺎﺷﺪ‬
: ‫ﻣﻤﻜﻦ اﺳﺖ‬
. ‫ﺑﺮاي ﻛﺎري ﻛﻪ اﻧﺠﺎم آن اﺧﺘﻴﺎري ﻣﻴﺒﺎﺷﺪ‬
IPS-E-PR-750(1)
ENGINEERING STANDARD
FOR
PROCESS DESIGN OF COMPRESSORS
FIRST REVISION
FEBRUARY 2010
‫اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ‬
‫ﺑﺮاي‬
‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
‫وﻳﺮاﻳﺶ اول‬
1388 ‫ﺑﻬﻤﻦ‬
This Standard is the property of Iranian Ministry of Petroleum.
All rights are reserved to the owner. Neither whole nor any
part of this document may be disclosed to any third party,
reproduced, stored in any retrieval system or transmitted in
any form or by any means without the prior written consent of
the Iranian Ministry of Petroleum.
‫ ﺗﻤﺎم ﺣﻘﻮق آن ﻣﺘﻌﻠﻖ ﺑﻪ‬.‫اﻳﻦ اﺳﺘﺎﻧﺪارد ﻣﺘﻌﻠﻖ ﺑﻪ وزارت ﻧﻔﺖ اﻳﺮان اﺳﺖ‬
‫ ﺗﻤﺎم ﻳﺎ‬،‫ﻣﺎﻟﻚ آن ﺑﻮده و ﻧﺒﺎﻳﺪ ﺑﺪون رﺿﺎﻳﺖ ﻛﺘﺒﻲ وزارت ﻧﻔﺖ اﻳﺮان‬
‫ ذﺧﻴﺮه‬،‫ ﺑﻪ ﻫﺮ ﺷﻜﻞ ﻳﺎ وﺳﻴﻠﻪ ازﺟﻤﻠﻪ ﺗﻜﺜﻴﺮ‬، ‫ﺑﺨﺸﻲ از اﻳﻦ اﺳﺘﺎﻧﺪارد‬
.‫ ﻳﺎ روش دﻳﮕﺮي در اﺧﺘﻴﺎر اﻓﺮاد ﺛﺎﻟﺚ ﻗﺮار ﮔﻴﺮد‬،‫ اﻧﺘﻘﺎل‬،‫ﺳﺎزي‬
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
Page
No.
CONTENTS:
:‫ﻓﻬﺮﺳﺖ ﻣﻄﺎﻟﺐ‬
0. INTRODUCTION ............................................. 3
3 ............................................................. ‫ ﻣﻘﺪﻣﻪ‬-0
1. SCOPE................................................................ 4
4 ..................................................... ‫ داﻣﻨﻪ ﻛﺎرﺑﺮد‬-1
2. REFERENCES .................................................. 4
4 ............................................................. ‫ ﻣﺮاﺟﻊ‬-2
3. DEFINITIONS AND TERMINOLOGY......... 6
6 ............................................... ‫ ﺗﻌﺎرﻳﻒ و واژﮔﺎن‬-3
4. SYMBOLS AND ABBREVIATIONS ............. 7
7 .......................................... ‫ ﻧﺸﺎﻧﻪ ﻫﺎ و اﺧﺘﺼﺎرات‬-4
5. UNITS................................................................. 8
8 ........................................................... ‫ واﺣﺪﻫﺎ‬-5
6. GENERAL ......................................................... 8
8 ............................................................ ‫ ﻋﻤﻮﻣﻲ‬-6
6.1 Type Selection Criteria ............................... 9
9 ................................... ‫ ﻣﻌﻴﺎرﻫﺎي اﻧﺘﺨﺎب ﻧﻮع‬1-6
6.2 Atmospheric Pressure................................. 11
11 ................................................. ‫ ﻓﺸﺎر ﺟﻮي‬2-6
6.3 Specification Sheets..................................... 11
11 .................................... ‫ ﺑﺮﮔﻪ ﻫﺎي ﻣﺸﺨﺼﺎت‬3-6
7. CENTRIFUGAL COMPRESSORS ................ 11
11 ..................................‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬-7
7.1 General .................................................... 11
11 ...................................................... ‫ ﻋﻤﻮﻣﻲ‬1-7
7.2 Design Criteria ............................................ 12
12 .............................................. ‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-7
8. AXIAL COMPRESSORS................................. 27
27 ........................................ ‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري‬-8
8.1 General .................................................... 27
27 ...................................................... ‫ ﻋﻤﻮﻣﻲ‬1-8
8.2 Design Criteria ............................................ 28
28 ..............................................‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-8
9. RECIPROCATING COMPRESSORS ........... 29
29 .............................. ‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬-9
9.1 General .................................................... 29
29 ...................................................... ‫ ﻋﻤﻮﻣﻲ‬1-9
9.2 Design Criteria ............................................ 30
30 .............................................. ‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-9
1
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
10. ROTARY COMPRESSORS .......................... 43
43 .........................................‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ‬-10
10.1 General................................................... 43
43 ..................................................... ‫ ﻋﻤﻮﻣﻲ‬1-10
10.2 Design Criteria .......................................... 44
44 ........................................ ‫ ﻣﻌﻴﺎرﻫﺎي ﻃﺮاﺣﻲ‬2-10
APPENDICES:
:‫ﭘﻴﻮﺳﺘﻬﺎ‬
APPENDIX A ........................................................ 48
48 ........................................................... ‫ﭘﻴﻮﺳﺖ اﻟﻒ‬
APPENDIX B......................................................... 54
54 ............................................................. ‫ﭘﻴﻮﺳﺖ ب‬
APPENDIX C TYPICAL COMPRESSORS
FIGURES ..................................... 58
58 ...................... ‫ﭘﻴﻮﺳﺖ ج ﻧﻤﻮﻧﻪ ﺷﻜﻞ ﻫﺎي ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
2
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
0. INTRODUCTION
‫ ﻣﻘﺪﻣﻪ‬-0
"Process
Design
of
Pressure
Reducing/Increasing Machineries and or
Equipment" are broad and contain various
subjects of paramount importance. Therefore a
group of process engineering standards are
prepared to cover the subject.
‫"ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﺗﺠﻬﻴﺰات و ﻳﺎ ﻣﺎﺷﻴﻦ آﻻت‬
‫ﻛﺎﻫﺶ دﻫﻨﺪه ﻓﺸﺎر " ﮔﺴﺘﺮده و ﺷﺎﻣﻞ ﻣﻮﺿﻮﻋﺎت‬/‫اﻓﺰاﻳﺶ‬
‫ ﺑﻨﺎﺑﺮاﻳﻦ ﻣﺠﻤﻮﻋﻪاي از‬.‫ﻣﺨﺘﻠﻒ ﺑﺎ اﻫﻤﻴﺖ ﺑﺎﻻ ﻣﻴﺒﺎﺷﺪ‬
‫اﺳﺘﺎﻧﺪاردﻫﺎي ﻣﻬﻨﺪﺳﻲ ﺑﺮاي ﭘﻮﺷﺶ اﻳﻦ ﻣﻮﺿﻮع ﺗﻬﻴﻪ‬
.‫ﺷﺪهاﻧﺪ‬
This group includes the following standards:
:‫اﻳﻦ ﻣﺠﻤﻮﻋﻪ ﺷﺎﻣﻞ اﺳﺘﺎﻧﺪاردﻫﺎي زﻳﺮ ﻣﻲ ﺑﺎﺷﺪ‬
Standard Code Standard Title
‫ﻋﻨﻮان اﺳﺘﺎﻧﺪارد‬
‫ﺷﻤﺎره اﺳﺘﺎﻧﺪارد‬
IPS-E-PR-330 " Engineering Standard for
Process
Design
of
Production & Distribution
Compressed Air Systems"
‫ "اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺑﺮاي‬IPS-E-PR-330
‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﺳﺎﻣﺎﻧﻪﻫﺎي‬
"‫ﺗﻮﻟﻴﺪ و ﺗﻮزﻳﻊ ﻫﻮاي ﻓﺸﺮده‬
IPS-E-PR-745 " Engineering Standard for
Process Design of Vacuum
Equipment
(Vacuum
Pumps and Steam Jet
Ejectors)"
‫ "اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺑﺮاي‬IPS-E-PR-745
‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﺗﺠﻬﻴﺰات‬
‫ﺧﻼء )ﺗﻠﻤﺒﻪﻫﺎي ﺧﻼء و ﻣﻜﻨﺪه‬
"(‫ﺟﺖ ﺑﺨﺎر‬
IPS-E-PR-750 " Engineering Standard for
Process
Design
of
Compressors"
‫ "اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺑﺮاي‬IPS-E-PR-750
"‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
IPS-E-PR-755 " Engineering Standard for
Process Design of Fans
and Blowers"
‫ "اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺑﺮاي‬IPS-E-PR-755
‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي دﻣﻨﺪهﻫﺎ و‬
"‫ﺑﺎدزن ﻫﺎ‬
This Engineering
covers:
Standard
Specification
:‫اﻳﻦ ﻣﺸﺨﺼﺎت اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ‬
"‫"ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
"PROCESS DESIGN OF COMPRESSORS"
.‫را ﭘﻮﺷﺶ ﻣﻴﺪﻫﺪ‬
3
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
1. SCOPE
‫ داﻣﻨﻪ ﻛﺎرﺑﺮد‬-1
This Engineering Standard Specification covers
the minimum requirements, basic reference
data and necessary formulas for process
calculations
and
proper
selection
of
compressors to be used in the OGP industries.
،‫اﻳﻦ ﻣﺸﺨﺼﺎت اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺣﺎوي ﺣﺪاﻗﻞ اﻟﺰاﻣﺎت‬
‫دادهﻫﺎي ﻣﺮﺟﻊ ﭘﺎﻳﻪ و ﻣﻌﺎدﻻت ﻻزم ﺑﺮاي ﻣﺤﺎﺳﺒﺎت‬
‫ﻓﺮآﻳﻨﺪي و اﻧﺘﺨﺎب ﻣﻨﺎﺳﺐ ﻛﻤﭙﺮﺳﻮرﻫﺎﻳﻲ اﺳﺖ ﻛﻪ در‬
.‫ ﮔﺎز و ﭘﺘﺮوﺷﻴﻤﻲ اﺳﺘﻔﺎده ﻣﻴﺸﻮد‬،‫ﺻﻨﺎﻳﻊ ﻧﻔﺖ‬
Compressors are dealt within four groups;
axial, centrifugal, reciprocating and rotary, and
each covered in separate section.
‫ﻛﻤﭙﺮﺳﻮرﻫﺎ در ﭼﻬﺎر ﮔﺮوه ﻣﻮرد ﺑﺮرﺳﻲ ﻗﺮار ﻣﻲ ﮔﻴﺮﻧﺪ؛‬
‫ رﻓﺖ و ﺑﺮﮔﺸﺘﻲ و دوراﻧﻲ ﻛﻪ‬،‫ ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬،‫ﻣﺤﻮري‬
.‫ﻫﺮﻛﺪام در ﺑﺨﺶ ﺟﺪاﮔﺎﻧﻪ ﺑﺮرﺳﻲ ﺷﺪهاﻧﺪ‬
:1 ‫ﻳﺎدآوري‬
Note 1:
‫ ﺗﻮﺳﻂ ﻛﻤﻴﺘﻪ ﻓﻨﻲ‬1384 ‫اﻳﻦ اﺳﺘﺎﻧﺪارد در ﺑﻬﻤﻦ ﻣﺎه ﺳﺎل‬
‫ﻣﺮﺑﻮﻃﻪ ﺑﺮرﺳﻲ و ﻣﻮارد ﺗﺄﻳﻴﺪ ﺷﺪه ﺑﻪ ﻋﻨﻮان اﺻﻼﺣﻴﻪ‬
.‫ اﺑﻼغ ﮔﺮدﻳﺪ‬257 ‫ ﻃﻲ ﺑﺨﺸﻨﺎﻣﻪ ﺷﻤﺎره‬1 ‫ﺷﻤﺎره‬
This standard specification is reviewed and
updated by the relevant technical committee on
Feb 2005, as amendment No. 1 by circular No.
257.
:2 ‫ﻳﺎدآوري‬
Note 2:
‫اﻳﻦ اﺳﺘﺎﻧﺪارد دو زﺑﺎﻧﻪ ﻧﺴﺨﻪ ﺑﺎزﻧﮕﺮي ﺷﺪه اﺳﺘﺎﻧﺪارد‬
‫ ﺗﻮﺳﻂ ﻛﻤﻴﺘﻪ ﻓﻨﻲ‬1388 ‫ﻣﻲﺑﺎﺷﺪ ﻛﻪ در ﺑﻬﻤﻦ ﻣﺎه ﺳﺎل‬
‫ از اﻳﻦ‬.‫( اراﻳﻪ ﻣﻲﮔﺮدد‬1) ‫ﻣﺮﺑﻮﻃﻪ اﻧﺠﺎم و ﺑﻪ ﻋﻨﻮان وﻳﺮاﻳﺶ‬
.‫( اﻳﻦ اﺳﺘﺎﻧﺪارد ﻣﻨﺴﻮخ ﻣﻲﺑﺎﺷﺪ‬0) ‫ﭘﺲ وﻳﺮاﻳﺶ‬
This bilingual standard is a revised version of
the standard specification by the relevant
technical committee on Feb 2010, which is
issued as revision (1). Revision (0) of the said
standard specification is withdrawn.
:3 ‫ﻳﺎدآوري‬
Note 3:
‫ ﻣﺘﻦ‬،‫در ﺻﻮرت اﺧﺘﻼف ﺑﻴﻦ ﻣﺘﻦ ﻓﺎرﺳﻲ و اﻧﮕﻠﻴﺴﻲ‬
.‫اﻧﮕﻠﻴﺴﻲ ﻣﻼك ﻣﻲﺑﺎﺷﺪ‬
In case of conflict between Farsi and English
languages, English language shall govern.
2. REFERENCES
‫ ﻣﺮاﺟﻊ‬-2
‫در اﻳﻦ اﺳﺘﺎﻧﺪارد ﺑﻪ آﻳﻴﻦ ﻧﺎﻣﻪﻫﺎ و اﺳﺘﺎﻧﺪاردﻫﺎي ﺗﺎرﻳﺦ دار‬
‫ ﺗﺎ ﺣﺪي ﻛﻪ‬،‫ اﻳﻦ ﻣﺮاﺟﻊ‬.‫و ﺑﺪون ﺗﺎرﻳﺦ زﻳﺮ اﺷﺎره ﺷﺪه اﺳﺖ‬
‫ ﺑﺨﺸﻲ از‬،‫در اﻳﻦ اﺳﺘﺎﻧﺪارد ﻣﻮرد اﺳﺘﻔﺎده ﻗﺮار ﮔﺮﻓﺘﻪاﻧﺪ‬
،‫ در ﻣﺮاﺟﻊ ﺗﺎرﻳﺦ دار‬.‫اﻳﻦ اﺳﺘﺎﻧﺪارد ﻣﺤﺴﻮب ﻣﻲﺷﻮﻧﺪ‬
‫وﻳﺮاﻳﺶ ﮔﻔﺘﻪ ﺷﺪه ﻣﻼك ﺑﻮده و ﺗﻐﻴﻴﺮاﺗﻲ ﻛﻪ ﺑﻌﺪ از ﺗﺎرﻳﺦ‬
‫ ﭘﺲ از ﺗﻮاﻓﻖ ﺑﻴﻦ ﻛﺎرﻓﺮﻣﺎ‬،‫وﻳﺮاﻳﺶ در آﻧﻬﺎ داده ﺷﺪه اﺳﺖ‬
،‫ در ﻣﺮاﺟﻊ ﺑﺪون ﺗﺎرﻳﺦ‬.‫و ﻓﺮوﺷﻨﺪه ﻗﺎﺑﻞ اﺟﺮا ﻣﻲﺑﺎﺷﺪ‬
‫آﺧﺮﻳﻦ وﻳﺮاﻳﺶ آﻧﻬﺎ ﺑﻪ اﻧﻀﻤﺎم ﻛﻠﻴﻪ اﺻﻼﺣﺎت و‬
.‫ﭘﻴﻮﺳﺖﻫﺎي آن ﻣﻼك ﻋﻤﻞ ﻣﻲﺑﺎﺷﻨﺪ‬
Throughout this Standard the following dated
and undated standards/codes are referred to.
These referenced documents shall, to the extent
specified herein, form a part of this standard.
For dated references, the edition cited applies.
The applicability of changes in dated references
that occur after the cited date shall be mutually
agreed upon by the Company and the Vendor.
For undated references, the latest edition of the
referenced
documents
(including
any
supplements and amendments) applies.
API
(AMERICAN
INSTITUTE)
API Std. 614
(‫ )ﻣﻮﺳﺴﻪ ﻧﻔﺖ آﻣﺮﻳﻜﺎ‬API
PETROLEUM
"Lubrication, Shaft-Sealing,
and Control-Oil Systems and
Auxiliaries" 5th. Ed
‫ ﻧﺸﺖ ﺑﻨﺪي‬،‫ " ﺳﺎﻣﺎﻧﻪ ﻫﺎي رواﻧﻜﺎري‬API Std. 614
"‫ﻣﺤﻮر و ﻛﻨﺘﺮل روﻏﻦ و ﻟﻮازم ﺟﺎﻧﺒﻲ‬
‫وﻳﺮاﻳﺶ ﭘﻨﺠﻢ‬
‫ "ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري و ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬API Std. 617
API Std. 617, "Axial
&
Centrifugal
Compressors & Expander
4
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
Compressors for Petroleum,
Chemical and Gas Industry
Services" 7th Ed., July 2002
‫و ﻛﻤﭙﺮﺳﻮرﻫﺎي اﻟﺤﺎﻗﻲ ﺑﻪ ﺗﻮرﺑﻴﻦ‬
،‫اﻧﺒﺴﺎﻃﻲ ﺑﺮاي ﻛﺎرﺑﺮي در ﺻﻨﺎﻳﻊ ﻧﻔﺖ‬
‫ﺷﻴﻤﻴﺎﻳﻲ و ﮔﺎز "وﻳﺮاﻳﺶ ﻫﻔﺘﻢ ﺟﻮﻻي‬
2002
API Std. 618, "Reciprocating Compressors
for Petroleum, Chemical and
Gas Industry Services" 4th
Ed. 1995
‫ "ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺮاي‬API Std. 618
‫ ﺷﻴﻤﻴﺎﻳﻲ و‬،‫ﻛﺎرﺑﺮي در ﺻﻨﺎﻳﻊ ﻧﻔﺖ‬
1995 ‫ﮔﺎز" وﻳﺮاﻳﺶ ﭼﻬﺎرم‬
API Std. 619,
‫"ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ‬
،‫ﻧﻮع دوراﻧﻲ ﺑﺮاي ﺻﻨﺎﻳﻊ ﻧﻔﺖ‬
"‫ﭘﺘﺮوﺷﻴﻤﻲ و ﮔﺎز ﻃﺒﻴﻌﻲ‬
1997 ‫وﻳﺮاﻳﺶ ﺳﻮم‬
"Rotary-Type
PositiveDisplacement Compressors
for
Petroleum,
Petrochemical, and Natural
Gas Industries” 3rd Ed.
1997
‫ "ﺗﺒﺪﻳﻞ واﺣﺪﻫﺎي اﻧﺪازه ﮔﻴﺮي‬API Publication
‫ﻋﻤﻠﻴﺎﺗﻲ و ﻓﺮآﻳﻨﺪي ﺑﻪ‬
2001"(SI) ‫واﺣﺪﻫﺎي ﻣﺘﺮﻳﻚ‬
API Publication "Conversion of Operational
and Process Measurement
Units to the Metric (SI)
Units",2001
IPS (IRANIAN
STANDARDS)
(‫ )اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ اﻳﺮان‬IPS
PETROLEUM
IPS-E-GN-100
"Engineering Standard for
Units"
‫ﺑﺮاي‬
‫"اﺳﺘﺎﻧﺪارد‬
"‫واﺣﺪﻫﺎ‬
IPS-E-GN-100
IPS-E-PR-330
"Engineering Standard for
Process
Design
of
Compressed Air Systems"
‫"اﺳﺘﺎﻧﺪارد ﻣﻬﻨﺪﺳﻲ ﺑﺮاي‬
‫ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي ﺳﺎﻣﺎﻧﻪﻫﺎي‬
"‫ﺗﻮﻟﻴﺪ و ﺗﻮزﻳﻊ ﻫﻮاي ﻓﺸﺮده‬
IPS-E-PR-330
IPS-M-PM-170 "Material and Equipment
Standard for Centrifugal
Compressors for Process
Services"
‫"اﺳﺘﺎﻧﺪارد ﺗﺠﻬﻴﺰات و ﻣﻮاد‬
‫ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از‬
‫ﻛﺎرﺑﺮيﻫﺎي‬
‫ﺑﺮاي‬
‫ﻣﺮﻛﺰ‬
"‫ﻓﺮآﻳﻨﺪي‬
IPS-M-PM-170
IPS-M-PM-190 " Material and Equipment
Standard for Axial Flow
Centrifugal Compressors"
‫"اﺳﺘﺎﻧﺪارد ﺗﺠﻬﻴﺰات و ﻣﻮاد‬
‫ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از‬
"‫ﻣﺮﻛﺰ ﺑﺎ ﺟﺮﻳﺎن ﻣﺤﻮري‬
IPS-M-PM-190
IPS-M-PM-200 " Material and Equipment
Standard for Reciprocating
Compressors for Process
Services"
‫"اﺳﺘﺎﻧﺪارد ﺗﺠﻬﻴﺰات و ﻣﻮاد‬
‫ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و‬
‫ﺑﺮﮔﺸﺘﻲ ﺑﺮاي ﻛﺎرﺑﺮي ﻫﺎي‬
"‫ﻓﺮآﻳﻨﺪي‬
‫"اﺳﺘﺎﻧﺪارد ﺗﺠﻬﻴﺰات و ﻣﻮاد‬
‫ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺟﺎﺑﺠﺎﻳﻲ‬
"‫ دوراﻧﻲ‬،‫ﻣﺜﺒﺖ‬
IPS-M-PM-200
IPS-M-PM-220 " Material and Equipment
Standard
for
Positive
Displacement
Compressors, Rotary"
API Std. 619
5
‫ﻣﻬﻨﺪﺳﻲ‬
IPS-M-PM-220
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
"GPSA
"‫"ﻛﺘﺎب اﻃﻼﻋﺎت ﻣﻬﻨﺪﺳﻲ‬
2004 ،‫وﻳﺮاﻳﺶ دوازدﻫﻢ‬
Engineering Data Book,"12th
Ed. January 2004
*Text Book
‫* ﻛﺘﺎب ﻣﻬﻨﺪﺳﻲ‬
‫ ﺗﻌﺎرﻳﻒ و واژﮔﺎن‬-3
3. DEFINITIONS AND TERMINOLOGY
3.1 Terms used in this Standard are in
accordance with the relevant sections of
definition of terms specified in API Standard
617, API Standard 618 and API Standard 619,
unless otherwise stated in this Section.
‫ اﺻﻄﻼﺣﺎت ﻣﻮرد اﺳﺘﻔﺎده در اﻳﻦ اﺳﺘﺎﻧﺪارد ﺑﻪ ﻏﻴﺮ‬1-3
‫از ﻣﻮارد ﺗﻌﻴﻴﻦ ﺷﺪه در اﻳﻦ ﻗﺴﻤﺖ ﻣﻄﺎﺑﻖ ﺑﺎ ﻗﺴﻤﺖ ﻫﺎي‬
API ‫ﻣﺮﺗﺒﻂ ﺗﻌﺎرﻳﻒ اﺻﻄﻼﺣﺎت ﻣﺸﺨﺺ ﺷﺪه در‬
API ‫ و‬API Standard 618 ‫و‬Standard 617
.‫ ﻣﻮﺳﺴﻪ ﻧﻔﺖ آﻣﺮﻳﻜﺎ اﺳﺖ‬Standard 619
(Im³/h) ‫ ﻣﺘﺮﻣﻜﻌﺐ ورودي ﺑﺮ ﺳﺎﻋﺖ‬2-3
3.2 Inlet Cubic Meters per Hour (Im³/h)
Refers to flow rate determined at the conditions
of pressure, temperature, compressibility and gas
composition, including moisture, at the
compressor inlet flange (substitution to API Std.
617, 1.5.14).
،‫ دﻣﺎ‬،‫اﺷﺎره ﺑﻪ ﺷﺪت ﺟﺮﻳﺎن ﻣﺸﺨﺺ در ﺷﺮاﻳﻂ ﻓﺸﺎر‬
‫ ﺗﺮﻛﻴﺐ ﮔﺎز و رﻃﻮﺑﺖ ﻣﻮﺟﻮد در ﻓﻠﻨﺞ‬،‫ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬
‫ورودي ﻛﻤﭙﺮﺳـﻮر دارد )ﺟــﺎﻳﮕــﺰﻳﻦ ﺑــﻪ اﺳﺘﺎﻧﺪارد‬
.(14-5-1‫ ﺑﻨﺪ‬API 617
(Am³/h) ‫ ﻣﺘﺮ ﻣﻜﻌﺐ ﺣﻘﻴﻘﻲ ﺑﺮ ﺳﺎﻋﺖ‬3-3
3.3 Actual Cubic Meters per Hour (Am³/h)
Refers to the flow rate at flowing conditions of
temperature and pressure at any given location.
Because this term describes flow at a number of
locations, it should not be used inter-chanegably
with inlet m³/h.
‫اﺷﺎره ﺑﻪ ﺷﺪت ﺟﺮﻳﺎن در ﺷﺮاﻳﻂ ﺟﺮﻳﺎﻧﻲ دﻣﺎ و ﻓﺸﺎر در‬
‫ ﺑﻪ ﺧﺎﻃﺮ اﻳﻦ ﻛﻪ اﻳﻦ واژه ﺟﺮﻳﺎن را در‬.‫ﻫﺮ ﻧﻘﻄﻪ دارد‬
‫ ﺗﻮﺻﻴﻪ ﻧﻤﻴﺸﻮد ﺑﻪ ﺟﺎي‬،‫ﺗﻌﺪادي از ﻧﻘﺎط ﺗﻮﺻﻴﻒ ﻣﻴﻜﻨﺪ‬
.‫ﻣﺘﺮﻣﻜﻌﺐ ﺑﺮ ﺳﺎﻋﺖ ورودي اﺳﺘﻔﺎده ﺷﻮد‬
(Sm³/h) ‫ ﻣﺘﺮﻣﻜﻌﺐ اﺳﺘﺎﻧﺪارد ﺑﺮ ﺳﺎﻋﺖ‬4-3
3.4 Standard Cubic Meter per Hour (Sm³/h)
‫اﺷﺎره ﺑﻪ ﺷﺪت ﺟﺮﻳﺎن در ﻫﺮ ﻣﻜﺎن دارد ﻛﻪ ﺑﻪ ﻓﺸﺎر‬
‫ درﺟﻪ‬15 ‫ ﻛﻴﻠﻮﭘﺎﺳﻜﺎل ﻣﻄﻠﻖ و دﻣﺎي‬101/325
‫ و ﺷﺮاﻳﻂ ﺧﺸﻚ‬1 ‫ﺳﺎﻧﺘﻴﮕﺮاد ﺑﺎ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬
.‫ﺗﺼﺤﻴﺢ ﺷﺪه اﺳﺖ‬
Refers to the flow rate at any location corrected
to a pressure of 101.325 kPa and at a temperature
of 15°C with a compressibility factor of 1.0 and
in a dry condition.
(Nm³/h) ‫ ﻣﺘﺮ ﻣﻜﻌﺐ ﻧﺮﻣﺎل ﺑﺮ ﺳﺎﻋﺖ‬5-3
3.5 Normal Cubic Meters per Hour (Nm³/h)
Refers to a flow rate at any location corrected to
the normal atmospheric pressure and a
temperature of 0°C with a compressibility factor
of 1.0 and in dry conditions.
‫اﺷﺎره ﺑﻪ ﺷﺪت ﺟﺮﻳﺎن در ﻫﺮ ﻣﻜﺎن دارد ﻛﻪ ﺑﻪ ﻓﺸﺎر‬
‫ﻋﺎدي ﻣﺤﻴﻂ و دﻣﺎي ﺻﻔﺮ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد ﺑﺎ ﺿﺮﻳﺐ‬
.‫ در ﺷﺮاﻳﻂ ﺧﺸﻚ اﺻﻼح ﺷﺪه اﺳﺖ‬1 ‫ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬
3.6 Specific Volume
‫ ﺣﺠﻢ وﻳﮋه‬6-3
Is the volume per unit mass or volume per mole
of material.
.‫ﺣﺠﻢ ﺑﺮ واﺣﺪ ﺟﺮم ﻳﺎ ﺣﺠﻢ ﺑﺮ ﻣﻮل ﻣﻮاد اﺳﺖ‬
GPSA
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
4. SYMBOLS AND ABBREVIATIONS
‫ ﻧﺸﺎﻧﻪ ﻫﺎ و اﺧﺘﺼﺎرات‬-4
‫ ﮔﺮﻣﺎي وﻳﮋه در ﻓﺸﺎر ﺛﺎﺑﺖ؛‬: Cp
‫ ﮔﺮﻣﺎي وﻳﮋه در ﺣﺠﻢ ﺛﺎﺑﺖ؛‬: Cv
‫ ﻗﻄﺮ داﺧﻠﻲ ﺳﻴﻠﻨﺪر؛‬: D
‫ ﻗﻄﺮ دﺳﺘﻪ ﭘﻴﺴﺘﻮن؛‬: d
‫ ﺗﻮان اﺳﺐ ﺑﺨﺎر واﻗﻌﻲ ﺗﺮاﻛﻢ‬،‫ ﺗﻮان اﺳﺐ ﺑﺨﺎر ﮔﺎز‬: Ghp
‫ﻣﻨﻬﺎي اﺗﻼف ﻣﻜﺎﻧﻴﻜﻲ؛‬
‫ ارﺗﻔﺎع؛‬: H
‫ آﻧﺘﺎﻟﭙﻲ؛‬: h
‫ ؛‬Cp/Cv ‫ ﻧﻤﺎي اﻳﺰﻧﺘﺮوﭘﻴﻚ‬: k
‫ ﮔﺮﻣﺎي وﻳﮋه ﻣﻮﻟﻲ در ﻓﺸﺎر ﺛﺎﺑﺖ؛‬: MCp
‫ ﮔﺮﻣﺎي وﻳﮋه ﻣﻮﻟﻲ در ﺣﺠﻢ ﺛﺎﺑﺖ ؛‬: MCv
‫ ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ؛‬: MW
‫ دور ﺑﺮ دﻗﻴﻘﻪ؛‬،‫ ﺳﺮﻋﺖ‬: N
‫ ﻣﻮل ﺑﺮ دﻗﻴﻘﻪ؛‬،‫ ﺟﺮﻳﺎن ﻣﻮﻟﻲ‬: Nm
Cp = Specific heat at constant pressure,
Cv = Specific heat at constant volume,
D = Cylinder inside diameter,
d = Piston rod diameter,
Ghp = Gas horsepower, actual compression
horsepower excluding mechanical losses,
H = Head,
h = Enthalpy,
k = Isentropic exponent, Cp/Cv
MCp = Molar specific heat at constant pressure,
MCv = Molar specific heat at constant volume,
MW = Molecular weight,
N = Speed, rpm
Nm = Molar flow, moles/min
‫ ﻧﻤﺎي ﭘﻠﻲ ﺗﺮوﭘﻴﻚ ﻳﺎ ﺗﻌﺪاد ﻣﻮﻟﻬﺎ؛‬: n
‫ ﻓﺸﺎر؛‬: P
‫ ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن؛‬: PD
‫ ﻇﺮﻓﻴﺖ ورودي؛‬: Q
‫ ﺷﺪت ﺟﺮﻳﺎن اﺳﺘﺎﻧﺪارد ﮔﺎز؛‬: Qg
‫ ؛‬P2/P1 ‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ‬: r
‫ آﻧﺘﺮوﭘﻲ؛‬: s
‫ ﻃﻮل ﺣﺮﻛﺖ ﭘﻴﺴﺘﻮن؛‬: Stroke
‫ دﻣﺎي ﻣﻄﻠﻖ؛‬: T
‫ دﻣﺎ؛‬: t
‫ راﻧﺪﻣﺎن ﺣﺠﻤﻲ؛‬: VE
‫ ﺟﺮﻳﺎن ﺟﺮﻣﻲ؛‬: w
‫ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي؛‬: Z
‫ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﻣﻴﺎﻧﮕﻴﻦ؛‬: Zavg
n = Polytropic exponent or number of moles
P = Pressure,
PD = Piston displacement,
Q = Inlet capacity
Qg = Standard gas flow rate,
r = Compression ratio, P2/P1
s = Entropy,
Stroke = Length of piston movement,
T = Absolute temperature,
t = Temperature
VE = Volumetric efficiency,
w = Weight flow,
Z = Compressibility factor,
Zavg = Average compressibility factor,
‫ ﺑﺼﻮرت اﻋﺸﺎري ﺑﻴﺎن ﻣﻲ ﺷﻮد؛‬، ‫ راﻧﺪﻣﺎن‬: 
= Efficiency, expressed as a decimal,
‫زﻳﺮوﻧﺪﻫﺎ‬
Subscripts
‫ ﻣﻴﺎﻧﮕﻴﻦ؛‬: avg
‫ ﺧﺮوﺟﻲ؛‬: d
‫ ﮔﺎز؛‬: g
‫ ﻓﺮآﻳﻨﺪ اﻳﺰﻧﺘﺮوﭘﻴﻚ؛‬: is
‫ ﺷﺮاﻳﻂ اﺳﺘﺎﻧﺪارد ﻣﻮرد اﺳﺘﻔﺎده ﺑﺮاي ﻣﺤﺎﺳﺒﻪ ﻳﺎ‬: L
‫ﻗﺮارداد؛‬
avg = Average
d = Discharge
g = Gas
is = Isentropic process
L = Standard conditions used for calculation or
contract
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
‫ ﻓﺮآﻳﻨﺪ ﭘﻠﻲ ﺗﺮوﭘﻴﻚ؛‬: P
p = Polytropic process
F ‫ ﻣﻄﻠﻖ ﻫﺮ‬psia 14/7 ً‫ ﺷﺮاﻳﻂ اﺳﺘﺎﻧﺪارد ﻋﻤﻮﻣﺎ‬: S
S = Standard conditions, usually 14.7 psia,60°F
‫؛‬60°
‫ ﻣﻜﺶ؛‬: s
‫ ﻛﻞ ﻳﺎ ﻛﻠﻲ؛‬: t
‫ ﺷﺮاﻳﻂ ورودي؛‬: 1
‫ ﺷﺮاﻳﻂ ﺧﺮوﺟﻲ؛‬: 2
s = Suction
t = Total or overall
1 = Inlet conditions
2 = Outlet conditions
5. UNITS
‫ واﺣﺪﻫﺎ‬-5
This Standard is based on International System
of Units (SI) as per IPS-E-GN-100, except where
otherwise specified.
،(SI) ‫ ﺑﺮﻣﺒﻨﺎي ﻧﻈﺎم ﺑﻴﻦ اﻟﻤﻠﻠﻲ واﺣﺪﻫﺎ‬،‫اﻳﻦ اﺳﺘﺎﻧﺪارد‬
‫ ﻣﮕﺮ ﺑﻪ‬،‫ ﻣﻲﺑﺎﺷﺪ‬IPS-E-GN-100 ‫ﻣﻨﻄﺒﻖ ﺑﺎ اﺳﺘﺎﻧﺪارد‬
.‫ﮔﻮﻧﻪ دﻳﮕﺮي ﻣﺸﺨﺺ ﺷﺪه ﺑﺎﺷﺪ‬
6. GENERAL
‫ ﻋﻤﻮﻣﻲ‬-6
- Compressors are generally divided into three
major types, dynamic, positive displacement
and thermal as shown in Fig. A.1 of Appendix
A.
‫ﻛﻤﭙﺮﺳﻮرﻫﺎ ﻋﻤﻮﻣﺎً ﺑﻪ ﺳﻪ ﻧﻮع ﻋﻤﺪه ﺗﻘﺴﻴﻢ‬
- For typical figures of three type of
compressors see Appendix C
‫ ﺑﺮاي ﺷﻜﻠﻬﺎي ﻧﻤﻮﻧﻪ ﺳﻪ ﻧﻮع ﻛﻤﭙﺮﺳﻮر ﭘﻴﻮﺳﺖ ج‬-
- The type of compressor to be used shall be the
most suitable for the duty involved. See the
compressor coverage chart in Fig. A.2 of
Appendix A.
‫ ﻧﻮع ﻛﻤﭙﺮﺳﻮر ﻣﻮرد اﺳﺘﻔﺎده ﺑﺎﻳﺪ ﺑﺮاي ﻇﺮﻓﻴﺖ‬-
- Adequate knock out facilities including
demister pads where necessary shall be
provided to prevent damage by liquid carry
over into the compressor.
‫ در ﻣﻮاﻗﻊ ﻟﺰوم ﺑﺮاي ﻣﻤﺎﻧﻌﺖ از آﺳﻴﺐ ﻫﻤﺮاه ﺑﺮي‬-
- Compressors handling SO2, HCl or other
gases which are corrosive in the presence of
water, shall not employ water as a cooling
medium unless the water circuit is positively
isolated from the gas side, e.g., by separate
water jackets. It is not sufficient to rely on
gaskets or seals for isolation.
‫ ﻳﺎ ﺳﺎﻳﺮ‬HCl ‫ و‬SO2 ‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﭘﺬﻳﺮﻧﺪه‬-
Similar restrictions shall apply to the use of
glycol as a coolant for machines handling
corrosive gases plus hydrogen as the hydrogen
can react with glycol to form water. The use of
oil as a cooling medium will be acceptable as
an alternative in special cases.
‫ﻣﺤﺪودﻳﺖﻫﺎي ﻣﺸﺎﺑﻪ ﺑﺮاي اﺳﺘﻔﺎده از ﮔﻼﻳﻜﻮل ﺑﻪ‬
‫ﻋﻨﻮان ﺧﻨﻚ ﻛﻦ ﺑﺮاي ﻣﺎﺷﻴﻨﻬﺎي ﺣﺎﻣﻞ ﮔﺎزﻫﺎي‬
‫ﺧﻮرﻧﺪه ﺑﻪ ﻋﻼوه ﻫﻴﺪروژن ﺑﺎﻳﺪ اﻋﻤﺎل ﮔﺮدد زﻳﺮا‬
‫ﻫﻴﺪروژن ﻣﻴﺘﻮاﻧﺪ در واﻛﻨﺶ ﺑﺎ ﮔﻼﻳﻜﻮل آب ﺗﻮﻟﻴﺪ‬
‫ اﺳﺘﻔﺎده از روﻏﻦ ﺑﻪ ﻋﻨﻮان ﻣﺤﻴﻂ ﺧﻨﻚ ﻛﻦ در‬.‫ﻛﻨﺪ‬
‫ﺣﺎﻟﺘﻬﺎي ﺧﺎص ﺑﻪ ﻋﻨﻮان ﺟﺎﻳﮕﺰﻳﻦ ﻗﺎﺑﻞ ﻗﺒﻮل ﺧﻮاﻫﺪ‬
.‫ﺑﻮد‬
-
‫ ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ و ﺣﺮارﺗﻲ ﻣﻄﺎﺑﻖ‬،‫ ﻣﺘﺤﺮك‬،‫ﻣﻴﺸﻮﻧﺪ‬
.‫ ﭘﻴﻮﺳﺖ اﻟﻒ‬1-‫ﺷﻜﻞ اﻟﻒ‬
.‫را ﺑﺒﻴﻨﻴﺪ‬
‫ ﻧﻤﻮدار ﻫﻤﮕﺮاﻳﻲ‬.‫ﻣﺸﺨﺺ ﺷﺪه ﻣﻨﺎﺳﺐﺗﺮﻳﻦ ﺑﺎﺷﺪ‬
.‫ ﭘﻴﻮﺳﺖ اﻟﻒ را ﺑﺒﻴﻨﻴﺪ‬2-‫ﻛﻤﭙﺮﺳﻮر در ﺷﻜﻞ اﻟﻒ‬
‫ ﺑﺎﻳﺪ ﺗﺴﻬﻴﻼت ﻗﻄﺮه ﮔﻴﺮي‬،‫ﻣﺎﻳﻊ ﺑﻪ داﺧﻞ ﻛﻤﭙﺮﺳﻮر‬
.‫ ﺗﻌﺒﻴﻪ ﺷﻮد‬، ‫ﻣﻨﺎﺳﺐ ﺷﺎﻣﻞ ﺻﻔﺤﺎت ﻗﻄﺮهﮔﻴﺮ‬
‫ﮔﺎزﻫﺎﻳﻲ ﻛﻪ در ﺣﻀﻮر آب ﺧﻮرﻧﺪه ﻫﺴﺘﻨﺪ ﻧﺒﺎﻳﺪ از‬
‫آب ﺑﻪ ﻋﻨﻮان ﻣﺤﻴﻂ ﺧﻨﻚ ﻛﻦ اﺳﺘﻔﺎده ﮔﺮدد ﻣﮕﺮ اﻳﻦ‬
‫ﻛﻪ ﻣﺪار آب ﺑﻪ ﺻﻮرت ﻣﻮﺛﺮ از ﺳﻤﺖ ﮔﺎز ﻣﺠﺰا ﺷﻮد‬
‫ اﻋﺘﻤﺎد ﺑﻪ ﻻﻳﻲ ﻫﺎ ﻳﺎ ﻧﺸﺖ‬.‫ﻣﺎﻧﻨﺪ ﺟﺪاره ﻣﺠﺰاي آب‬
.‫ﺑﻨﺪﻫﺎ ﺑﺮاي ﺟﺪاﺳﺎزي ﻛﺎﻓﻲ ﻧﻤﻲ ﺑﺎﺷﺪ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
- Rotodynamic compressors are to be provided
with anti-surge equipment. The response time
for the control equipment shall be such as to
prevent surge during any anticipated process
condition, due consideration being given to the
speed at which process changes or upsets can
move the compressor operation towards surge.
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺘﺤﺮك دوراﻧﻲ ﺑﺎﻳﺪ ﺑﻪ ﺗﺠﻬﻴﺰات‬-
For the more complicated installations with
multiple stages and sidestreams, or multiple
units (in series or parallel) or variable speed
units, an analysis of the stability of the antisurge control system is also necessary.
‫ﺑﺮاي ﺗﺠﻬﻴﺰات ﭘﻴﭽﻴﺪهﺗﺮ ﺑﺎ ﭼﻨﺪ ﻣﺮﺣﻠﻪ و ﺟﺮﻳﺎنﻫﺎي‬
‫ ﻳﺎ ﭼﻨﺪ واﺣﺪ )ﺑﻪ ﺻﻮرت ﺳﺮي ﻳﺎ ﻣﻮازي( ﻳﺎ‬،‫ﺟﺎﻧﺒﻲ‬
‫ ﺑﺮرﺳﻲ ﭘﺎﻳﺪاري ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل‬،‫واﺣﺪﻫﺎي دور ﻣﺘﻐﻴﺮ‬
.‫ﺿﺪ – ﻧﻮﺳﺎن ﻧﻴﺰ ﻻزم اﺳﺖ‬
‫ زﻣﺎن ﭘﺎﺳﺦ ﺗﺠﻬﻴﺰات‬.‫ ﻧﻮﺳﺎن ﻣﺠﻬﺰ ﺑﺎﺷﻨﺪ‬-‫ﺿﺪ‬
‫ﻛﻨﺘﺮﻟﻲ ﺑﺎﻳﺪ ﻣﻘﺪاري ﺑﺎﺷﺪ ﻛﻪ از ﻧﻮﺳﺎن در ﻫﺮ ﮔﻮﻧﻪ‬
‫ ﺑﺎﻳﺪ ﺑﻪ‬.‫ﺷﺮاﻳﻂ ﻓﺮآﻳﻨﺪي ﻣﻮرد اﻧﺘﻈﺎر ﻣﻤﺎﻧﻌﺖ ﻛﻨﺪ‬
‫ﺳﺮﻋﺘﻲ ﻛﻪ ﻓﺮآﻳﻨﺪ ﺗﻐﻴﻴﺮ ﻣﻲ ﻛﻨﺪ ﻳﺎ اﺧﺘﻼل اﻳﺠﺎد ﻣﻲ‬
‫ﻛﻨﺪ و ﻣﻴﺘﻮاﻧﺪ ﻋﻤﻠﻜﺮد ﻛﻤﭙﺮﺳﻮر را ﺑﻪ ﺳﻤﺖ ﻧﻮﺳﺎن‬
.‫ﺣﺮﻛﺖ دﻫﺪ ﺗﻮﺟﻪ ﻛﺎﻓﻲ ﺷﻮد‬
6.1 Type Selection Criteria
‫ ﻣﻌﻴﺎر اﻧﺘﺨﺎب ﻧﻮع‬1-6
The choice of the type of compressor, whether
axial, centrifugal, reciprocating or rotary,
depends primarily on the required flow to be
compressed, the density of the gas in conjunction
with the total head (for a given gas, this is the
compression ratio) and the duty which has to be
performed. Table A.1 of Appendix A outlines the
compression limits for the four types of
compression equipment.
،‫ ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬،‫اﻧﺘﺨﺎب ﻧﻮع ﻛﻤﭙﺮﺳﻮر ﭼﻪ از ﻧﻮع ﻣﺤﻮري‬
‫رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﻳﺎ دوراﻧﻲ ﺑﺎﺷﺪ اﺻﻮﻻً ﺑﻪ ﺟﺮﻳﺎن ﻣﻮرد‬
‫ ﭼﮕﺎﻟﻲ ﮔﺎز ﺑﻪ ﻫﻤﺮاه ارﺗﻔﺎع‬،‫ﻧﻴﺎزي ﻛﻪ ﺑﺎﻳﺪ ﻣﺘﺮاﻛﻢ ﺷﻮد‬
‫ﻛﻞ )ﺑﺮاي ﮔﺎز ﻣﺸﺨﺺ اﻳﻦ ﻫﺪف ﻧﺴﺒﺖ ﺗﺮاﻛﻢ اﺳﺖ( و‬
1-‫ ﺟﺪول اﻟﻒ‬.‫وﻇﻴﻔﻪاي ﻛﻪ اﻧﺠﺎم ﻣﻲ ﺷﻮد ﺑﺴﺘﮕﻲ دارد‬
‫ﭘﻴﻮﺳﺖ اﻟﻒ ﺑﻪ رﺋﻮس ﻣﺤﺪودﻳﺘﻬﺎي ﺗﺮاﻛﻢ ﭼﻬﺎر ﻧﻮع از‬
.‫ﺗﺠﻬﻴﺰات ﻣﺘﺮاﻛﻢ ﺳﺎزي ﻣﻲ ﭘﺮدازد‬
6.1.1 Axial compressors
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري‬1-1-6
Axial compressors can handle large volume flow
and are more efficient than centrifugal
compressors. However, centrifugals are less
vulnerable and hence more reliable, have wider
operating ranges and are less susceptible to
fouling.
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري ﻣﻴﺘﻮاﻧﻨﺪ ﺣﺠﻢ ﺑﺰرﮔﻲ از ﺟﺮﻳﺎن را‬
‫ﻣﺘﺮاﻛﻢ ﻛﻨﻨﺪ و ﻛﺎرآﻣﺪﺗﺮ از ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬
‫ ﺑﺎ اﻳﻦ وﺟﻮد ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ آﺳﻴﺐ‬.‫ﻫﺴﺘﻨﺪ‬
‫ﭘﺬﻳﺮي ﻛﻤﺘﺮي داﺷﺘﻪ و از اﻳﻦ رو ﻗﺎﺑﻞ اﻋﺘﻤﺎدﺗﺮ ﻫﺴﺘﻨﺪ و‬
‫داﻣﻨﻪ ﻓﻌﺎﻟﻴﺖ وﺳﻴﻊﺗﺮ و ﺣﺴﺎﺳﻴﺖ ﻛﻤﺘﺮي ﺑﻪ رﺳﻮب‬
.‫دارﻧﺪ‬
Axial compressors should be considered only for
air, sweet natural gas or non-corrosive gases.
Axial compressors shall be in accordance with
Iranian Petroleum Standards IPS-M-PM-190, for
"Axial Flow Centrifugal Compressors".
‫ ﮔﺎز‬،‫ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري ﻓﻘﻂ ﺑﺮاي ﻫﻮا‬
‫ﻃﺒﻴﻌﻲ ﺷﻴﺮﻳﻦ ﻳﺎ ﮔﺎزﻫﺎي ﻏﻴﺮﺧﻮرﻧﺪه در ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬
‫ ﻛﻤﭙﺮﺳﻮرﻫــﺎي ﻣﺤﻮري ﺑـﺎﻳـﺪ ﻣﻄﺎﺑﻖ ﺑــﺎ‬.‫ﺷﻮﻧﺪ‬
‫ ﺑﺮاي "ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ‬IPS-M-PM-190 ‫اﺳﺘـﺎﻧﺪارد‬
.‫از ﻣﺮﻛﺰ ﺟﺮﻳﺎن ﻣﺤﻮري" ﺑﺎﺷﻨﺪ‬
6.1.2 Centrifugal compressors
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬2-1-6
‫ﺗﻌﺒﻴﻪ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﻣﻴﺘﻮاﻧﺪ ﻣﻘﺪار ﺟﺮﻳﺎن ﻣﻮرد‬
‫ ﺑﻨﺎﺑﺮاﻳﻦ اﻳﻦ ﻧﻮع‬،‫ﻧﻴﺎز را ﺑﺎ راﻧﺪﻣﺎن ﻗﺎﺑﻞ ﻗﺒﻮل ﺗﺄﻣﻴﻦ ﻛﻨﺪ‬
‫اﻧﺘﺨﺎب ارﺟﺢ ﻣﻲ ﺑﺎﺷﺪ زﻳﺮا ﺗﻮاﻧﺎﻳﻲ ﻛﺎر ﻛﺮدن ﺑﻪ ﺻﻮرت‬
‫ﻣﺪاوم ﺑﺮاي دورهﻫﺎي زﻣﺎن ﻃﻮﻻﻧﻲ را در ﺻﻮرﺗﻲ ﻛﻪ ﺑﻪ‬
‫ اﮔﺮ ﺟﺮﻳﺎن‬.‫ دارد‬،‫ﻃﻮر ﺻﺤﻴﺢ ﻃﺮاﺣﻲ و ﻧﺼﺐ ﺷﺪه ﺑﺎﺷﺪ‬
Providing a centrifugal compressor can handle
the required flow with a reasonable efficiency,
then this type is the preferred choice because it
has the potential to operate continuously for long
9
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
periods, if properly designed and assembled. If
‫ ﻣﺘﺮ ﻣﻜﻌﺐ در ﺳﺎﻋﺖ ﻳﺎ ﺑﻴﺸﺘﺮ‬300 ‫در ﺷﺮاﻳﻂ ﺧﺮوﺟﻲ‬
‫ﺑﺎﺷﺪ در آن ﺻﻮرت اﻣﻜﺎن اﺳﺘﻔﺎده از ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ‬
.‫از ﻣﺮﻛﺰ ﺑﺮرﺳﻲ ﻣﻴﺸﻮد‬
the flow at discharge conditions is 300 m³/h or
more, then the possibility of using centrifugal
compressor to be investigated.
API ‫ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ اﺳﺘﺎﻧﺪارد‬
Centrifugal compressors shall be designed in
accordance with API Std. 617 as amended by
Iranian Petroleum Standards IPS-M-PM-170, for
"Centrifugal Compressors for Process Services".
‫و ﻣﺘﻤﻢ اﺳﺘﺎﻧﺪاردﻫﺎي ﻧﻔﺖ اﻳﺮان‬
617
‫ ﺑﺮاي "ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬,IPS-M-PM-170
.‫ﺑﺮاي ﻛﺎرﺑﺮي ﻓﺮآﻳﻨﺪي" ﺑﺎﺷﺪ‬
6.1.3 Reciprocating compressors
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬3-1-6
Where the required flow is too small for a
centrifugal compressor, or where the required
head is so high that an undesirably large number
of stages would be necessary, then generally the
choice should be a reciprocating compressor.
‫در ﺻﻮرﺗﻲ ﻛﻪ ﻣﻘﺪار ﺟﺮﻳﺎن ﻻزم ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي‬
‫ ﻳﺎ ارﺗﻔﺎع ﻣﻮرد ﻧﻴﺎز آﻧﻘﺪر‬،‫ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺧﻴﻠﻲ ﻛﻢ ﺑﺎﺷﺪ‬
‫زﻳﺎد ﺑﺎﺷﺪ ﻛﻪ ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺑﻄﻮر ﻏﻴﺮﻗﺎﺑﻞ ﻗﺒﻮﻟﻲ زﻳﺎد ﻣﻲ‬
‫ﺷﻮد در اﻳﻦ ﺣﺎﻟﺖ ﻋﻤﻮﻣﺎً ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻛﻤﭙﺮﺳﻮر رﻓﺖ و‬
.‫ﺑﺮﮔﺸﺘﻲ اﻧﺘﺨﺎب ﺷﻮد‬
As a reciprocating compressor cannot fulfill the
minimum
requirement
of
continuous
uninterrupted operation for a twoyear period, due
to fairly high maintenance requirements, a fullcapacity spare shall be provided as general rule
for reciprocating compressors in critical services.
Alternatively, three half-capacity machines may
be specified, two running in parallel with the
third unit as a spare. Reciprocating compressors
shall be in accordance with API Std. 618 as
amended by IPS-G-PM-200, for "Reciprocating
Compressors for Process Services".
‫از آﻧﺠﺎﻳﻲ ﻛﻪ ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺣﺪاﻗﻞ اﻟﺰاﻣﺎت‬
‫ﻋﻤﻠﻴﺎت ﻣﺪاوم ﺑﻲ وﻗﻔﻪ ﺑﺮاي دوره دو ﺳﺎﻟﻪ را ﻧﻤﻴﺘﻮاﻧﺪ‬
‫ ﺑﻪ دﻟﻴﻞ اﻟﺰاﻣﺎت ﺗﻌﻤﻴﺮاﺗﻲ ﻧﺴﺒﺘﺎً ﺑﺎﻻ ﺑﻪ ﻃﻮر‬،‫ﺑﺮآورده ﻛﻨﺪ‬
‫ﻛﻠﻲ ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ در ﻛﺎرﺑﺮيﻫﺎي‬
‫ روش‬.‫ﺣﺴﺎس ﻳﻚ ﻳﺪك ﺗﻤﺎم ﻇﺮﻓﻴﺖ ﺑﺎﻳﺪ ﺗﻌﺒﻴﻪ ﺷﻮد‬
،‫دﻳﮕﺮ ﻣﻤﻜﻦ اﺳﺖ ﺗﻌﺒﻴﻪ ﺳﻪ ﻣﺎﺷﻴﻦ ﻧﺼﻒ ﻇﺮﻓﻴﺖ ﺑﺎﺷﺪ‬
‫دوﺗﺎ در ﺣﺎل ﻛﺎر ﺑﻪ ﺻﻮرت ﻣﻮازي و واﺣﺪ ﺳﻮم ﺑﻪ ﺻﻮرت‬
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺎﻳﺪ‬.‫ﻳﺪك ﻣﻲ ﺑﺎﺷﺪ‬
IPS-G-PM-200‫ و ﻣﺘﻤﻢ‬API 618 ‫ﻣﻄﺎﺑﻖ ﺑﺎاﺳﺘﺎﻧﺪارد‬
‫ﺑﺮاي "ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺮاي ﻛﺎرﺑﺮي‬
.‫ﻓﺮآﻳﻨﺪي" ﺑﺎﺷﻨﺪ‬
6.1.4 Rotary compressors
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ‬4-1-6
Rotary compressor shall be considered only
where there is proven experience of acceptable
performance of this type of compressor in the
duty concerned and only where there are
advantages over a reciprocating compressor.
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ ﻓﻘﻂ در ﺟﺎﻳﻲ ﻛﻪ ﺗﺠﺮﺑﻪ ﻗﺎﺑﻞ‬
‫اﺳﺘﻨﺎد از ﻛﺎرآﻳﻲ ﻗﺎﺑﻞ ﻗﺒﻮل اﻳﻦ ﻧﻮع از ﻛﻤﭙﺮﺳﻮر در‬
‫ﻇﺮﻓﻴﺖ ﻣﺸﺨﺺ و ﻓﻘﻂ ﺟﺎﻳﻲ ﻛﻪ ﻧﺴﺒﺖ ﺑﻪ ﻛﻤﭙﺮﺳﻮر‬
.‫ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﻴﺸﻮد‬،‫رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﻣﺰﻳﺖ دارد‬
The application of oil flooded screw compressors
for instrument air and of dry running rotary
screw compressors, sliding vane compressors
and rotary lube compressors for process duties,
requires the explicit approval of the Company.
‫ﻛﺎرﺑﺮد ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺎرﭘﻴﭽﻲ ﻏﻮﻃﻪور در روﻏﻦ ﺑﺮاي‬
‫ﻫﻮاي اﺑﺰار دﻗﻴﻖ و ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺎرﭘﻴﭽﻲ ﺧﺸﻚ‬
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺗﻴﻐﻪاي ﻟﻐﺰﺷﻲ و ﻛﻤﭙﺮﺳﻮرﻫﺎي‬،‫ﻛﺎرﻛﻦ‬
‫ ﻧﻴﺎز ﺑﻪ ﺗﺄﻳﻴﺪ ﺻﺮﻳﺢ‬،‫روﻏﻨﻲ دوراﻧﻲ ﺑﺮاي وﻇﺎﻳﻒ ﻓﺮآﻳﻨﺪي‬
.‫ﻛﺎرﻓﺮﻣﺎ دارد‬
Rotary-type positive displacement compressors
shall be in accordance with API Std. 619 as
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ ﻧﻮع دوراﻧﻲ ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ‬
‫ ﺑﺮاي‬IPS-M-PM-220 ‫ و ﻣﺘﻤﻢ‬API 619 ‫اﺳﺘﺎﻧﺪارد‬
10
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
amended by IPS-M-PM-220, for "Positive
Displacement Compressors, Rotary".
.‫"ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ دوراﻧﻲ" ﺑﺎﺷﻨﺪ‬
6.2 Atmospheric Pressure
‫ ﻓﺸﺎر ﺟﻮي‬2-6
The absolute pressure of the atmosphere at the
site should be considered as the "absolute
pressure" in the compressor calculations. The
value of the absolute pressure is taken as 101.325
kPa at sea level and declines with increasing
altitude as shown in Table A.2 of Appendix A.
‫ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻓﺸﺎر ﻣﻄﻠﻖ ﻣﺤﻴﻂ در ﻣﺤﻞ واﺣﺪ در‬
‫ﻣﺤﺎﺳﺒﺎت ﻛﻤﭙﺮﺳﻮر ﺑﻪ ﻋﻨﻮان "ﻓﺸﺎر ﻣﻄﻠﻖ " در ﻧﻈﺮ‬
101/325 ‫ ﻣﻘﺪار ﻓﺸﺎر ﻣﻄﻠﻖ در ﺳﻄﺢ درﻳﺎ‬.‫ﮔﺮﻓﺘﻪ ﺷﻮد‬
2-‫ﻛﻴﻠﻮ ﭘﺎﺳﻜﺎل ﺑﻮده و ﺑﺎ اﻓﺰاﻳﺶ ارﺗﻔﺎع ﻣﻄﺎﺑﻖ ﺷﻜﻞ اﻟﻒ‬
.‫ﭘﻴﻮﺳﺖ اﻟﻒ ﻛﺎﻫﺶ ﻣﻴﻴﺎﺑﺪ‬
6.3 Specification Sheets
‫ ﺑﺮﮔﻪﻫﺎي ﻣﺸﺨﺼﺎت‬3-6
Process information required to complete
specification sheets for compressors are
presented in Appendix B.
‫اﻃﻼﻋﺎت ﻓﺮآﻳﻨﺪي ﻻزم ﺑﺮاي ﺗﻜﻤﻴﻞ ﺑﺮﮔﻪﻫﺎي ﻣﺸﺨﺼﺎت‬
.‫ﻛﻤﭙﺮﺳﻮر در ﭘﻴﻮﺳﺖ )ب( ﻧﺸﺎن داده ﺷﺪهاﻧﺪ‬
7. CENTRIFUGAL COMPRESSORS
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬-7
7.1 General
‫ ﻋﻤﻮﻣﻲ‬1-7
7.1.1 The centrifugal (radial flow) compressor is
well established for the compression of gases and
vapors. It has proven its economy and
uniqueness in many applications, particularly
where large volumes are handled at medium
pressures.
‫ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ )ﺟﺮﻳﺎن ﺷﻌﺎﻋﻲ( ﺑﺮاي‬1-1-7
‫ﻣﺘﺮاﻛﻢ ﻛﺮدن ﮔﺎزﻫﺎ و ﺑﺨﺎرات ﻛﺎﻣﻼً ﺷﻨﺎﺧﺘﻪ ﺷﺪه‬
‫ ﻣﻨﺤﺼﺮ ﺑﻪ ﻓﺮدي و اﻗﺘﺼﺎدي ﺑﻮدن آن در اﻛﺜﺮ‬.‫ﻣﻲﺑﺎﺷﺪ‬
‫ﻛﺎرﺑﺮدﻫﺎ ﺛﺎﺑﺖ ﺷﺪه اﺳﺖ ﻣﺨﺼﻮﺻﺎً ﺟﺎﻳﻲ ﻛﻪ ﺣﺠﻢ زﻳﺎدي‬
.‫ﺑﺎ ﻓﺸﺎر ﻣﺘﻮﺳﻂ ﻣﺘﺮاﻛﻢ ﻣﻴﺸﻮد‬
-‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺑﺮاي ﺗﻤﺎم ﻛﺎرﺑﺮي‬2-1-7
7.1.2 Centrifugal compressors shall conform to
API Std. No. 617 for all services handling air or
gas, except machines developing less than 35
kPa (0.35 bar) from atmospheric pressure, which
may be classified as fans or blowers.
API 617 ‫ﻫﺎي ﺣﺎﻣﻞ ﻫﻮا ﻳﺎ ﮔﺎز ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ اﺳﺘﺎﻧﺪارد‬
35 ‫ﺑﺎﺷﺪ ﺑﻪ ﺟﺰ ﻣﺎﺷﻴﻦ آﻻت ﻛﻪ ﻓﺸﺎر ﻛﻤﺘﺮ از‬
‫ ﺑﺎر( از ﻓﺸﺎر ﺟﻮي ﺗـﻮﻟﻴـﺪ ﻣﻴﻜﻨﻨﺪ‬0/35)‫ﻛﻴﻠﻮﭘﺎﺳﻜﺎل‬
.‫ﻛــﻪ ﺑــﻪ ﻋﻨﻮان دﻣﻨﺪه و ﺑﺎدزن ﻃﺒﻘﻪ ﺑﻨﺪي ﻣﻴﺸﻮﻧﺪ‬
7.1.3 Performance
‫ ﻛﺎرآﻳﻲ‬3-1-7
7.1.3.1 Compressors shall be guaranteed for
head, capacity, and satisfactory performance at
all specified operating points and further shall be
guaranteed for power at the rated point.
‫ ﻇﺮﻓﻴﺖ و‬،‫ ﻛﻤﭙﺮﺳﻮرﻫﺎ ﺑﺎﻳﺪ ﺑﺮاي ارﺗﻔﺎع‬1-3-1-7
‫ﻛﺎرآﻳﻲ رﺿﺎﻳﺖ ﺑﺨﺶ در ﺗﻤﺎم ﻧﻘﺎط ﻋﻤﻠﻴﺎﺗﻲ ﻣﺸﺨﺺ‬
‫ﺗﻀﻤﻴﻦ ﺷﻮﻧﺪ و ﻫﻤﭽﻨﻴﻦ ﺑﺎﻳﺪ ﺑﺮاي ﺗﻮان ﻣﺼﺮﻓﻲ در‬
.‫ﻧﻘﻄﻪ ﺗﻌﻴﻴﻦ ﻇﺮﻓﻴﺖ ﺗﻀﻤﻴﻦ ﺷﻮﻧﺪ‬
7.1.3.2
2-3-1-7
a) The volume capacity at the surge point
shall not exceed the specified percentage of
normal capacity at normal speed, and normal
(unthrottled) suction conditions. The rise in
pressure ratio from normal capacity to the
surge point at normal speed shall not be less
than that specified.
‫اﻟﻒ( ﻇﺮﻓﻴﺖ ﺣﺠﻤﻲ در ﻧﻘﻄﻪ ﻧﻮﺳﺎن ﻧﺒﺎﻳﺪ از درﺻﺪ‬
‫ﻣﻌﻴﻨﻲ از ﻇﺮﻓﻴﺖ ﻋﺎدي در ﺳﺮﻋﺖ ﻋﺎدي و ﺷﺮاﻳﻂ‬
‫ اﻓﺰاﻳﺶ ﻧﺴﺒﺖ ﻓﺸﺎر از‬.‫ﻣﻜﺶ ﻋﺎدي ﺑﻴﺸﺘﺮ ﺷﻮد‬
‫ﻇﺮﻓﻴﺖ ﻋﺎدي ﺑﻪ ﻧﻘﻄﻪ ﻧﻮﺳﺎن در ﺳﺮﻋﺖ ﻋﺎدي ﻧﺒﺎﻳﺪ‬
.‫از ﻣﻘﺪار ﻣﺸﺨﺺ ﻛﻤﺘﺮ ﺷﻮد‬
b) The head developed at 115% of normal
capacity at normal speed shall be not less than
approximately 85% of the head developed at
the normal operating point.
‫ درﺻﺪ ﻇﺮﻓﻴﺖ ﻋﺎدي‬115 ‫ب ( ارﺗﻔﺎع ﺗﻮﻟﻴﺪ ﺷﺪه در‬
‫ درﺻﺪ‬85 ً‫در ﺳﺮﻋﺖ ﻋﺎدي ﻧﺒﺎﻳﺪ ﻛﻤﺘﺮ از ﺗﻘﺮﻳﺒﺎ‬
.‫ارﺗﻔﺎع ﺗﻮﻟﻴﺪ ﺷﺪه در ﻧﻘﻄﻪ ﻋﻤﻠﻴﺎت ﻋﺎدي ﺑﺎﺷﺪ‬
11
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
7.1.3.3 The head-capacity characteristic curve
shall rise continuously from the rated point to the
predicted surge. The compressor, without the use
of a bypass, shall be suitable for continuous
operation at any capacity at least 10 percent
greater than the predicted approximate surge
capacity shown in the proposal.
‫ ﻇﺮﻓﻴﺖ ﺑﺎﻳﺪ ﺑﻪ‬- ‫ ﻣﻨﺤﻨﻲ ﻣﺸﺨﺼﻪ ارﺗﻔﺎع‬3-3-1-7
7.1.3.4 For variable speed compressors, the head
and capacity shall be guaranteed with the
understanding that the power may vary ±4%.
‫ ارﺗﻔﺎع و‬،‫ ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي دور ﻣﺘﻐﻴﺮ‬4-3-1-7
‫ﻃﻮر ﭘﻴﻮﺳﺘﻪ از ﻧﻘﻄﻪ ﻧﺎﻣﻲ ﺑﻪ ﻧﻘﻄﻪ ﻧﻮﺳﺎن ﭘﻴﺶ ﺑﻴﻨﻲ‬
‫ ﻛﻤﭙﺮﺳﻮر ﺑﺪون اﺳﺘﻔﺎده از ﺟﺮﻳﺎن‬.‫ﺷﺪه اﻓﺰاﻳﺶ ﻳﺎﺑﺪ‬
‫ ﺑﺮاي ﻋﻤﻠﻴﺎت ﭘﻴﻮﺳﺘﻪ در ﻫﺮ ﻇﺮﻓﻴﺖ ﺣﺪاﻗﻞ‬،‫ﻛﻨﺎرﮔﺬر‬
‫ درﺻﺪ ﺑﻴﺶ از ﻇﺮﻓﻴﺖ ﺗﻘﺮﻳﺒﻲ ﭘﻴﺶ ﺑﻴﻨﻲ ﺷﺪه‬10
.‫ ﻣﻨﺎﺳﺐ ﺑﺎﺷﺪ‬، ‫ﻧﻮﺳﺎن ﭘﻴﺸﻨﻬﺎدي‬
‫ درﺻﺪ‬±4 ‫ﻇﺮﻓﻴﺖ ﺑﺎ درك اﻳﻦ ﻛﻪ ﺗﻮان ﻣﻤﻜﻦ اﺳﺖ‬
.‫ ﺑﺎﻳﺪ ﺗﻀﻤﻴﻦ ﺷﻮﻧﺪ‬،‫ﺗﻐﻴﻴﺮ ﻛﻨﺪ‬
7.1.3.5 For constant-speed compressors, the
specified capacity shall be guaranteed with the
understanding that the head shall be within ±5%
and -0% of that specified; the power shall not
exceed stated power by more than 4%. These
tolerances are not additive.
‫ ﻇﺮﻓﻴﺖ‬،‫ ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي دور ﺛﺎﺑﺖ‬5-3-1-7
‫ درﺻﺪ و‬±5 ‫ﻣﺸﺨﺺ ﺑﺎ درك اﻳﻦ ﻛﻪ ارﺗﻔﺎع ﺑﺎﻳﺪ ﺑﻴﻦ‬
‫ﺻﻔﺮ درﺻﺪ ﻣﻘﺪار ﻣﺸﺨﺺ ﺑﺎﺷﺪ ﺑﺎﻳﺪ ﺗﻀﻤﻴﻦ ﺷﻮد؛ ﺗﻮان‬
.‫ درﺻﺪ ﺗﻮان ﻣﺸﺨﺺ ﺷﺪه اﻓﺰاﻳﺶ ﻳﺎﺑﺪ‬4 ‫ﻧﺒﺎﻳﺪ ﺑﻴﺶ از‬
.‫اﻳﻦ رواداريﻫﺎ ﻗﺎﺑﻞ اﻓﺰاﻳﺶ ﻧﻴﺴﺘﻨﺪ‬
7.1.4 The compressor manufacturer shall be
responsible for checking the "k" (ratio of specific
heats) and "Z" (compressibility factor) values
specified against the gas analysis specified.
‫ ﺳﺎزﻧﺪه ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﺟﻮاﺑﮕﻮ و ﻣﺴﺌﻮل ﺑﺮاي‬4-1-7
‫" )ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي‬k" ‫ﺑﺮرﺳﻲ ﻣﻘﺎدﻳﺮ ﻣﺸﺨﺺ ﺷﺪه‬
‫" )ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي( در ﻗﺒﺎل آﻧﺎﻟﻴﺰ‬Z" ‫وﻳﮋه( و‬
.‫ﻣﺸﺨﺺ ﮔﺎز ﺑﺎﺷﺪ‬
7.1.5 Compressor mach numbers shall not exceed
0.90 when measured at any point.
‫ ﻋﺪد ﻣﺎخ ﻛﻤﭙﺮﺳﻮر در ﻫﺮ ﻧﻘﻄﻪ ﻛﻪ اﻧﺪازه‬5-1-7
.‫ ﺗﺠﺎوز ﻧﻤﺎﻳﺪ‬0/9 ‫ﮔﻴﺮي ﻣﻲ ﺷﻮد ﻧﺒﺎﻳﺪ از‬
‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-7
7.2 Design Criteria
7.2.1 This Section of Standard covers
information necessary to select centrifugal
compressors and to determine whether the
selected machine should be considered for a
specific job.
‫ اﻳﻦ ﺑﺨﺶ از اﺳﺘﺎﻧﺪارد اﻃﻼﻋﺎت ﻻزم را ﺑﺮاي‬1-2-7
7.2.2 An approximate idea of the flow range that
a centrifugal compressor will handle is shown in
Table 1. A multistage centrifugal compressor is
normally considered for inlet volumes between
850 and 340,000 Im³/h. A single stage
compressor would normally have applications
between 170 and 255,000 Im³/h. A multi-stage
compressor can be thought of as series of single
stage compressors contained in a single casing.
‫ ﻳﻚ اﻳﺪه ﺗﻘﺮﻳﺒﻲ ﺑﺮاي ﻣﺤﺪوده ﺟﺮﻳﺎﻧﻲ ﻛﻪ‬2-2-7
‫ ﻧﺸﺎن‬1 ‫ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺗﺤﻤﻞ ﻣﻴﻜﻨﺪ در ﺟﺪول‬
‫ ﻋﻤﻮﻣﺎً ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﭼﻨﺪ‬.‫داده ﺷﺪه اﺳﺖ‬
340000 ‫ ﺗﺎ‬850 ‫ﻣﺮﺣﻠﻪاي ﺑﺮاي ﺣﺠﻢﻫﺎي ورودي‬
،‫ﻣﺘﺮﻣﻜﻌﺐ ورودي در ﺳﺎﻋﺖ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﻲ ﺷﻮﻧﺪ‬
170 ‫ﻛﻤﭙﺮﺳﻮر ﻳﻚ ﻣﺮﺣﻠﻪ اي ﻣﻌﻤﻮﻻً ﺑﺮاي ﺣﺠﻢ ﻫﺎي‬
‫ ﻣﺘﺮﻣﻜﻌﺐ ورودي در ﺳﺎﻋﺖ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬255000 ‫ﺗﺎ‬
‫ﻛﻤﭙﺮﺳﻮر ﭼﻨﺪ ﻣﺮﺣﻠﻪاي ﻣﻴﺘﻮاﻧﺪ ﺑﻪ ﻋﻨﻮان ﻳﻚ‬.‫ﻣﻲ ﺷﻮد‬
‫ﺳﺮي از ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺗﻚ ﻣﺮﺣﻠﻪاي ﻛﻪ در ﻳﻚ ﭘﻮﺳﺘﻪ‬
.‫ ﺗﺼﻮر ﺷﻮد‬،‫ﻗﺮار دارﻧﺪ‬
‫اﻧﺘﺨﺎب ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ و ﺗﻌﻴﻴﻦ اﻳﻦ ﻛﻪ آﻳﺎ‬
‫دﺳﺘﮕﺎه اﻧﺘﺨﺎب ﺷﺪه ﺑﺮاي ﻛﺎر ﺗﻌﻴﻴﻦ ﺷﺪه ﺗﻮﺻﻴﻪ ﺷﺪه‬
.‫ را ﭘﻮﺷﺶ ﻣﻴﺪﻫﺪ‬،‫اﺳﺖ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
TABLE 1 – CENTRIFUGAL COMPRESSOR FLOW RANGE
‫ ﻣﺤﺪوده ﺟﺮﻳﺎن ﻛﻤﭙﺮﺳﻮر ﭼﻨﺪ ﻣﺮﺣﻠﻪاي‬-1 ‫ﺟﺪول‬
SPEED TO DEVELOP
3048 m HEAD/WHEEL
‫ ﻣﺘﺮ‬3048 ‫ﺳﺮﻋﺖ ﺑﺮاي ﺗﻮﻟﻴﺪ‬
AVERAGE ISENTROPIC
EFFICIENCY
AVERAGE POLYTROPIC
EFFICIENCY
NOMINAL FLOW RANGE
(INLET m³/h)
‫ﻣﻴﺎﻧﮕﻴﻦ ﺑﺎزده اﻳﺰوﻧﺘﺮوﭘﻴﻚ‬
‫ﻣﻴﺎﻧﮕﻴﻦ ﺑﺎزده ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
‫ﻣﺤﺪوده ﺟﺮﻳﺎن اﺳﻤﻲ‬
0.63
0.74
0.77
0.77
0.77
0.77
0.77
0.77
0.77
0.60
0.70
0.73
0.73
0.73
0.73
0.73
0.73
0.73
‫ﻣﺤﻮر‬/‫ارﺗﻔﺎع‬
170 - 850
850 - 12,743
12,743 - 34,000
34,000 - 56,000
56,000 - 93,400
93,400 - 135,900
135,900 - 195,400
195,400 - 246,400
246,400 - 340,000
7.2.3 Effect of speed
‫ اﺛﺮ ﺳﺮﻋﺖ‬3-2-7
7.2.3.1 With variable speed, the centrifugal
compressor can deliver constant capacity at
variable pressure, variable capacity at constant
pressure, or a combination of variable capacity
and variable pressure.
‫ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﻣﻴﺘﻮاﻧﺪ‬،‫ ﺑﺎ دور ﻣﺘﻐﻴﺮ‬1-3-2-7
،‫ ﻇﺮﻓﻴﺖ ﻣﺘﻐﻴﺮ در ﻓﺸﺎر ﺛﺎﺑﺖ‬،‫ﻇﺮﻓﻴﺖ ﺛﺎﺑﺖ در ﻓﺸﺎر ﻣﺘﻐﻴﺮ‬
.‫ﻳﺎ ﺗﺮﻛﻴﺒﻲ از ﻇﺮﻓﻴﺖ ﻣﺘﻐﻴﺮ و ﻓﺸﺎر ﻣﺘﻐﻴﺮ اراﺋﻪ ﻛﻨﺪ‬
7.2.3.2 Basically, the performance of the
centrifugal compressor, at speeds other than
design, follows the affinity (or fan) laws.
‫ در‬،‫ ﻛﺎرآﻳﻲ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬،ً‫ اﺳﺎﺳﺎ‬2-3-2-7
7.2.3.3 By varying speed, the centrifugal
compressor will meet any load and pressure
condition demanded by the process system
within the operating limits of the compressor
and the driver.
‫ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﻫﺮ‬،‫ ﺑﺎ ﺗﻐﻴﻴﺮ ﺳﺮﻋﺖ‬3-3-2-7
7.2.3.4 If speed is constant then Characteristic
operating curve will be also constant. The
following factors will increase suction pressure
resulting in change of discharge pressure:
‫ اﮔﺮ ﺳﺮﻋﺖ ﺛﺎﺑﺖ ﺑﺎﺷﺪ آﻧﮕﺎه ﻣﻨﺤﻨﻲ ﻣﺸﺨﺼﻪ‬4-3-2-7
‫ﺳﺮﻋﺘﻬﺎي ﻏﻴﺮ از ﺳﺮﻋﺖ ﻃﺮاﺣﻲ از ﻗﻮاﻧﻴﻦ ﺗﺮﻛﻴﺒﻲ )ﻳﺎ‬
.‫ﺑﺎدزن( ﭘﻴﺮوي ﻣﻲ ﻛﻨﺪ‬
‫ﺷﺮاﻳﻂ ﺑﺎر و ﻓﺸﺎري را در ﻣﺤﺪوده ﻋﻤﻠﻴﺎﺗﻲ ﻛﻤﭙﺮﺳﻮر و‬
‫ﻣﺤﺮك ﻛﻪ ﺗﻮﺳﻂ ﺳﺎﻣﺎﻧﻪ ﻓﺮآﻳﻨﺪي ﻻزم ﺑﺎﺷﺪ ﭘﻮﺷﺶ‬
.‫ﻣﻴﺪﻫﺪ‬
‫ ﻋﻮاﻣﻞ زﻳﺮ ﻓﺸﺎر ﻣﻜﺶ را ﺑﺎ‬.‫ﻋﻤﻠﻴﺎﺗﻲ ﻧﻴﺰ ﺛﺎﺑﺖ ﻣﻲ ﻣﺎﻧﺪ‬
.‫ﺗﻐﻴﻴﺮ در ﻓﺸﺎر ﺧﺮوﺟﻲ زﻳﺎد ﻣﻲ ﻛﻨﺪ‬
‫اﻟﻒ( اﻓﺰاﻳﺶ ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ ﮔﺎز‬
a) Molecular weight of gas increases
b) Suction pressure increases
‫ب( اﻓﺰاﻳﺶ ﻓﺸﺎر ﻣﻜﺶ‬
c) Inlet temperature decreases
‫ج( ﻛﺎﻫﺶ دﻣﺎي ورودي‬
‫د( ﻛﺎﻫﺶ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬
d) Compressibility factor decreases
k ‫ﻫ( ﻛﺎﻫﺶ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬
e) Ratio of specific heats, k decreases
20,500
10,500
8,200
6,500
4,900
4,300
3,600
2,800
2,500
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
7.2.4 Performance calculation
7.2.4.1
Determination
pertaining to compression
of
‫ ﻣﺤﺎﺳﺒﻪ ﻛﺎرآﻳﻲ‬4-2-7
properties
‫ ﺗﻌﻴﻴﻦ ﺧﻮاص ﻣﺮﺑﻮط ﺑﻪ ﺗﺮاﻛﻢ‬1-4-2-7
‫ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬،(Z ‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي )ﺿﺮﻳﺐ‬
‫( و ﺟﺮم ﻣﻠﻜﻮﻟﻲ ﺳﻪ ﺧﺎﺻﻴﺖ ﻓﻴﺰﻳﻜﻲ اﺻﻠﻲ‬k ‫ ﻳﺎ‬Cp/Cv)
.‫ﺑﺮاي ﻛﻤﭙﺮﺳﻮر ﻫﺴﺘﻨﺪ ﻛﻪ ﺑﺎﻳﺪ ﻣﺸﺨﺺ ﮔﺮدﻧﺪ‬
Compressibility factor (Z factor), ratio of
specific heats (Cp/Cv or k value) and molecular
mass are three major physical properties for
compressor which must be clarified.
‫ ﺗﻌﻴﻴﻦ ﺷﺮاﻳﻂ ﻣﻜﺶ‬2-4-2-7
7.2.4.2 Determination of suction conditions
The following conditions at the suction flange
should be determined:
‫ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﺷﺮاﻳﻂ زﻳﺮ در ﻓﻠﻨﺞ ﻣﻜﺶ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬
:‫ﺷﻮد‬
a) Temperature
‫اﻟﻒ( دﻣﺎ‬
b) Pressure
‫ب ( ﻓﺸﺎر‬
In case of air taken from atmosphere,
corrections should be made for elevation. Air
humidity should also be considered.
‫ اﺻﻼﺣﺎﺗﻲ ﺑﺎﻳﺪ‬،‫در ﺣﺎﻟﺖ درﻳﺎﻓﺖ ﻫﻮا از ﻣﺤﻴﻂ‬
‫ ﺗﻮﺻﻴﻪ‬.‫ﺑﺮاﺳﺎس ارﺗﻔﺎع از ﺳﻄﺢ درﻳﺎ اﻧﺠﺎم ﺷﻮد‬
.‫ﻣﻴﺸﻮد رﻃﻮﺑﺖ ﻫﻮا ﻧﻴﺰ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﻮد‬
c) Flow rate
‫ج ( ﻣﻴﺰان ﺟﺮﻳﺎن‬
‫ﺗﻤﺎم ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺑﺮاﺳﺎس ﺟﺮﻳﺎﻧﻬﺎﻳﻲ‬
‫ﻛﻪ ﺑﻪ ﺷﺮاﻳﻂ ورودي ﻳﺎ ﺣﻘﻴﻘﻲ ﺗﺒﺪﻳﻞ ﺷﺪهاﻧﺪ‬
‫ ﻳﺎ ﻣﺘﺮ ﻣﻜﻌﺐ ورودي ﺑﺮ ﺳﺎﻋﺖ( ﻣﻲ ﺑﺎﺷﻨﺪ و‬Im³/h)
‫ﺑﻪ اﻳﻦ دﻟﻴﻞ اﻧﺠﺎم ﻣﻲ ﺷﻮد ﻛﻪ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از‬
‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ )ﻳﻌﻨﻲ ﻓﺸﺎر‬،‫ﻣﺮﻛﺰ ﺑﻪ ﺣﺠﻢ ورودي‬
‫ دﻳﺪه‬7-2-6 ‫ﻣﻌﺎدل ارﺗﻔﺎع( و ﺳﺮﻋﺖ ﻣﺸﺨﺼﻪ )ﺑﻨﺪ‬
.‫ﺷﻮد( ﺣﺴﺎس ﻫﺴﺘﻨﺪ‬
All centrifugal compressors are based on
flows that are converted to inlet or actual
conditions (Im³/h or inlet cubic meters per
hour). This is done because centrifugal
compressor is sensitive to inlet volume,
compression ratio (i.e., head) and specific
speed (see 6.2.7).
d) Fluctuation in conditions
‫د ( ﻧﻮﺳﺎن در ﺷﺮاﻳﻂ‬
Since fluctuations in inlet conditions will
have large effects on the centrifugal
compressor performance, owing to the
compressibility of the fluid, all conceivable
condition fluctuations must be taken into
consideration in determination of design
conditions.
‫از آﻧﺠﺎﻳﻲ ﻛﻪ ﻧﻮﺳﺎن در ﺷﺮاﻳﻂ ورودي اﺛﺮ زﻳﺎدي‬
‫ ﺑﻪ ﺧﺎﻃﺮ‬،‫روي ﻛﺎرآﻳﻲ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ دارد‬
‫ﺗﺮاﻛﻢ ﭘﺬﻳﺮ ﺑﻮدن ﺳﻴﺎل ﺑﻬﺘﺮ اﺳﺖ در ﺗﻌﻴﻴﻦ ﺷﺮاﻳﻂ‬
‫ﻃﺮاﺣﻲ ﺗﻤﺎم ﺷﺮاﻳﻂ ﻗﺎﺑﻞ ﺗﺼﻮر ﻧﻮﺳﺎن در ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬
.‫ﺷﻮﻧﺪ‬
7.2.4.3 Determination of discharge conditions
‫ ﺗﻌﻴﻴﻦ ﺷﺮاﻳﻂ ﺧﺮوﺟﻲ‬3-4-2-7
7.2.4.3.1 Calculation method
‫ روش ﻣﺤﺎﺳﺒﻪ‬1-3-4-2-7
Discharge conditions of a centrifugal
compressor can be calculated by the following
procedure.
‫ﺷﺮاﻳﻂ ﺧﺮوﺟﻲ ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺗﻮﺳﻂ دﺳﺘﻮراﻟﻌﻤﻞ‬
:‫زﻳﺮ ﻣﻴﺘﻮاﻧﺪ ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬
"n" ‫اﻟﻒ( ﻣﺤﺎﺳﺒﻪ ﻧﻤﺎي ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
a) Calculate the polytropic exponent "n":
1) Using the equation:
:‫( ﺑﺎ اﺳﺘﻔﺎده از ﻣﻌﺎدﻟﻪ‬1
14
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
n
k

 P
n 1 k 1
(Eq. 1)
(1 ‫)ﻣﻌﺎدﻟﻪ‬
if  p (polytropic efficiency) is known
from the manufacturer data.
‫ )ﺑﺎزده ﭘﻠﻲ ﺗﺮوﭘﻴﻚ( از اﻃﻼﻋﺎت‬ p ‫اﮔﺮ‬
 p can also be estimated from Table1
k) ‫ ﻗﺎﺑﻞ ﺗﺨﻤﻴﻦ اﺳﺖ‬1 ‫ ﻫﻤﭽﻨﻴﻦ از ﺟﺪول‬ p
.‫ﺳﺎزﻧﺪه ﻣﻌﻠﻮم ﺑﺎﺷﺪ‬
(k is the ratio of specific heats).
2)
.(‫ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه اﺳﺖ‬
‫ )ﺑﺎزده اﻳﺰﻧﺘﺮوﭘﻴﻚ ﻳﺎ ﺑﻲ دررو( ﻣﻌﻠﻮم‬is ‫( اﮔﺮ‬2
if  is (isentropic or adiabatic
efficiency) is known, then  p can be
found from Figs. 1 or 2 and the
Equation 1 can be used to calculate
"n".
‫ ﺑﺪﺳﺖ‬2 ‫ ﻳﺎ‬1 ‫ از ﺷﻜﻠﻬﺎي‬ p ‫ آﻧﮕﺎه‬،‫ﺑﺎﺷﺪ‬
‫ ﺑﺮاي ﻣﺤﺎﺳﺒﻪ‬1 ‫ﻣﻲآﻳﺪ و ﻣﻲﺗﻮان از ﻣﻌﺎدﻟﻪ‬
.‫" اﺳﺘﻔﺎده ﻛﺮد‬n"
3) Fig. 3 is useful for rough estimation of
"n".
.‫" ﻛﺎرﺑﺮد دارد‬n" ‫ ﺑﺮاي ﺗﺨﻤﻴﻦ ﺗﻘﺮﻳﺒﻲ‬3 ‫( ﺷﻜﻞ‬3
4) "n" can also be calculated iteratively
from equation:
‫" ﻫﻤﭽﻨﻴﻦ ﺑﻪ ﺻﻮرت ﺗﻜﺮاري از ﻣﻌﺎدﻟﻪ زﻳﺮ‬n" (4
(Eq. 2)
n
:‫ﻣﺤﺎﺳﺒﻪ ﻣﻴﺸﻮد‬
log10 ( P2 / P1 )
log10 (V1 / V2 )
(2 ‫)ﻣﻌﺎدﻟﻪ‬
‫ ﺣﺠﻢﻫﺎي ﻣﺨﺼﻮص )ﺣﻘﻴﻘﻲ( و‬V2 ‫ و‬V1 ‫ﻛﻪ‬
‫ ﺑﻪ ﺗﺮﺗﻴﺐ ﻓﺸﺎر ﻣﻄﻠﻖ در ﺷﺮاﻳﻂ‬P2 ‫ و‬P1
.‫ورودي و ﺧﺮوﺟﻲ ﻫﺴﺘﻨﺪ‬
Where V1 and V2 are specific volumes
(actual) and P1 and P2 are absolute
pressures at inlet and outlet conditions
respectively.
‫ﺑﺎزده ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬ P ‫ﻧﺴﺒﺖ ﻛﻤﭙﺮﺳﻮر‬
Fig. 1-EFFICIENCY CONVERSION
‫ ﺗﺒﺪﻳﻞ ﺑﺎزده‬-1 ‫ﺷﻜﻞ‬
15
% ‫ﺑﺎزده اﻳﺰوﻧﺘﺮوﭘﻴﻚ‬
‫‪ ‬ﺑﻬﻤﻦ ‪Feb. 2010/ 1388‬‬
‫)‪IPS-E-PR-750(1‬‬
‫راﻧﺪﻣﺎن ﺑﻲ دررو‬
‫ــــــــــــــــــ‬
‫راﻧﺪﻣﺎن ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
‫‪ ‬‬
‫‪ ‬‬
‫= ﻧﺴﺒﺖ‬
‫راﻧﺪﻣﺎن ﭘﻠﻲ ﺗﺮوﭘﻴﻚ ‪ ‬‬
‫‪Fig. 2-RELATIONSHIP BETWEEN ADIABATIC AND POLYTROPIC EFFICIENCIES‬‬
‫ﺷﻜﻞ ‪ -2‬راﺑﻄﻪ ﺑﻴﻦ راﻧﺪﻣﺎن ﻫﺎي ﺑﻲ دررو و ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
‫ﻧــﺴﺒﺖ ﮔﺮﻣﺎﻫــﺎي وﻳــﮋه ﺑــﺮاي ﮔﺎزﻫــﺎي ﻣــﻮرد‬
‫اﺳﺘﻔﺎده ﻣﺘﺪاول‬
‫ﻫﻮا‬
‫‪1.406‬‬
‫‪1.401‬‬
‫اﻛﺴﻴﮋن‬
‫‪1.407‬‬
‫ﻧﻴﺘﺮوژن‬
‫ﺣﺠﻢ ﻣﻜﺶ‬
‫اﻳﺰوﻧﺘﺮوﭘﻴﻚ ﻳﺎ ﺧﻨﻚ ﻛﺮدن‬
‫دﻳﺎﻓﺮاﮔﻢ‬
‫‪1.306‬‬
‫‪1.189‬‬
‫‪1.150‬‬
‫‪1.100‬‬
‫‪1.110‬‬
‫‪1.300‬‬
‫‪1.270‬‬
‫‪p‬‬
‫‪v‬‬
‫ﻣﺘﺎن‬
‫اﺗﺎن‬
‫ﭘﺮوﭘﺎن‬
‫ﻧﺮﻣﺎل ﺑﻮﺗﺎن‬
‫اﻳﺰوﺑﻮﺗﺎن‬
‫دي اﻛﺴﻴﺪﻛﺮﺑﻦ‬
‫دي اﻛﺴﻴﺪﮔﻮﮔﺮد‬
‫‪C‬‬
‫‪C‬‬
‫= ‪Fig. 3- RATIO OF SPECIFIC HEATS, K‬‬
‫‪(n-1)/n VERSUS RATIO OF SPECIFIC HEATS‬‬
‫ﺷﻜﻞ ‪ -3‬ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬
‫‪p‬‬
‫‪v‬‬
‫‪n -1‬‬
‫‪n‬‬
‫‪C‬‬
‫‪C‬‬
‫=‪K‬‬
‫ﺑﺮﺣﺴﺐ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬
‫‪16‬‬
‫‪ ‬‬
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
This equation applies with good accuracy
for single wheels and the overall
multistage compressor.
‫اﻳﻦ ﻣﻌﺎدﻟﻪ ﺑﺮاي ﻣﺎﺷﻴﻨﻬﺎي ﺗﻚ ﻣﺮﺣﻠﻪاي و ﻛﻞ‬
.‫ﻛﻤﭙﺮﺳﻮر ﭼﻨﺪ ﻣﺮﺣﻠﻪاي ﺑﺎ دﻗﺖ ﺧﻮﺑﻲ ﺑﻜﺎر ﻣﻴﺮود‬
‫ )ﻛﻠﻮﻳﻦ( را از ﻣﻌﺎدﻟﻪ زﻳﺮ‬T2 ‫ب ( دﻣﺎي ﺧﺮوﺟﻲ‬
b) Calculate discharge temperature T2,
(kelvin) from equation:
:‫ﻣﺤﺎﺳﺒﻪ ﻛﻨﻴﺪ‬
T2 = T1 (P2 / P1) (n-1)/n
(Eq. 3)
(3 ‫)ﻣﻌﺎدﻟﻪ‬
(‫ دﻣﺎﻫﺎي ﻣﻄﻠﻖ ﻫﺴﺘﻨﺪ‬T2 ‫ و‬T1)
(T1 and T2 are absolute temperatures)
These values are for polytropic
compression in an uncooled compressor
with no diaphragm cooling, no liquid
injection and no external coolers. In the
cases of internal cooling, the adiabatic
exponent "k" approximates the actual
condition.
‫اﻳﻦ ﻣﻘﺎدﻳﺮ ﺑﺮاي ﺗﺮاﻛﻢ ﭘﻠﻲ ﺗﺮوﭘﻴﻚ در‬
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺧﻨﻚ ﻧﺸﺪه ﺑﺪون ﺧﻨﻚ ﻛﺮدن‬
‫ ﺑﺪون ﺗﺰرﻳﻖ ﻣﺎﻳﻊ و ﺑﺪون ﺧﻨﻚ ﻛﻨﻨﺪه‬،‫دﻳﺎﻓﺮاﮔﻢ‬
‫ در ﺣﺎﻟﺖ ﺧﻨﻚ ﻛﺮدن‬.‫ﻫﺎي ﺧﺎرﺟﻲ ﻫﺴﺘﻨﺪ‬
‫" ﺗﺨﻤﻴﻨﻲ از ﺷﺮاﻳﻂ‬k" ‫ ﻧﻤﺎي ﺑﻲ دررو‬،‫داﺧﻠﻲ‬
.‫ﺣﻘﻴﻘﻲ ﻣﻲ ﺑﺎﺷﺪ‬
In such cases:
(Eq. 4)
:‫در ﭼﻨﺎن ﺷﺮاﻳﻄﻲ‬
 (k 1)/k 
 P2 
 1
 P 

 1 

ΔT  T1 
ηis
(4 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــﻪ‬
T
is the temperature increase, in
(°C).
(‫اﻓﺰاﻳﺶ دﻣﺎ ﺑﺮﺣﺴﺐ )درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬
T
.‫اﺳﺖ‬
Note:
:‫ﻳﺎدآوري‬
The operating temperature should not exceed
190°C (375°F) at any point in the operating
range, otherwise, difficulties will be encountered
in the mechanical design, higher temperatures up
to 232°C (450°F) are subject to Company’s
approval.
‫ﻫﺮ ﻧﻘﻄﻪ از ﻣﺤﺪوده‬
(‫ درﺟﻪ ﻓﺎرﻧﻬﺎﻳﺖ‬375)
‫ﻣﺸﻜﻼﺗﻲ در ﻃﺮاﺣﻲ‬
‫ درﺟﻪ‬232 ‫ﺑﺎﻻﺗﺮ ﺗﺎ‬
‫ﻣﻨﻮط ﺑﻪ ﺗﺄﻳﻴﺪ ﻛﺎرﻓﺮﻣﺎ‬
‫ راﺣﺴﺎب‬His (‫ج ( ارﺗﻔﺎع )ﻣﺘﺮ( ﺑﻲ دررو )آﻳﺰوﻧﺘﺮوﭘﻴﻚ‬
c) Calculate adiabatic (isentropic) head His
(meters):
(Eq. 5)
.‫ﻛﻨﻴﺪ‬
Z ave .R.T1
H is 
gM (k  1) / k
 P  ( k 1) / k 
 2 
 1
 P1 

Where:
‫ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد دﻣﺎي ﻋﻤﻠﻴﺎﺗﻲ در‬
‫ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬190 ‫ﻋﻤﻠﻴﺎﺗﻲ از‬
‫ در ﻏﻴﺮ اﻳﻨﺼﻮرت‬،‫ﺗﺠﺎوز ﻧﻨﻤﺎﻳﺪ‬
‫ دﻣﺎﻫﺎي‬،‫ﻣﻜﺎﻧﻴﻜﻲ اﻳﺠﺎد ﻣﻴﺸﻮد‬
(‫ درﺟﻪ ﻓﺎرﻧﻬﺎﻳﺖ‬450) ‫ﺳﺎﻧﺘﻴﮕﺮاد‬
.‫ﻣﻲ ﺑﺎﺷﺪ‬
(5 ‫)ﻣﻌﺎدﻟﻪ‬
:‫ﻛـــﻪ‬
17
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
‫ج‬ in
is gas constant,
J/kmol.K);
Zave
is average inlet and
compressibility factors;
outlet
‫ﻣﻴﺎﻧﮕﻴﻦ ﺿﺮاﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ورودي و‬
‫ﺧﺮوﺟﻲ؛‬
Zave
T1
is inlet absolute temperature,
kelvin (K);
‫(؛‬k) ‫دﻣﺎي ﻣﻄﻠﻖ ورودي ﻛﻠﻮﻳﻦ‬
T1
M
is molecular mass, (kg/kmol);
‫ ( ؛‬Kg
g
is acceleration
(9.80665 m/s²).
‫( ؛‬9/80665 m2 ) ‫ﺷﺘﺎب ﮔﺮاﻧﺶ‬
of
(8314.3
J
) ‫ﺛﺎﺑﺖ ﮔﺎز ﺑﺼﻮرت‬
kmol.K
R
(8314/35
gravity,
HP 
) ‫ﺟﺮم ﻣﻠﻜﻮﻟﻲ‬
M
g
S
:‫ را ﺣﺴﺎب ﻛﻨﻴﺪ‬Hp ‫د ( ارﺗﻔﺎع ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
d) Calculate polytropic head Hp:
(Eq. 6)
kmol
R
Z ave .R.T1  P2

gM (n  1) / n  P1

( n 1) / n




 1

(6 ‫)ﻣﻌﺎدﻟﻪ‬
Note:
:‫ﻳﺎدآوري‬
Polytropic and isentropic heads are related by:
(Eq. 7)
‫ارﺗﻔﺎعﻫﺎي ﭘﻠﻲﺗﺮوﭘﻴﻚ و اﻳﺰﻧﺘﺮوﭘﻴﻚ ﺑﺼﻮرت زﻳﺮ ﺑﺎﻫﻢ راﺑﻄﻪ‬
:‫دارﻧﺪ‬
H
H
P
is



P
(7 ‫)ﻣﻌﺎدﻟﻪ‬
is
e) Calculate gas horse power in kilowatt (hp):
‫ﻫـ( ﺗﻮان اﺳﺐ ﺑﺨﺎر ﮔﺎز را ﺑﺮﺣﺴﺐ ﻛﻴﻠﻮوات ﺣﺴﺎب‬
:(hp) ‫ﻛﻨﻴﺪ‬
.
Ghp = W HP
(Eq. 8)
(8 ‫)ﻣﻌﺎدﻟﻪ‬
6119.099ηP
or;
،‫ﻳﺎ‬
(Eq. 9)
W . His
Ghp =
6119.099ηis
(9 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛﻪ‬
W
is mass flow rate, (kg/min);
Hp
is polytropic head, (m).
W
.(m) ‫ارﺗﻔﺎع ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
Hp
:‫و ( ارﺗﻔﺎع را در ﻫﺮ ﻣﺮﺣﻠﻪ ﺗﺨﻤﻴﻦ ﺑﺰﻧﻴﺪ‬
f) Estimate head per stage:
‫( از ﻣﻌﺎدﻟﻪ زﻳﺮ ﻛﻪ ﺑﺮاﺳﺎس ﺟﺮم ﻣﻠﻜﻮﻟﻲ اﺳﺖ ﺑﺮاي‬1
‫ﻣﺤﺎﺳﺒﻪ ﺣﺪاﻛﺜﺮ ارﺗﻔﺎع در ﻫﺮ ﻣﺮﺣﻠﻪ اﺳﺘﻔﺎده‬
:‫ﻛﻨﻴﺪ‬
1) Use the following equation based on
molecular mass for calculation of
maximum head per stage:
‫(؛‬kg/min) ‫ﻣﻴﺰان ﺟﺮﻳﺎن ﺟﺮﻣﻲ‬
18
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
(Eq. 10)
Hmax/stage = 4572 - 457.2 (M)0.35
: ‫ را ﭘﻴﺪا ﻛﻨﻴﺪ‬SN ‫( ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺗﺼﺤﻴﺢ ﻧﺸﺪه‬2
2) Find uncorrected number of stages SN:
(Eq. 11)
SN 
(10 ‫)ﻣﻌﺎدﻟﻪ‬
HP
(11 ‫)ﻣﻌﺎدﻟﻪ‬
H max /stage
3) Correct number of stages by choosing
the next upper integer, S.
‫( ﺗﻌﺪاد ﻣﺮاﺣﻞ را ﺑﺎ اﻧﺘﺨﺎب ﻋﺪد ﺻﺤﻴﺢ ﺑﺰرﮔﺘﺮ‬3
.‫ﺑﻌﺪي اﺻﻼح ﻛﻨﻴﺪ‬
4) Find H’, the head per impeller:
:‫" ) ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع ﺑﺮﻫﺮ ﭘﺮه( را ﭘﻴﺪا ﻛﻨﻴﺪ‬H" (4
H’ = H P
S
(Eq. 12)
(12 ‫)ﻣﻌﺎدﻟﻪ‬
g) Estimate speed and wheel diameter:
:‫ز ( ﺳﺮﻋﺖ و ﻗﻄﺮ ﭼﺮخ را ﺗﺨﻤﻴﻦ ﺑﺰﻧﻴﺪ‬
1) Use Fig. 4 to find the size number;
‫ ﺑﺮاي ﭘﻴﺪا ﻛﺮدن ﻋﺪد اﻧﺪازه‬4 ‫( از ﺷﻜﻞ‬1
‫اﺳﺘﻔﺎده ﻛﻨﻴﺪ؛‬
2) Find the approximate wheel diameter,
D, from Table 2;
‫ ﭘﻴﺪا‬2 ‫" را از ﺟﺪول‬D" ‫( ﻗﻄﺮ ﺗﻘﺮﻳﺒﻲ ﭼﺮخ‬2
:‫ﻛﻨﻴﺪ‬
3) Choose pressure coefficient,  and
find peripheral velocity, u, from Fig.
5;
‫ را اﻧﺘﺨﺎب و ﺳﺮﻋﺖ ﻣﺤﻴﻄﻲ‬ ،‫( ﺿﺮﻳﺐ ﻓﺸﺎر‬3
.‫ ﭘﻴﺪا ﻛﻨﻴﺪ‬5 ‫" را از ﺷﻜﻞ‬U"
.‫ از ﻣﻌﺎدﻟﻪ زﻳﺮ ﺣﺴﺎب ﺷﻮد‬N (4
4) Calculate N from the equation.
(Eq. 13)
N
59809.42 H
D
μ
 19108.33  u/D
(13 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛــــﻪ‬
N = r/min (rpm)
Htotal
S
(‫ )دور ﺑﺮ دﻗﻴﻘﻪ‬N = r/min (rpm)
Is total compressor head (meters
of fluid);
‫ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع ﻛﻞ ﻛﻤﭙﺮﺳﻮر )ﻣﺘﺮ‬
Is No. of stages S, can also be
found by dividing Hp by H’;
S ‫ و ﻫﻤﭽﻨﻴـــــﻦ‬،‫ﺗﻌـﺪاد ﻣﺮاﺣﻞ اﺳﺖ‬
Htotal
‫ﺳﻴﺎل(؛‬
‫ ﺑﻪ‬H’ ‫ﺑﻪ‬
S
Hp ‫ﻣﻲ ﺗﻮاﻧﺪ از ﺗﻘﺴﻴﻢ‬
.‫دﺳﺖ ﻣﻲآﻳﺪ‬
D
Is impeller diameter, (mm);
H’
Is head per stage, (meters of
fluid);
µ(mu)
Is pressure coefficient, values
range from 0.5 to 0.6 (average
0.55, use Fig. 5);
‫ﻗﻄﺮ ﭘﺮواﻧﻪ )ﻣﻴﻠﻴﻤﺘﺮ(؛‬
‫ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع در ﻫﺮ ﻣﺮﺣﻠﻪ )ﻣﺘﺮﺳﻴﺎل(؛‬
0/6 ‫ ﺗﺎ‬0/5 ‫ ﻣﺤﺪوده ﺑﻴﻦ‬،‫ﺿﺮﻳﺐ ﻓﺸﺎر‬
‫ اﺳﺘﻔﺎده‬5 ‫از ﺷﻜﻞ‬، 0/55 ‫)ﻣﻴﺎﻧﮕﻴﻦ‬
(‫ﻛﻨﻴﺪ؛‬
19
D
H’
µ(mu)
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
u
.(m/s)‫ﺳﺮﻋﺖ ﭘﻴﺮاﻣﻮﻧﻲ‬
is peripheral velocity, (m/s).
TABLE 2 - APPROXIMATE WHEEL DIAMETER vs SIZE NUMBER
‫ ﻗﻄﺮ ﺗﻘﺮﻳﺒﻲ ﭼﺮخ ﺑﺮﺣﺴﺐ ﺷﻤﺎره اﻧﺪازه‬-2 ‫ﺟﺪول‬
Size No.
‫ﺷﻤﺎره اﻧﺪازه‬
Wheel diameter
(mm)
1
2
3
4
5
6
7
375
450
600
800
1060
1350
1650
‫اﻧﺪازه ﻛﻤﭙﺮﺳﻮر‬
‫ﻗﻄﺮ ﭼﺮخ‬
(‫)ﻣﻴﻠﻴﻤﺘﺮ‬
Fig. 4-CENTRIFUGAL COMPRESSOR SIZE vs CAPACITY
‫ اﻧﺪازه ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺑﺮﺣﺴﺐ ﻇﺮﻓﻴﺖ‬-4 ‫ﺷﻜﻞ‬
‫ﻣﻴﺎﻧﮕﻴﻦ‬
" µ"‫ﻋﺎﻣﻞ‬
Fig. 5-PERIPHERAL VELOCITY (m/s)
( m ) ‫ ﺳﺮﻋﺖ ﭘﻴﺮاﻣﻮﻧﻲ‬-5 ‫ﺷﻜﻞ‬
s
20
u
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
h) Brake horse power (in kilowatt):
:(‫ح( ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي)ﺑﺮﺣﺴﺐ ﻛﻴﻠﻮوات‬
Is determined by addition of power
losses due to friction in bearings, seals
and speed increasing gears to the gas
horse power in kilowatts (Ghp). The
equation:
(Eq. 14)
‫ﺑﺎ اﻓﺰودن ﺗﻮانﻫﺎي اﺗﻼﻓﻲ ﺑﻪ ﺧﺎﻃﺮ اﺻﻄﻜﺎك در‬
‫ ﻧﺸﺖ ﺑﻨﺪﻫﺎ و دﻧﺪهﻫﺎي اﻓﺰاﻳﻨﺪه‬،‫ﺑﻠﺒﺮﻳﻨﮓﻫﺎ‬
‫( ﻣﺤﺎﺳﺒﻪ‬Ghp) ‫ﺳﺮﻋﺖ ﺑﻪ ﺗﻮان اﺳﺐ ﺑﺨﺎر ﮔﺎز‬
:‫ﻣﻴﺸﻮد‬
Mechanical losses = 0.663 (Ghp) 0.4
is a good estimation for these losses.
(Eq. 15)
‫( اﺗﻼف ﻣﻜﺎﻧﻴﻜﻲ‬14 ‫)ﻣﻌﺎدﻟﻪ‬
‫ ﺗﻘﺮﻳﺐ ﺧﻮﺑﻲ ﺑﺮاي اﻳﻦ اﺗﻼف ﻫﺎ‬14 ‫ﻣﻌﺎدﻟﻪ‬
.‫اﺳﺖ‬
Bhp = hp + mechanical losses
(15 ‫)ﻣﻌﺎدﻟﻪ‬
P-H ‫ روش ﻧﻤﻮدار‬2-3-4-2-7
7.2.4.3.2 P-H diagram method
The use of an enthalpy diagram, when
available, is the most accurate and an easy
method for determining power. Fig. 7
represents a section of a typical P-H diagram.
The following procedure should be followed:
starting from point 1 (inlet conditions), follow
the line of constant entropy to the required
discharge pressure P2, locating the isentropic
discharge state point (2is). Now the differential
isentropic enthalpy can be calculated from:
‫ روش ﺑﺴﻴﺎر‬،‫ درﺻﻮرت وﺟﻮد‬،‫اﺳﺘﻔﺎده از ﻧﻤﻮدار آﻧﺘﺎﻟﭙﻲ‬
‫ ﺑﺨﺸﻲ از‬7 ‫ ﺷﻜﻞ‬.‫دﻗﻴﻖ و آﺳﺎن ﺑﺮاي ﺗﻌﻴﻴﻦ ﺗﻮان اﺳﺖ‬
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد‬.‫ را ﻧﺸﺎن ﻣﻴﺪﻫﺪ‬P-H ‫ﻧﻤﻮدار ﻧﻤﻮﻧﻪ‬
‫ ﺷﺮوع ﻧﻤﻮده‬1 ‫ از ﻧﻘﻄﻪ‬:‫دﺳﺘﻮراﻟﻌﻤﻞ زﻳﺮ دﻧﺒﺎل ﺷﻮد‬
‫)ﺷﺮاﻳﻂ ورودي( ﺧﻂ آﻧﺘﺮوﭘﻲ ﺛﺎﺑﺖ را دﻧﺒﺎل ﻛﺮده ﺗﺎ ﺑﻪ‬
‫ ﺣﺎﻟﺖ ﺧﺮوﺟﻲ‬2is ‫ ﻛﻪ در ﻧﻘﻄﻪ‬،‫ ﺑﺮﺳﻴﺪ‬P2 ‫ﻓﺸﺎر ﺧﺮوﺟﻲ‬
‫ اﺧﺘﻼف آﻧﺘﺎﻟﭙﻲ اﻳﺰﻧﺘﺮوﭘﻴﻚ از‬.‫آﻳﺰﻧﺘﺮوﭘﻴﻚ ﻣﻲ ﺑﺎﺷﺪ‬
:‫رواﺑﻂ زﻳﺮ ﻗﺎﺑﻞ ﻣﺤﺎﺳﺒﻪ اﺳﺖ‬
 his = h2is - h1
(Eq. 16)
‫ )ارﺗﻔﺎع اﻳﺰوﻧﺘﺮوﭘﻴﻚ( ﺑﻪ اﻳﻦ ﺻﻮرت ﺑــﻪ دﺳﺖ‬His ‫ﺳﭙﺲ‬
:‫ﻣﻲآﻳﺪ‬
His (isentropic head) can then be found:
(Eq. 17)
His =  his × 101.978 if h is in kJ/kg
From Eqs. 17, 7, 8 and 9:
:9 ‫ و‬8 ،7 ،17 ‫از ﻣﻌﺎدﻻت‬
 h = Δ his 
ηis
Δ hp
(18 ‫)ﻣﻌﺎدﻟﻪ‬
ηp
.‫ اﺧﺘﻼف آﻧﺘﺎﻟﭙﻲ ﺣﻘﻴﻘﻲ اﺳﺖ‬ ‫ﻛﻪ‬
Where  h is the actual differential enthalpy.
(17 ‫)ﻣﻌﺎدﻟﻪ‬
.‫ ﺑﺮﺣﺴﺐ ﻣﺘﺮ ﺳﻴﺎل اﺳﺖ‬His ‫ﻛﻪ‬
Where His is in meters of fluid.
(Eq. 18)
(16 ‫)ﻣﻌﺎدﻟﻪ‬
21
‫‪ ‬ﺑﻬﻤﻦ ‪Feb. 2010/ 1388‬‬
‫)‪IPS-E-PR-750(1‬‬
‫‪ ‬‬
‫‪ ‬‬
‫اﺗﻴﻠﻦ در ‪-150‬‬
‫ﺣﺪاﻗﻞ ﺗﻌﺪاد ﺗﻘﺮﻳﺒﻲ ﭼﺮخ ﻣﻮرد ﻧﻴﺎز‬
‫درﺟﻪ ﻓﺎرﻧﻬﺎﻳﺖ‬
‫ﻫﻮا و ﮔﺎز ﻃﺒﻴﻌﻲ‬
‫ارﺗﻔﺎع )‪ (m‬‬
‫‪Fig. 6-REQUIRED NUMBER OF WHEELS‬‬
‫ﺷﻜﻞ ‪ -6‬ﺗﻌﺪاد ﭼﺮﺧﻬﺎي ﻣﻮرد ﻧﻴﺎز‬
‫ﻧﻘﻄﻪ ﺑﺤﺮاﻧﻲ ‪ ‬‬
‫ﺧﻄﻮط‬
‫آﻧﺘﺮوﭘﻲ ﺛﺎﺑﺖ ‪ ‬‬
‫ﻓﺸﺎر ‪ ‬‬
‫آﻧﺘﺎﻟﭙﻲ ‪ ‬‬
‫‪Fig. 7-P-H DIAGRAM CONSTRUCTION‬‬
‫ﺷﻜﻞ ‪ -7‬ﺳﺎﺧﺘﺎر ﻧﻤﻮدار آﻧﺘﺎﻟﭙﻲ‪ ،‬ﻓﺸﺎر‬
‫ج‬
‫‪22‬‬
‫‪ ‬‬
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
To find the discharge enthalpy:
:‫ﺑﺮاي ﭘﻴﺪا ﻛﺮدن آﻧﺘﺎﻟﭙﻲ ﺧﺮوﺟﻲ‬
h2 
(Eq. 19)
Δ his
ηis
 h1
(19 ‫)ﻣﻌﺎدﻟﻪ‬
The actual discharge temperature can now be
obtained from the P-H diagram.
P-H ‫اﻛﻨﻮن دﻣﺎي واﻗﻌﻲ ﺧﺮوﺟﻲ واﻗﻌﻲ ﻣﻴﺘﻮاﻧﺪ از ﻧﻤﻮدار‬
7.2.5 Sonic or acoustic velocity, in any gas
may be calculated from:
‫ ﺳﺮﻋﺖ ﺻﻮت ﻳﺎ آﮔﻮﺳﺘﻴﻚ در ﻫﺮ ﮔﺎز ﻣﻴﺘﻮاﻧﺪ از‬5-2-7
.‫ﺑﻪ دﺳﺖ آﻳﺪ‬
:‫راﺑﻄﻪ زﻳﺮ ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬
VS  ( k.RM.T.Z )1 / 2
(Eq. 20)
(20 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛــــﻪ‬
Vs
Is in meters per second;
(‫ﺳﺮﻋﺖ ) ﻣﺘﺮ ﺑﺮ ﺛﺎﻧﻴﻪ؛‬
Vs
k
Is the ratio of specific heats;
‫ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه؛‬
k
T
Is suction absolute temperature
of gas, in (Kelvin);
‫دﻣﺎي ﻣﻄﻠﻖ ورودي ﮔﺎز )ﻛﻠﻮﻳﻦ(؛‬
T
. N.m/kmol. K 8314/3
R
R is 8314.3 N.m/kmol. K.
General design practice avoids using gas
velocities near or above the sonic velocity.
‫ اﺳﺘﻔﺎده از ﺳﺮﻋﺖ ﮔﺎز ﻧﺰدﻳﻚ ﻳﺎ ﺑﺎﻻي‬،‫ﺗﺠﺮﺑﻪ ﻛﻠﻲ ﻃﺮاﺣﻲ‬
.‫ﺳﺮﻋﺖ ﺻﻮت را ﻣﻨﻊ ﻣﻴﻜﻨﺪ‬
7.2.6 The ratio of gas velocity at any point to
the sonic velocity of the gas is known as "mach
number, (M’)".
‫ ﻧﺴﺒﺖ ﺳﺮﻋﺖ ﮔﺎز در ﻫﺮ ﻧﻘﻄﻪ ﺑﻪ ﺳﺮﻋﺖ ﺻﻮت‬6-2-7
(Eq. 21)
‫(" ﺷﻨﺎﺧﺘﻪ ﻣﻴﺸﻮد‬M) ‫ﮔﺎز ﺑﻪ ﻋﻨﻮان "ﻋﺪد ﻣﺎخ‬
(21 ‫)ﻣﻌﺎدﻟﻪ‬
M’ = u’/Vs
.‫ ﺳﺮﻋﺖ ﮔﺎز در ﻫﺮ ﻧﻘﻄﻪ اﺳﺖ‬u’ ‫ﻛﻪ‬
Where u’ is gas velocity at any point.
7.2.7 Specific speed
‫ ﺳﺮﻋﺖ وﻳﮋه‬7-2-7
At a given point, the "specific speed",
correlates the important performance factors of
adiabatic head, capacity and r/min for
geometrically similar wheels. The specific
speed of all geometrically similar wheels is the
same and does not change when the speed of
the wheel is changed.
(Eq. 22)
NS 
‫ "ﺳﺮﻋﺖ وﻳﮋه" ارﺗﺒﺎط ﺿﺮاﻳﺐ ﻣﻬﻢ‬،‫در ﻳﻚ ﻧﻘﻄﻪ ﻣﺸﺨﺺ‬
‫ ﻇﺮﻓﻴﺖ و دور ﺑﺮ دﻗﻴﻘﻪ را ﺑﺮاي‬،‫ ارﺗﻔﺎع آدﻳﺎﺑﺎﺗﻴﻚ‬،‫ﻛﺎراﻳﻲ‬
‫ ﺳﺮﻋﺖ‬.‫ﭼﺮﺧﻬﺎي ﻣﺸﺎﺑﻪ از ﻧﻈﺮ ﻫﻨﺪﺳﻲ را ﻧﺸﺎن ﻣﻲ دﻫﺪ‬
‫وﻳﮋه ﺗﻤﺎم ﭼﺮﺧﻬﺎي ﻣﺸﺎﺑﻪ از ﻧﻈﺮ ﻫﻨﺪﺳﻲ ﻳﻜﺴﺎن ﺑﻮده و ﺑﺎ‬
.‫ﺗﻐﻴﻴﺮ ﺳﺮﻋﺖ ﭼﺮخ ﺗﻐﻴﻴﺮ ﻧﻤﻲ ﻛﻨﺪ‬
0.315  r / min V1
( Ha) 0.75
(22 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛــــﻪ‬
Ns
Is specific speed, in r/min (rpm);
V1
Is flow rate, in m³/h at suction
condition;
‫(؛‬rpm) ‫ﺳﺮﻋﺖ وﻳﮋه ﺑﺮﺣﺴﺐ دور ﺑﺮ دﻗﻴﻘﻪ‬
‫ در ﺷﺮاﻳﻂ‬m³/h ‫ﻣﻴﺰان ﺟﺮﻳﺎن ﺑﺮﺣﺴﺐ‬
Ns
V1
‫ورودي؛‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
Ha
Is total adiabatic or polytropic
head, in meters;
r/min
Is actual speed of wheel.
‫ارﺗﻔﺎع ﻛﻞ ﺑﻲ دررو ﻳﺎ ﭘﻠﻲ ﺗﺮوﭘﻴﻚ ﺑﺮﺣﺴﺐ‬
‫ﻣﺘﺮ؛‬
Ha
.‫ ﺳﺮﻋﺖ ﺣﻘﻴﻘﻲ ﭼﺮخ‬r/min
Note:
:‫ﻳﺎدآوري‬
Centrifugal compressors usually have specific
speeds of 1500-3000 at the high efficiency
point.
-3000 ‫اﻛﺜﺮاً ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺳﺮﻋﺖ وﻳﮋه‬
.‫ در ﺑﺎﻻﺗﺮﻳﻦ ﻧﻘﻄﻪ ﺑﺎزده دارﻧﺪ‬1500
7.2.8 Flow limits
‫ ﻣﺤﺪوده ﻫﺎي ﺟﺮﻳﺎن‬8-2-7
Two conditions associated with centrifugal
compressors are surge (pumping) and stonewall (choked flow).
‫دو ﺣﺎﻟﺘﻲ ﻛﻪ ﺑﺎ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﻫﻤﺮاه ﻫﺴﺘﻨﺪ‬
(stone-wall) ‫( و ﺟﺮﻳﺎن اﺧﺘﻨﺎﻗﻲ‬Pumping) ‫ﻧﻮﺳﺎن‬
.‫ﻣﻲﺑﺎﺷﻨﺪ‬
7.2.8.1 Surge point
‫ ﻧﻘﻄﻪ ﻧﻮﺳﺎن‬1-8-2-7
At some point on the compressors operating
curve there exists a condition of minimum
flow/maximum head where the developed head
is insufficient to overcome the system
resistance. This is the "surge point". When the
compressor reaches this point, the gas in the
discharge piping back-flows into the
compressors. Without discharge flow, discharge
pressure drops until it is within the
compressor’s capability, only to repeat the
cycle. The repeated pressure oscillations at the
surge point should be avoided since it can be
detrimental to the compressor. Surging can
cause the compressor to overheat to the point
the maximum allowable temperature of the unit
is exceeded. Also, surging can cause damage to
the thrust bearing due to the rotor shifting back
and forth from the active to the inactive side.
‫در ﺑﺮﺧﻲ ﻧﻘﺎط در ﻣﻨﺤﻨﻲ ﻋﻤﻠﻴﺎﺗﻲ ﻛﻤﭙﺮﺳﻮر ﺷﺮاﻳﻂ‬
‫ﺣﺪاﻛﺜﺮ ارﺗﻔﺎع وﺟﻮد دارد ﻛﻪ ارﺗﻔﺎع ﺗﻮﻟﻴﺪ ﺷﺪه‬/‫ﺣﺪاﻗﻞ‬
‫ اﻳﻦ "ﻧﻘﻄﻪ‬.‫ﺑﺮاي ﻏﻠﺒﻪ ﺑﺮ ﻣﻘﺎوﻣﺖ ﺳﺎﻣﺎﻧﻪ ﻛﺎﻓﻲ ﻧﻤﻲ ﺑﺎﺷﺪ‬
،‫ زﻣﺎﻧﻲ ﻛﻪ ﻛﻤﭙﺮﺳﻮر ﺑﻪ اﻳﻦ ﻧﻘﻄﻪ ﻣﻲ رﺳﺪ‬.‫ﻧﻮﺳﺎن" اﺳﺖ‬
‫ ﺑﺪون‬.‫ﮔﺎز در ﻟﻮﻟﻪ ﻛﺸﻲ ﺧﺮوﺟﻲ ﺑﻪ ﻛﻤﭙﺮﺳﻮر ﺑﺮﻣﻴﮕﺮدد‬
‫ ﻓﺸﺎر ﺧﺮوﺟﻲ ﺗﺎ زﻣﺎﻧﻲ ﻛﻪ ﻛﻤﭙﺮﺳﻮر‬،‫ﺟﺮﻳﺎن ﺧﺮوﺟﻲ‬
‫ ﺗﻮﺻﻴﻪ‬.‫ اﻓﺖ ﺧﻮاﻫﺪ داﺷﺖ‬،‫ﺑﺘﻮاﻧﺪ ﭼﺮﺧﻪ را ﺗﻜﺮار ﻛﻨﺪ‬
‫ﻣﻴﺸﻮد از ﻧﻮﺳﺎن ﻓﺸﺎر در ﻧﻘﻄﻪ ﻧﻮﺳﺎن ﻣﻤﺎﻧﻌﺖ ﺷﻮد زﻳﺮا‬
‫ ﻧﻮﺳﺎن ﻣﻤﻜﻦ اﺳﺖ‬.‫ﻣﻤﻜﻦ اﺳﺖ ﺑﺮاي ﻛﻤﭙﺮﺳﻮر ﻣﻀﺮ ﺑﺎﺷﺪ‬
‫ﻣﻮﺟﺐ ﮔﺮم ﺷﺪن ﻛﻤﭙﺮﺳﻮر ﺑﻴﺶ از ﺣﺪاﻛﺜﺮ دﻣﺎي ﻣﺠﺎز‬
‫ ﻫﻤﭽﻨﻴﻦ ﻧﻮﺳﺎن ﻣﻴﺘﻮاﻧﺪ ﺑﻪ ﻳﺎﺗﺎﻗﺎن ﻣﺤﻮري ﺑﻪ‬.‫واﺣﺪ ﺷﻮد‬
‫ﺧﺎﻃﺮ ﺟﻠﻮ و ﻋﻘﺐ ﺷﺪن روﺗﻮر از ﺳﻤﺖ ﻓﻌﺎل ﺑﻪ ﻏﻴﺮﻓﻌﺎل‬
.‫آﺳﻴﺐ ﺑﺮﺳﺎﻧﺪ‬
7.2.8.2 Stone-Wall or choked flow
‫ ﭘﺪﻳﺪه دﻳﻮار ﺳﻨﮕﻲ ﻳﺎ ﺟﺮﻳﺎن اﺧﺘﻨﺎﻗﻲ‬2-8-2-7
Stone-wall-or choked flow occurs when sonic
velocity is reached at any point in the
compressor. When this point is reached for a
given gas, the flow through the compressor can
not be increased further without internal
modifications.
‫ﭘﺪﻳﺪه دﻳﻮار ﺳﻨﮕﻲ ﻳﺎ ﺟﺮﻳﺎن اﺧﺘﻨﺎﻗﻲ زﻣﺎﻧﻲ اﺗﻔﺎق ﻣﻴﺎﻓﺘﺪ‬
.‫ﻛﻪ ﺳﺮﻋﺖ در ﻫﺮ ﻧﻘﻄﻪ از ﻛﻤﭙﺮﺳﻮر ﺑﻪ ﺳﺮﻋﺖ ﺻﻮت ﺑﺮﺳﺪ‬
‫ ﺑﺪون اﺻﻼح‬،‫زﻣﺎﻧﻲ ﻛﻪ ﮔﺎز ﺑﻪ اﻳﻦ ﻧﻘﻄﻪ ﻣﺸﺨﺺ ﺑﺮﺳﺪ‬
.‫ ﺟﺮﻳﺎن در ﻛﻤﭙﺮﺳﻮر ﻧﻤﻴﺘﻮاﻧﺪ اﻓﺰاﻳﺶ ﻳﺎﺑﺪ‬،‫ﺳﺎﺧﺘﺎر داﺧﻠﻲ‬
7.2.9 Interstage cooling
‫ ﺧﻨﻚ ﻛﺮدن ﺑﻴﻦ ﻣﺮﺣﻠﻪ‬9-2-7
Multistage compressors rely on intercooling
whenever the inlet temperature of the gas and
the required compression ratio are such that the
discharge temperature of the gas exceeds about
‫در ﺻﻮرﺗﻲ ﻛﻪ دﻣﺎي ورودي ﮔﺎز و ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﻻزم‬
‫ درﺟﻪ‬150 ‫ﻣﻘﺪاري ﺑﺎﺷﺪ ﻛﻪ دﻣﺎي ﺧﺮوﺟﻲ ﮔﺎز از ﺣﺪود‬
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﭼﻨﺪ ﻣﺮﺣﻠﻪاي ﺑﻪ‬،‫ﺳﺎﻧﺘﻴﮕﺮاد ﺗﺠﺎوز ﻧﻤﺎﻳﺪ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
150°C. Performance calculations indicate that
the head and power are directly proportional to
the absolute gas temperature at each impeller.
‫ ﻣﺤﺎﺳﺒﺎت ﻛﺎراﻳﻲ ﻧﺸﺎن‬.‫ﺧﻨﻚ ﻛﺮدن داﺧﻠﻲ ﺗﻜﻴﻪ ﻣﻴﻜﻨﻨﺪ‬
‫داده ﻛﻪ ارﺗﻔﺎع و ﺗﻮان ﻧﺴﺒﺖ ﻣﺴﺘﻘﻴﻢ ﺑﺎ دﻣﺎي ﻣﻄﻠﻖ ﮔﺎز‬
.‫در ﻫﺮ ﭘﺮواﻧﻪ دارﻧﺪ‬
When interstage coolers are furnished, the
vender shall provide the following:
،‫زﻣﺎﻧﻲ ﻛﻪ ﺧﻨﻚ ﻛﻦ ﻫﺎي ﺑﻴﻦ ﻣﺮﺣﻠﻪ اي ﺗﻌﺒﻴﻪ ﺷﻮﻧﺪ‬
:‫ﻓﺮوﺷﻨﺪه ﺑﺎﻳﺪ ﻣﻮارد زﻳﺮ را ﻓﺮاﻫﻢ ﻛﻨﺪ‬
a. Drawing showing cooling system details
b. Data for purchasers heat and material
balances.
c. Details of provisions for separating and
withdrawing condensate .
.‫اﻟﻒ( ﻧﻘﺸﻪ ﻫﺎي ﻧﺸﺎﻧﮕﺮ ﺟﺰﺋﻴﺎت ﺳﺎﻣﺎﻧﻪ ﺧﻨﻚ ﻛﻨﻨﺪه‬
.‫ب( اﻃﻼﻋﺎت ﻣﻮازﻧﻪ ﺟﺮﻣﻲ و ﺣﺮارﺗﻲ ﺑﺮاي ﺧﺮﻳﺪاران‬
.‫ج( ﺟﺰﺋﻴﺎت ﺗﻤﻬﻴﺪات ﺟﺪاﺳﺎزي و ﺣﺬف ﻣﻴﻌﺎﻧﺎت‬
d. Vendor’s recommendations regarding
provision for support and piping expansion.
‫د( ﺗﻮﺻﻴﻪ ﻫﺎي ﻓﺮوﺷﻨﺪه ﺑﺮاي ﺗﻤﻬﻴﺪات ﻧﮕﻬﺪارﻧﺪه ﻫﺎ و‬
.‫اﻧﺒﺴﺎط ﻟﻮﻟﻪ ﻛﺸﻲ‬
7.2.10 Controls and instrumentation
‫ ﻛﻨﺘﺮل و ادوات اﺑﺰار دﻗﻴﻖ‬10-2-7
Compressor controls can vary from the very
basic manual recycle control to the elaborate
ratio controllers. The driver characteristics,
process response and compressor operating
range must be determined before the right
controls can be selected.
‫ﻛﻨﺘﺮلﻫﺎي ﻛﻤﭙﺮﺳﻮر ﻣﻴﺘﻮاﻧﺪ از ﻛﻨﺘﺮل ﺑﺴﻴﺎر اوﻟﻴﻪ ﺟﺮﻳﺎن‬
‫ﺑﺎزﮔﺸﺘﻲ ﺑﺼﻮرت دﺳﺘﻲ ﺗﺎ ﻛﻨﺘﺮلﻫﺎي دﻗﻴﻖ ﺗﻨﺎﺳﺒﻲ‬
‫ واﻛﻨﺶ ﻓﺮآﻳﻨﺪي و‬،‫ ﻣﺸﺨﺼﺎت ﮔﺮداﻧﻨﺪه‬.‫ﻣﺘﻔﺎوت ﺑﺎﺷﺪ‬
‫ﻣﺤﺪوده ﻋﻤﻠﻴﺎﺗﻲ ﻛﻤﭙﺮﺳﻮر ﺑﻬﺘﺮ اﺳﺖ ﻗﺒﻞ از اﻧﺘﺨﺎب‬
.‫روﺷﻬﺎي ﺻﺤﻴﺢ ﻛﻨﺘﺮل ﺗﻌﻴﻴﻦ ﺷﻮﻧﺪ‬
7.2.10.1 Control systems
‫ ﺳﺎﻣﺎﻧﻪ ﻫﺎي ﻛﻨﺘﺮل‬1-10-2-7
Control system shall be designed for start-up
operation, for all specified operating conditions,
and for surge prevention. The method of
control, the source of the control signal, its
sensitivity and range, and the equipment to be
furnished by vendor should be specified.
Compressor control may be accomplished by
suction throttling, variable inlet guide vanes,
variable stator vans, speed variation, a cooled
bypasss from discharge to suction, discharge
blowoff or discharge throttling.
‫ ﺑﺮاي ﺗﻤﺎم‬،‫ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل ﺑﺎﻳﺪ ﺑﺮاي ﻋﻤﻠﻴﺎت راه اﻧﺪازي‬
‫ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ ﻣﺸﺨﺺ و ﺑﺮاي ﻣﻤﺎﻧﻌﺖ از ﻧﻮﺳﺎن ﻃﺮاﺣﻲ‬
،‫ ﻣﻨﺒﻊ ﺳﻴﮕﻨﺎل ﻛﻨﺘﺮل‬،‫ ﺗﻮﺻﻴﻪ ﻣﻲ ﺷﻮد روش ﻛﻨﺘﺮل‬.‫ﺷﻮد‬
‫ﺣﺴﺎﺳﻴﺖ و داﻣﻨﻪ آن و ﺗﺠﻬﻴﺰي ﻛﻪ ﺗﻮﺳﻂ ﻓﺮوﺷﻨﺪه ﺗﻬﻴﻪ‬
‫ ﻛﻨﺘﺮل ﻛﻤﭙﺮﺳﻮر ﻣﻤﻜﻦ اﺳﺖ ﺑﺎ‬.‫ ﻣﺸﺨﺺ ﺷﻮد‬،‫ﻣﻲ ﺷﻮد‬
‫ ﭘﺮه ﻫﺎي‬،‫ ﭘﺮه ﻫﺎي ورودي ﻣﺘﻐﻴﺮ‬،‫ﺑﺴﺘﻦ ﺟﺰﺋﻲ ﻣﻜﺶ‬
‫ ﺟﺮﻳﺎن ﻛﻨﺎرﮔﺬر ﺧﻨﻚ‬،‫ ﺗﻐﻴﻴﺮات ﺳﺮﻋﺖ‬،‫ﻣﺘﻐﻴﺮ اﺳﺘﺎﺗﻮر‬
‫ ﺗﺨﻠﻴﻪ ﺧﺮوﺟﻲ ﺑﺎ ﺑﺴﺘﻦ ﺟﺰﺋﻲ‬،‫ﺷﺪه از ﺧﺮوﺟﻲ ﺑﻪ ﻣﻜﺶ‬
.‫ﺧﺮوﺟﻲ اﻧﺠﺎم ﺷﻮد‬
In cases where constant speed drivers are used,
the inlet gas density can be reduced by
throttling or by adjusting the compressor guide
vanes. Different features of the centrifugal
compressor control systems are described in
GPSA.
‫در ﺣﺎﻟﺘﻬﺎﻳﻲ ﻛﻪ از ﮔﺮداﻧﻨﺪه ﻫﺎي ﺳﺮﻋﺖ ﺛﺎﺑﺖ اﺳﺘﻔﺎده‬
-‫ ﭼﮕﺎﻟﻲ ﮔﺎز ورودي ﺑﺎ ﺑﺴﺘﻦ ﺟﺰﺋﻲ ﻳﺎ ﺗﻨﻈﻴﻢ ﭘﺮه‬،‫ﻣﻴﺸﻮﻧﺪ‬
‫ وﻳﮋﮔﻲﻫﺎي‬.‫ﻫﺎي راﻫﻨﻤﺎي ﻛﻤﭙﺮﺳﻮر ﻣﻴﻮاﻧﺪ ﻛﺎﻫﺶ ﻳﺎﺑﺪ‬
‫ﻣﺨﺘﻠﻒ ﺳﺎﻣﺎﻧﻪﻫﺎي ﻛﻨﺘﺮل ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ در‬
.‫ ﺗﺸﺮﻳﺢ ﺷﺪه اﺳﺖ‬GPSA
7.2.10.2 Instrumentation
All instruments shall be located and arranged to
permit easy visibility by the operators, as well
as accessibility for tests, adjustments, and
maintenance.
‫ ادوات اﺑﺰاردﻗﻴﻖ‬2-10-2-7
‫ﺗﻤﺎم ادوات اﺑﺰاردﻗﻴﻖ ﺑﺎﻳﺪ ﻃﻮري ﺗﻌﺒﻴﻪ و آراﻳﺶ ﺷﻮﻧﺪ ﻛﻪ‬
‫ﺑﻪ راﺣﺘﻲ ﺑﺮاي ﻣﺘﺼﺪي واﺣﺪ ﻗﺎﺑﻞ روﻳﺖ ﺑﻮده و ﻫﻤﭽﻨﻴﻦ‬
. ‫ ﺗﻨﻈﻴﻢ ﻳﺎ ﺗﻌﻤﻴﺮ را داﺷﺘﻪ ﺑﺎﺷﻨﺪ‬، ‫ﺗﻮاﻧﺎﻳﻲ آزﻣﺎﻳﺶ‬
Unless otherwise specified, all instruments
other than shut-down sensing devices shall be
‫ ﺗﻤﺎم ادوات اﺑﺰاردﻗﻴﻖ ﻏﻴﺮ از‬،‫ﺑﻪ ﻏﻴﺮ از ﻣﻮارد ﻣﺸﺨﺺ ﺷﺪه‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
installed with sufficient valving to permit their
replacement while the system is in operation.
When shut-off valves are specified for shutdown sensing devices, the vendor shall provide
a means of locking the valves in the open
position.
‫وﺳﺎﻳﻞ ﺗﺸﺨﻴﺺ ﺗﻮﻗﻒ ﺑﺎﻳﺪ ﺑﺎ ﺷﻴﺮﻫﺎي ﻣﻨﺎﺳﺐ ﺑﻪ ﮔﻮﻧﻪ اي‬
‫ﻧﺼﺐ ﺷﻮﻧﺪ ﻛﻪ ﺗﻌﻮﻳﺾ آﻧﻬﺎ در ﻃﻮل ﻋﻤﻠﻴﺎت ﺳﺎﻣﺎﻧﻪ ﻣﻴﺴﺮ‬
‫ زﻣﺎﻧﻲ ﻛﻪ ﺷﻴﺮﻫﺎي ﻗﻄﻊ ﺑﺮاي وﺳﺎﻳﻞ ﺗﺸﺨﻴﺺ ﺗﻮﻗﻒ‬.‫ﺑﺎﺷﺪ‬
‫ ﻓﺮوﺷﻨﺪه ﺑﺎﻳﺪ وﺳﺎﻳﻞ ﻗﻔﻞ ﻛﺮدن‬،‫ﻣﺸﺨﺺ ﻣﻲ ﺷﻮﻧﺪ‬
.‫ﺷﻴﺮﻫﺎ در وﺿﻌﻴﺖ ﺑﺎز را ﺗﺎﻣﻴﻦ ﻛﻨﺪ‬
Except for instrument air service, bleed valves
are required between instruments and their
isolation valves. Combination isolation/bleed
valves may be used.
‫ ﺷﻴﺮﻫﺎي ﺗﺨﻠﻴﻪ ﺑﻴﻦ‬،‫ﺑﻪ ﻏﻴﺮ از ﻛﺎرﺑﺮي ﻫﻮاي اﺑﺰاردﻗﻴﻖ‬
.‫ادوات اﺑﺰاردﻗﻴﻖ و ﺷﻴﺮﻫﺎي ﺟﺪاﺳﺎزي آﻧﻬﺎ ﻻزم اﺳﺖ‬
‫ﺗﺨﻠﻴﻪ ﻣﻤﻜﻦ اﺳﺖ اﺳﺘﻔﺎده‬/‫ﺗﺮﻛﻴﺒﻲ از ﺷﻴﺮﻫﺎي ﺟﺪاﺳﺎزي‬
. ‫ﺷﻮد‬
Refer to API Std. 614 for details on
instrumentation.
‫ ﺑﺮاي ﺟﺰﺋﻴﺎت اﺑﺰاردﻗﻴﻖ ﻣﺮاﺟﻌﻪ‬API 614 ‫ﺑﻪ اﺳﺘﺎﻧﺪارد‬
.‫ﻛﻨﻴﺪ‬
7.2.10.3 Anti-Surge control
‫ ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن‬3-10-2-7
It is essential that all centrifugal compressor
control systems be designed to avoid possible
operation in surge which usually occurs below
50% to 70% of the rated flow.
‫ﻃﺮاﺣﻲ ﺳﺎﻣﺎﻧﻪﻫﺎي ﻛﻨﺘﺮل ﻛﻤﭙﺮﺳﻮرﻫﺎي ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬
50 ‫ﺑﺮاي اﺟﺘﻨﺎب از ﻋﻤﻠﻴﺎت ﻣﺤﺘﻤﻞ ﻧﻮﺳﺎن ﻛﻪ اﻏﻠﺐ زﻳﺮ‬
.‫ ﻻزم اﺳﺖ‬،‫ درﺻﺪ ﺟﺮﻳﺎن ﻃﺮاﺣﻲ اﺗﻔﺎق ﻣﻲاﻓﺘﺪ‬70 ‫ﺗﺎ‬
The surge limit line can be reached by reducing
flow or decreasing suction pressures and/or
increasing discharge to suction pressure ratio.
An anti-surge system senses conditions
approaching surge, and maintains the unit
pressure ratio below the surge limit by
recycling some flow to the compressor suction.
A volume-controlled anti-surge system is
shown in Fig. 8. As the flow decreases to less
than the minimum volume set point, a signal
will cause the surge control valve to open, to
keep a minimum volume flowing through the
compressor.
‫ﺧﻂ ﻣﺤﺪوده ﻧﻮﺳﺎن ﺑﺎ ﻛﺎﻫﺶ ﺟﺮﻳﺎن ﻳﺎ ﻛﺎﻫﺶ ﻓﺸﺎر‬
‫ﻳﺎ اﻓﺰاﻳﺶ ﻧﺴﺒﺖ ﻓﺸﺎر ﺗﺨﻠﻴﻪ ﺑﻪ ﻣﻜﺶ ﻗﺎﺑﻞ‬/‫ﻣﻜﺶ و‬
‫ ﺳﺎﻣﺎﻧﻪ ﺿﺪ ﻧﻮﺳﺎن ﺷﺮاﻳﻂ ﻧﺰدﻳﻚ ﺷﺪن‬.‫دﺳﺘﻴﺎﺑﻲ اﺳﺖ‬
‫ﻧﻮﺳﺎن را ﺣﺲ ﻛﺮده و ﻧﺴﺒﺖ ﻓﺸﺎر واﺣﺪ را ﺑﺎ ﺑﺎزﮔﺮداﻧﺪن‬
‫ﻣﻘﺪاري از ﺟﺮﻳﺎن ﺑﻪ ﻣﻜﺶ ﻛﻤﭙﺮﺳﻮر زﻳﺮ ﺣﺪ ﻧﻮﺳﺎن ﻧﮕﻪ‬
8 ‫ ﺳﺎﻣﺎﻧﻪ ﺿﺪ ﻧﻮﺳﺎن ﻛﻨﺘﺮل ﺣﺠﻤﻲ در ﺷﻜﻞ‬.‫ﻣﻴﺪارد‬
‫ ﺑﺎ ﻛﺎﻫﺶ ﺟﺮﻳﺎن ﺑﻪ زﻳﺮ ﻧﻘﻄﻪ ﺗﻨﻈﻴﻢ‬.‫ﻧﺸﺎن داده ﺷﺪه اﺳﺖ‬
‫ ﺷﻴﺮ ﻛﻨﺘﺮل ﻧﻮﺳﺎن را ﺑﺮاي‬،‫ ﻳﻚ ﺳﻴﮕﻨﺎل‬،‫ﺣﺪاﻗﻞ ﺣﺠﻢ‬
.‫ﻧﮕﻬﺪاﺷﺘﻦ ﺣﺪاﻗﻞ ﺣﺠﻢ ﺟﺮﻳﺎﻧﻲ در ﻛﻤﭙﺮﺳﻮر ﺑﺎز ﻣﻴﻜﻨﺪ‬
A pressure-limiting anti-surge control system is
shown in Fig. 9. A process pressure increase
over the pressure set point will cause the blowoff valve to open. The valve opens as required
to keep the pressure limited to a minimum of
gas or air flowing through the compressor.
‫ﻳﻚ ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن ﻣﺤﺪود ﻛﻨﻨﺪه ﻓﺸﺎر در‬
‫ اﻓﺰاﻳﺶ ﻓﺸﺎر ﺑﺎﻻي ﻧﻘﻄﻪ‬.‫ ﻧﺸﺎن داده ﺷﺪه اﺳﺖ‬9 ‫ﺷﻜﻞ‬
‫ ﺷﻴﺮ در‬.‫ﺗﻨﻈﻴﻢ ﻓﺸﺎر ﻣﻨﺠﺮ ﺑﻪ ﺑﺎزﺷﺪن ﺷﻴﺮ ﺗﺨﻠﻴﻪ ﻣﻴﺸﻮد‬
‫ﺻﻮرت ﻟﺰوم ﺑﺮاي ﻧﮕﻬﺪاﺷﺘﻦ ﻓﺸﺎر در ﻣﺤﺪودهاي ﻛﻪ‬
‫ ﺑﺎز‬،‫ﺣﺪاﻗﻞ ﺟﺮﻳﺎن ﮔﺎز ﻳﺎ ﻫﻮا از ﻛﻤﭙﺮﺳﻮر ﻋﺒﻮر ﻛﻨﺪ‬
.‫ﻣﻴﺸﻮد‬
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‫)‪IPS-E-PR-750(1‬‬
‫‪ ‬‬
‫‪ ‬‬
‫ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن ﺣﺪاﻗﻞ ﺣﺠﻢ ﺟﺮﻳﺎن ‪ ‬‬
‫ﻛﻤﭙﺮﺳﻮر ‪ ‬‬
‫ﺑﻪ ﻓﺮآﻳﻨﺪ‬
‫ﻣﺤﺮك ‪ ‬‬
‫‪Set point fixed or varlable form set‬‬
‫‪point computer‬‬
‫‪Through cooler to suction (i.e. gas) or to‬‬
‫‪atmosphere on open- suction machine‬‬
‫)‪(i.e.air‬‬
‫ﻧﻘﻄﻪ ﺗﻨﻈﻴﻢ ﺛﺎﺑﺖ ﻳﺎ ﻣﺘﻐﻴﺮ ﺑﻮﺳﻴﻠﻪ ﺳﺎﻣﺎﻧﻪ‬
‫ﻣﺤﺎﺳﺒﻪ ﮔﺮ ‪ ‬‬
‫از ﺧﻨﻚﻛﻨﻨﺪه ﺑﻪ ﻣﻜﺶ )ﻣﺜﻞ ﮔﺎز( ﻳﺎ ﺑﻪ آﺗﻤﺴﻔﺮ‬
‫در ﻣﺎﺷﻴﻦﻫﺎي ﻣﻜﺶ ﺑﺎز )ﻣﺎﻧﻨﺪ ﻫﻮا(‬
‫‪ INLET‬ورودي ‪ ‬‬
‫‪Fig. 8- ANTI SURGE CONTROL - MINIMUM VOLUME‬‬
‫ﺷﻜﻞ ‪ -8‬ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن‪ -‬ﺣﺪاﻗﻞ ﺣﺠﻢ ﺟﺮﻳﺎن‬
‫ﺑﻪ ﻓﺮآﻳﻨﺪ‬
‫ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن ﻣﺤﺪودﻳﺖ ﻓﺸﺎر ‪ ‬‬
‫ﮔﺮداﻧﺪه ‪ ‬‬
‫ﻛﻤﭙﺮﺳﻮر ‪ ‬‬
‫‪Set point fixed or variable form‬‬
‫‪set point computer‬‬
‫ﻧﻘﻄﻪ ﺗﻨﻈﻴﻢ ﺛﺎﺑﺖ ﻳﺎ ﻣﺘﻐﻴﺮ ﺑﻮﺳﻴﻠﻪ‬
‫ﺳﺎﻣﺎﻧﻪ ﻣﺤﺎﺳﺒﻪ ﮔﺮ ‪ ‬‬
‫‪Through cooler to suction (i.e. gas) or to‬‬
‫)‪atmosphere on open- suction machine (i.e.air‬‬
‫از ﺧﻨﻚﻛﻦ ﺑﻪ ﻣﻜﺶ )ﻣﺜﻞ ﮔﺎز( ﻳﺎ ﺑﻪ آﺗﻤﺴﻔﺮ‬
‫در ﻣﺎﺷﻴﻦﻫﺎي ﻣﻜﺶ ﺑﺎز )ﻣﺜﻞ ﻫﻮا(‬
‫‪Fig. 9-ANTI-SURGE CONTROL-PRESSURE LIMITING‬‬
‫ﺷﻜﻞ ‪ -9‬ﻛﻨﺘﺮل ﺿﺪ ﻧﻮﺳﺎن – ﻣﺤﺪودﻳﺖ ﻓﺸﺎر‬
‫‪8. AXIAL COMPRESSORS‬‬
‫‪ -8‬ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري‬
‫‪8.1 General‬‬
‫‪ 1-8‬ﻋﻤﻮﻣﻲ‬
‫‪8.1.1 Axial compressor is usually a single inlet,‬‬
‫‪uncooled machine consisting essentially of‬‬
‫‪blades mounted on a rotor turning between rows‬‬
‫‪of stationary blades mounted on the horizontally‬‬
‫‪split casing.‬‬
‫‪ 1-1-8‬ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻣﺤﻮري ﻋﻤﻮﻣﺎً داراي ﻳﻚ ورودي‪،‬‬
‫ﺑﺪون ﺳﻴﺴﺘﻢ ﺧﻨﻚ ﺳﺎزي ﻛﻪ اﺳﺎﺳﺎً از ﺗﻴﻐﻪﻫﺎﻳﻲ روي‬
‫روﺗﻮر ﻛﻪ در ﻣﻴﺎن ردﻳﻒ ﻫﺎي ﭘﺮهﻫﺎي ﺛﺎﺑﺖ ﻛﻪ روي ﭘﻮﺳﺘﻪ‬
‫ﻣﺠﺰاي اﻓﻘﻲ ﻗﺮار ﮔﺮﻓﺘﻪ ﻣﻲ ﮔﺮدﻧﺪ‪ ،‬ﺗﺸﻜﻴﻞ ﺷﺪه اﻧﺪ‪.‬‬
‫‪27‬‬
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8.1.2 All requirements and recommendations
specified in this Section are amendments or
additions to those of Section 6 of this Standard.
‫ ﺗﻤﺎم اﻟﺰاﻣﺎت و ﺗﻮﺻﻴﻪﻫﺎي ﻣﺸﺨﺺ در اﻳﻦ ﺑﺨﺶ‬2-1-8
.‫ اﻳﻦ اﺳﺘﺎﻧﺪارد ﻣﻴﺒﺎﺷﺪ‬6 ‫ﻣﺘﻤﻢ ﻳﺎ اﻓﺰون ﺑﻪ ﻗﺴﻤﺖ‬
8.1.3 Performance guarantee
‫ ﺗﻀﻤﻴﻦ ﻋﻤﻠﻜﺮد‬3-1-8
a) Compressors shall be guaranteed for head;
capacity and satisfactory performance at
all specified operating points and further
shall be guaranteed for power at the
normal operating point.
‫ ﻇﺮﻓﻴﺖ‬،‫اﻟﻒ( ﻛﻤﭙﺮﺳﻮرﻫﺎ ﺑﺎﻳﺪ ﺑﺮاي ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع‬
‫و ﻋﻤﻠﻜﺮد رﺿﺎﻳﺖ ﺑﺨﺶ در ﺗﻤﺎم ﻧﻘﺎط ﻋﻤﻠﻴﺎﺗﻲ‬
‫ﻣﺸﺨﺺ و ﻫﻤﭽﻨﻴﻦ ﺑﺮاي ﺗﻮان در ﻧﻘﻄﻪ ﻋﻤﻠﻴﺎﺗﻲ‬
.‫ﻋﺎدي ﺗﻀﻤﻴﻦ ﺷﻮﻧﺪ‬
b) For variable-speed compressors, the head
and capacity shall be guaranteed with the
understanding that the power may vary
±4%.
‫ ارﺗﻔﺎع و ﻇﺮﻓﻴﺖ‬،‫ب ( ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي دور ﻣﺘﻐﻴﺮ‬
c) For constant-speed compressors, the
specified capacity shall be guaranteed
with the understanding that the head shall
be specified for 100.0 and 105.0 percent;
the power consumption shall not exceed
stated power by more than 4%. These
tolerances are not additive.
‫ ﻇﺮﻓﻴﺖ ﻣﺸﺨﺺ‬،‫ج( ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي دور ﺛﺎﺑﺖ‬
‫ درﺻﺪ‬±4 ‫ﺑﺎﻳﺪ ﺑﺎ درك اﻳﻦ ﻛﻪ ﺗﻮان ﻣﻴﺘﻮاﻧﺪ‬
.‫ﺗﻐﻴﻴﺮ ﻛﻨﺪ ﺗﻀﻤﻴﻦ ﺷﻮد‬
‫ﺷﺪه ﺑﺎ درك اﻳﻦ ﻛﻪ ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع ﺑﺎﻳﺪ‬
‫درﺻﺪ ﻣﺸﺨﺺ ﺷﻮد ﺑﺎﻳﺪ‬105 ‫ و‬100 ‫ﺑﺮاي‬
‫ درﺻﺪ ﺑﻴﺶ از‬4 ‫ ﻣﺼﺮف ﺗﻮان ﻧﺒﺎﻳﺪ‬:‫ﺗﻀﻤﻴﻦ ﺷﻮد‬
‫ اﻳﻦ رواداريﻫﺎ‬.‫ﺗﻮان ﺗﻌﻴﻴﻦ ﺷﺪه ﺑﻴﺸﺘﺮ ﺷﻮد‬
.‫ﻗﺎﺑﻞ اﻓﺰاﻳﺶ ﻧﻴﺴﺘﻨﺪ‬
d) For compressors handling side loads or
for two or more compressors driven by a
single drive, the required performance
guarantee for each compressor "section"
shall be agreed upon by the Company and
the Vendor.
‫د ( ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﭘﺬﻳﺮﻧﺪه ﺑﺎرﻫﺎي ﺟﺎﻧﺒﻲ ﻳﺎ ﺑﺮاي‬
‫ ﺗﻀﻤﻴﻦ‬،‫دو ﻳﺎ ﭼﻨﺪ ﻛﻤﭙﺮﺳﻮر ﺑﺎ ﻳﻚ ﻣﺤﺮك‬
‫ﻋﻤﻠﻜﺮد ﻻزم ﻫﺮ "ﺑﺨﺶ" ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ‬
.‫ﺑﺎ ﺗﻮاﻓﻖ ﻛﺎرﻓﺮﻣﺎ و ﻓﺮوﺷﻨﺪه ﺑﺎﺷﺪ‬
8.2 Design Criteria
‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-8
8.2.1 Performance
‫ ﻋﻤﻠﻜﺮد‬1-2-8
8.2.1.1 The minimum head rise to surge of an
axial machine should be specified. The normal
operating point shall be at least 10% removed in
flow from surge point.
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﺣﺪاﻗﻞ اﻓﺰاﻳﺶ ﻓﺸﺎر ﻣﻌﺎدل‬1-1-2-8
.‫ارﺗﻔﺎع ﺑﺮاي ﻧﻮﺳﺎن در ﻣﺎﺷﻴﻨﻬﺎي ﻣﺤﻮري ﻣﺸﺨﺺ ﺷﻮد‬
‫ درﺻﺪ اﻣﻜﺎن اﻓﺰاﻳﺶ‬10 ‫ﻧﻘﻄﻪ ﻋﻤﻠﻴﺎت ﻋﺎدي ﺑﺎﻳﺪ ﺣﺪاﻗﻞ‬
.‫ﺟﺮﻳﺎن از ﻧﻘﻄﻪ ﻧﻮﺳﺎن داﺷﺘﻪ ﺑﺎﺷﺪ‬
8.2.2 Gas velocities
‫ ﺳﺮﻋﺘﻬﺎي ﮔﺎز‬2-2-8
General guideline for good design practice
indicates an axial velocity for air of 91 to 137
meters per second. For other gases, the axial
velocity range is in direct proportion to the
speed of sound of the gas compared to air. The
internal shape of the machine is usually
arranged to give constant gas velocity as the gas
travels through.
‫راﻫﻨﻤﺎﻳﻲ ﻛﻠﻲ ﺑﺮاي اﻧﺠﺎم ﻃﺮاﺣﻲ ﻣﻨﺎﺳﺐ ﻧﺸﺎن ﻣﻴﺪﻫﺪ ﻛﻪ‬
‫ ﺑﺮاي‬.‫ ﻣﺘﺮ در ﺛﺎﻧﻴﻪ ﻣﻲ ﺑﺎﺷﺪ‬137 ‫ ﺗﺎ‬91 ‫ﺳﺮﻋﺖ ﻣﺤﻮري ﻫﻮا‬
‫ ﻣﺤﺪوده ﺳﺮﻋﺖ ﻣﺤﻮري ﻧﺴﺒﺖ ﻣﺴﺘﻘﻴﻤﻲ ﺑﺎ‬،‫ﺳﺎﻳﺮ ﮔﺎزﻫﺎ‬
‫ ﺷﻜﻞ داﺧﻠﻲ‬.‫ﺳﺮﻋﺖ ﺻﻮت ﮔﺎز در ﻣﻘﺎﻳﺴﻪ ﺑﺎ ﻫﻮا دارد‬
‫ﻣﺎﺷﻴﻦ ﻃﻮري ﺟﺎﻧﻤﺎﻳﻲ ﺷﺪه ﻛﻪ ﮔﺎز اﻛﺜﺮاً ﺳﺮﻋﺖ ﺛﺎﺑﺘﻲ را‬
.‫در ﻋﺒﻮر از آن داﺷﺘﻪ ﺑﺎﺷﺪ‬
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8.2.3 Volume
‫ ﺣﺠﻢ‬3-2-8
The size is determined by the inlet volume. The
lower volume limit is approximately 8500 m³/h
but the upper limit practically does not exist,
units have been built to handle well above
1,700,000 m³/h.
‫ ﺣﺪ ﭘﺎﻳﻴﻦ ﺟﺮﻳﺎن‬.‫اﻧﺪازه ﺑﺎ ﺣﺠﻢ ورودي ﻣﺸﺨﺺ ﻣﻴﺸﻮد‬
‫ ﻣﺘﺮﻣﻜﻌﺐ در ﺳﺎﻋﺖ اﺳﺖ اﻣﺎ ﺣﺪ ﺑﺎﻻ‬8500 ً‫ﺣﺠﻤﻲ ﺗﻘﺮﻳﺒﺎ‬
‫ واﺣﺪﻫﺎﻳﻲ ﺑﺎ ﺗﺤﻤﻞ ﻇﺮﻓﻴﺖ‬،‫ﺑﻪ ﺻﻮرت ﺗﺠﺮﺑﻲ وﺟﻮد ﻧﺪارد‬
.‫ ﻣﺘﺮ ﻣﻜﻌﺐ ﺑﺮ ﺳﺎﻋﺖ ﻧﻴﺰ ﺳﺎﺧﺘﻪ ﺷﺪهاﻧﺪ‬1,700,000 ‫ﺑﺎﻻي‬
9. RECIPROCATING COMPRESSORS
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬-9
9.1 General
‫ ﻋﻤﻮﻣﻲ‬1-9
9.1.1 The reciprocating compressor is a positive
displacement unit with the pressure on the fluid
developed within a cylindrical chamber by the
action of a moving piston. It may consist of one
or more cylinders each with a piston or plunger
that moves back and forth, displacing a positive
volume with each stroke.
‫ ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﻳﻚ واﺣﺪ ﺟﺎﺑﺠﺎﻳﻲ‬1-1-9
‫ﻣﺜﺒﺖ اﺳﺖ ﻛﻪ ﻓﺸﺎر ﺳﻴﺎل در ﻣﺤﻔﻈﻪ ﺳﻴﻠﻨﺪر ﺑﺎ ﺣﺮﻛﺖ‬
‫ﭘﻴﺴﺘﻮن ﺗﻮﻟﻴﺪ ﻣﻴﺸﻮد و ﺷﺎﻣﻞ ﻳﻚ ﻳﺎ ﭼﻨﺪ ﺳﻴﻠﻨﺪر ﻛﻪ‬
‫ﻫﺮﻛﺪام داراي ﻳﻚ ﭘﻴﺴﺘﻮن ﻳﺎ ﭘﻴﺴﺘﻮن ﺷﻨﺎور اﺳﺖ ﻛﻪ ﺑﻪ‬
‫ﺟﻠﻮ و ﻋﻘﺐ ﺣﺮﻛﺖ ﻣﻴﻜﻨﺪ و ﺑﺎ ﻫﺮ ﺿﺮﺑﻪ ﺣﺠﻢ ﻣﻌﻴﻨﻲ‬
.‫ﺟﺎﺑﺠﺎ ﻣﻴﺸﻮد‬
9.1.2 Reciprocating compressors shall conform
to API 618 for all services except portable air
compressors, and standard utility air
compressors of 400 kW or less with not more
than 900 kPa (9 bar) discharge pressure. This
latter group will generally be purchased as
packaged units.
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺮاي ﺗﻤﺎم ﻛﺎرﺑﺮﻳﻬﺎ‬2-1-9
9.1.3 Reciprocating compressors normally
should be specified for constant-speed operation
to avoid excitation of torsional and acoustic
resonances. Rated speed (in revolutions per
minute) is the highest speed required to meet
any of the specified operating conditions. When
variable-speed drivers are used, all equipment
shall be designed to run safely to the trip speed
setting.
‫ﻋﻤﻮﻣﺎً ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و‬
‫ﺑﻪ ﻏﻴﺮ از ﻛﻤﭙﺮﺳﻮرﻫﺎي ﻗﺎﺑﻞ ﺣﻤﻞ ﻫﻮا و ﻛﻤﭙﺮﺳﻮرﻫﺎي‬
‫ ﻛﻴﻠﻮ وات ﻳﺎ ﻛﻤﺘﺮ و‬400 ‫اﺳﺘﺎﻧﺪارد ﻫﻮاي ﻛﻤﻜﻲ ﺑﺎ ﺗﻮان‬
‫ ﺑﺎﻳﺪ‬،(‫ ﺑﺎر‬9) ‫ ﻛﻴﻠﻮ ﭘﺎﺳﻜﺎل‬900 ‫ﻓﺸﺎر ﺧﺮوﺟﻲ ﻛﻤﺘﺮ از‬
‫ ﻣﺠﻤﻮﻋﻪ ﻓﻮق ﻋﻤﻮﻣﺎً ﺑﻪ ﺻﻮرت‬.‫ ﺑﺎﺷﻨﺪ‬API 618 ‫ﻣﻄﺎﺑﻖ‬
.‫واﺣﺪ ﺑﺴﺘﻪاي ﺧﺮﻳﺪاري ﻣﻴﺸﻮﻧﺪ‬
‫ﺑﺮﮔﺸﺘﻲ ﺑﺮاي ﺟﻠﻮﮔﻴﺮي از ﺗﺤﺮﻳﻚ ﭘﻴﭽﺸﻲ و ﺗﺸﺪﻳﺪ‬
‫ ﺳﺮﻋﺖ‬.‫اﻛﻮﺳﺘﻴﻚ ﺑﺮاي ﻋﻤﻠﻴﺎت دور ﺛﺎﺑﺖ ﻣﺸﺨﺺ ﺷﻮﻧﺪ‬
‫ﻃﺮاﺣﻲ )دور ﺑﺮ دﻗﻴﻘﻪ( ﺑﺎﻻﺗﺮﻳﻦ ﺳﺮﻋﺖ ﻻزم ﺑﺮاي ﻣﻮاﺟﻪ‬
‫ زﻣﺎﻧﻲ ﻛﻪ از‬.‫ﺷﺪن ﺑﺎ ﻫﺮﮔﻮﻧﻪ ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ ﻣﺸﺨﺺ اﺳﺖ‬
‫ ﺗﻤﺎم ﺗﺠﻬﻴﺰات ﺑﺎﻳﺪ‬،‫ﻣﺤﺮﻛﻬﺎي دور ﻣﺘﻐﻴﺮ اﺳﺘﻔﺎده ﺷﻮد‬
‫ ﻃﺮاﺣﻲ‬،‫ﺑﺮاي ﺣﺮﻛﺖ اﻳﻤﻦ ﺗﺎ ﺳﺮﻋﺖ ﺗﻨﻈﻴﻢ ﺷﺪه ﻗﻄﻊ‬
.‫ﺷﻮﻧﺪ‬
9.1.4 When considering the use of a single
frame for cylinders on different services
particular attention shall be given to the means
of independently controlling the different
process streams. Care shall also be taken to
ensure that the frame, transmission and driver
can accept the wide variety of loadings that
occur during all operating modes including
start-up and shut-down.
‫ در ﺻﻮرت در ﻧﻈﺮ ﮔﺮﻓﺘﻦ ﻳﻚ ﻗﺎب ﺑﺮاي ﺳﻴﻠﻨﺪرﻫﺎ‬4-1-9
‫در ﻛﺎرﺑﺮيﻫﺎي ﻣﺨﺘﻠﻒ ﺗﻮﺟﻪ وﻳﮋهاي ﺑﺮاي وﺳﺎﻳﻞ ﻛﻨﺘﺮل‬
‫ ﺑﺎﻳﺪ‬.‫ﻣﺴﺘﻘﻞ ﺟﺮﻳﺎنﻫﺎي ﻓﺮآﻳﻨﺪي ﻣﺨﺘﻠﻒ ﺑﺎﻳﺪ اﻧﺠﺎم ﺷﻮد‬
‫ وﺳﺎﻳﻞ اﻧﺘﻘﺎل و ﻣﺤﺮك ﻫﺎ‬،‫ﺑﺮاي اﻃﻤﻴﻨﺎن از اﻳﻦ ﻛﻪ ﭘﻮﺳﺘﻪ‬
‫ﻣﻴﺘﻮاﻧﻨﺪ ﺗﻐﻴﻴﺮات وﺳﻴﻌﻲ از ﺑﺎر ﻛﻪ در ﻃﻮل ﺣﺎﻟﺖ ﻋﻤﻠﻴﺎﺗﻲ‬
‫ دﻗﺖ‬،‫ را ﺗﺤﻤﻞ ﻛﻨﻨﺪ‬،‫ﺷﺎﻣﻞ راهاﻧﺪازي و ﺗﻮﻗﻒ ﻣﻲ ﺷﻮد‬
.‫ﺷﻮد‬
9.1.5 Speed ranges
‫ داﻣﻨﻪ ﻫﺎي ﺳﺮﻋﺖ‬5-1-9
The vendor shall inform the purchaser of all
critical speeds from zero to trip speed or
3-1-9
‫ﻓﺮوﺷﻨﺪه ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﺑﻪ ﺧﺮﻳﺪار ﺗﻤﺎم ﺳﺮﻋﺘﻬﺎي ﺑﺤﺮاﻧﻲ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
synchronous speed that
acceleration or deceleration.
occur
during
Low speed unit-up to
‫واﺣﺪ ﺳﺮﻋﺖ ﻛﻢ ﺗﺎ‬
Medium speed unit
High speed unit-over
‫از ﺻﻔﺮ ﺗﺎ ﺳﺮﻋﺖ ﻗﻄﻊ ﻳﺎ ﺳﺮﻋﺖ ﻫﻤﺰﻣﺎﻧﻲ ﻛﻪ در ﻃﻮل‬
.‫ﺷﺘﺎب دﻫﻲ ﻳﺎ ﻛﺎﻫﺶ ﺷﺘﺎب اﺗﻔﺎق ﻣﻲاﻓﺘﺪ را اﻃﻼع دﻫﺪ‬
‫واﺣﺪ ﺳﺮﻋﺖ ﻣﺘﻮﺳﻂ‬
‫واﺣﺪ ﺳﺮﻋﺖ ﺑﺎﻻ – ﺑﻴﺶ از‬
330 r/min
(rpm)
330 to 700 r/min
(rpm)
700 r/min
(rpm)
Generally high speed units are preferred for units
under 1865 kW. For larger units the choice is
between low and medium speed.
1865 ‫ﻋﻤﻮﻣﺎً واﺣﺪﻫﺎي ﺳﺮﻋﺖ ﺑﺎﻻ ﺑﺮاي واﺣﺪﻫﺎي ﺑﺎ ﺗﻮان زﻳﺮ‬
‫ اﻧﺘﺨﺎب‬،‫ ﺑﺮاي واﺣﺪﻫﺎي ﺑﺰرگ‬.‫ﻛﻴﻠﻮ وات ﺗﺮﺟﻴﺢ داده ﻣﻴﺸﻮد‬
.‫ﺑﻴﻦ ﺳﺮﻋﺖ ﻣﺘﻮﺳﻂ و ﻛﻢ ﺧﻮاﻫﺪ ﺑﻮد‬
The compressor vendor shall provide the
necessary lateral and torsional vibrations that
may hinder the operation of the complete unit
within the specified operating speed range in any
specified loading step.
‫ﻓﺮوﺷﻨﺪه ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﻧﻮﺳﺎﻧﺎت ﻋﺮﺿﻲ و ﭘﻴﭽﺸﻲ ﻻزم ﻛﻪ‬
‫ﻣﻤﻜﻦ اﺳﺖ ﻋﻤﻠﻴﺎت ﻛﻞ واﺣﺪ را در ﻣﺤﺪوده ﺳﺮﻋﺖ ﻋﻤﻠﻴﺎﺗﻲ‬
.‫ ﺗﻌﻴﻴﻦ ﻛﻨﺪ‬،‫ﻣﺸﺨﺺ در ﻫﺮ ﻣﺮﺣﻠﻪ ﺑﺎرﮔﻴﺮي ﺑﻪ ﺗﺄﺧﻴﺮ ﺑﻴﺎﻧﺪازد‬
9.1.6 Capacity control
‫ ﻛﻨﺘﺮل ﻇﺮﻓﻴﺖ‬6-1-9
‫ ﻛﻨﺘﺮل ﻇﺮﻓﻴﺖ ﺑﺮاي واﺣﺪﻫﺎي دور ﺛﺎﺑﺖ ﻋﻤﻮﻣﺎً ﺑﺎ‬1-6-1-9
9.1.6.1 Capacity control for constant-speed units
normally will be obtained by suction valve
unloading (depressors or lifters), clearance
pockets, a combination of both pockets and
unloaders, or bypass. Operation of controls shall
be automatic. Unless stated otherwise, five-step
unloading shall provide capacities of 100, 75, 50,
25 and 0 percent; three-step unloading shall
provide capacities of 100, 50, and 0 percent; and
two-step unloading shall provide capacities of
100 and 0 percent.
،‫ ﻓﺎﺻﻠﻪ ﻟﻘﻲ ﺷﻴﺎرﻫﺎ‬،(‫ﺑﺮداﺷﺘﻦ ﺑﺎر از ﺷﻴﺮﻣﻜﺶ )ﻛﺎﻫﻨﺪه ﻳﺎ ﺑﺎﻻﺑﺮ‬
‫ﺗﺮﻛﻴﺒﻲ از ﺑﺎر زداﻫﺎ و ﻓﺎﺻﻠﻪ ﻟﻘﻲ ﺷﻴﺎرﻫﺎ ﻳﺎ ﻛﻨﺎر ﮔﺬر ﺑﻪ دﺳﺖ‬
‫ ﺑﻪ ﻏﻴﺮ از ﻣﻮارد‬.‫ ﻋﻤﻠﻴﺎت ﻛﻨﺘﺮل ﺑﺎﻳﺪ ﺧﻮدﻛﺎر ﺑﺎﺷﺪ‬.‫ﻣﻲآﻳﺪ‬
،75 ،100 ‫ ﺑﺮداﺷﺘﻦ ﺑﺎر ﭘﻨﺞ ﻣﺮﺣﻠﻪاي ﺑﺎﻳﺪ ﻇﺮﻓﻴﺘﻬﺎي‬،‫ﻣﺸﺨﺺ‬
‫ ﺑﺎرﺑﺮداري ﺳﻪ ﻣﺮﺣﻠﻪاي‬.‫ و ﺻﻔﺮ درﺻﺪ را ﺗﺄﻣﻴﻦ ﻛﻨﺪ‬25 ،50
‫ و ﺻﻔﺮ درﺻﺪ و ﺑﺎرﺑﺮداري دو‬50 ‫ و‬100 ‫ﺑﺎﻳﺪ ﻇﺮﻓﻴﺖﻫﺎي‬
.‫ و ﺻﻔﺮ درﺻﺪ را ﺗﺄﻣﻴﻦ ﻧﻤﺎﻳﺪ‬100 ‫ﻣﺮﺣﻠﻪاي ﺑﺎﻳﺪ ﻇﺮﻓﻴﺖﻫﺎي‬
9.1.6.2 Capacity control on variable-speed units
generally is by speed control.
‫ ﻛﻨﺘﺮل ﻇﺮﻓﻴﺖ در واﺣﺪﻫﺎي دور ﻣﺘﻐﻴﺮ ﻋﻤﻮﻣﺎً ﺑﺎ‬2-6-1-9
9.1.6.3 Clearance pockets may be either the twoposition type (pocket either open or closed) or
the variable-capacity type. If not specified, the
Vendor shall propose on the data sheet the type
recommended for the Purchaser’s or Company’s
operating conditions.
،‫ ﻓﺎﺻﻠﻪ ﻟﻘﻲ ﺷﻴﺎرﻫﺎ ﻣﻤﻜﻦ اﺳﺖ ﻳﻜﻲ از دو ﻧﻮع‬3-6-1-9
.‫ﻛﻨﺘﺮل ﺳﺮﻋﺖ اﻧﺠﺎم ﮔﻴﺮد‬
‫ﻧﻮع دو ﭘﻴﺴﺘﻮﻧﻪ )ﻣﺤﻔﻈﻪ ﺑﺎز ﻳﺎ ﺑﺴﺘﻪ اﺳﺖ( ﻳﺎ ﻧﻮع ﻇﺮﻓﻴﺖ‬
‫ ﻓﺮوﺷﻨﺪه ﺑﺎﻳﺪ در ﺑﺮﮔﻪ‬،‫ اﮔﺮ ﻧﻮع ﺗﻌﻴﻴﻦ ﻧﺸﻮد‬.‫ﻣﺘﻐﻴﺮ ﺑﺎﺷﺪ‬
‫اﻃﻼﻋﺎت ﻧﻮع ﺗﻮﺻﻴﻪ ﺷﺪه ﺑﺮاي ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ ﺧﺮﻳﺪار ﻳﺎ‬
.‫ﻛﺎرﻓﺮﻣﺎ را ﭘﻴﺸﻨﻬﺎد ﻛﻨﺪ‬
9.1.6.4 When unloading for startup is necessary,
unloading arrangement shall be stated on the
data sheet or shall be mutually agreed upon
between the Purchaser’s and or the Company’s
and the Vendor.
،‫ زﻣﺎﻧﻲ ﻛﻪ ﺑﺮاي راه اﻧﺪازي ﺑﺎرﺑﺮداري ﻻزم ﺑﺎﺷﺪ‬4-6-1-9
‫آراﻳﺶ ﺑﺎرﺑﺮداري ﺑﺎﻳﺪ ﻳﺎ در ﺑﺮﮔﻪ ﻣﺸﺨﺼﺎت ﺑﻴﺎن ﺷﻮد ﻳﺎ ﺑﺎ‬
.‫ﺗﻮاﻓﻖ ﻣﺘﻘﺎﺑﻞ ﺑﻴﻦ ﺧﺮﻳﺪار و ﻳﺎ ﻛﺎرﻓﺮﻣﺎ و ﻓﺮوﺷﻨﺪه ﺑﺎﺷﺪ‬
9.2 Design Criteria
‫ ﻣﻌﻴﺎر ﻃﺮاﺣﻲ‬2-9
9.2.1 This Section covers information necessary
for process engineers to determine the
‫ اﻳﻦ ﺑﺨﺶ اﻃﻼﻋﺎت ﻻزم ﺑﺮاي ﻣﻬﻨﺪﺳﺎن ﻓﺮآﻳﻨﺪ ﺑﺮاي‬1-2-9
30
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
approximate power required to compress a
certain volume of gas at some intake conditions
to a given discharge pressure, and estimate the
capacity of an existing reciprocating compressor
under specified suction and discharge conditions.
‫ﺗﻌﻴﻴﻦ ﺗﻮان ﺗﻘﺮﻳﺒﻲ ﻻزم ﺑﺮاي ﺗﺮاﻛﻢ ﺣﺠﻢ ﻣﻌﻴﻨﻲ از ﮔﺎز در‬
‫ﺷﺮاﻳﻂ ورودي ﺑﻪ ﻓﺸﺎر ﺧﺮوﺟﻲ ﻣﺸﺨﺺ و ﺗﺨﻤﻴﻦ ﻇﺮﻓﻴﺖ‬
‫ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﻣﻮﺟﻮد در ﺷﺮاﻳﻂ ﻣﻜﺶ و ﺧﺮوج‬
.‫ﻣﺸﺨﺺ را ﭘﻮﺷﺶ ﻣﻴﺪﻫﺪ‬
9.2.2 Reciprocating compressors are furnished
either single-stage or multi-stage. The number of
stages is determined by the overall compression
ratio.
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺗﻚ ﻣﺮﺣﻠﻪاي ﻳﺎ ﭼﻨﺪ‬2-2-9
‫ ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺑﺎ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﻛﻠﻲ‬.‫ﻣﺮﺣﻠﻪاي ﺳﺎﺧﺘﻪ ﻣﻴﺸﻮﻧﺪ‬
.‫ﻣﺸﺨﺺ ﻣﻴﺸﻮد‬
9.2.3 On multistage machines, intercoolers may
be provided between stages. Such cooling
reduces the actual volume of gas going to the
high pressure cylinders, reduces the power
required for compression, and keeps the
temperature within safe operating limits.
‫ ﺣﺠﻢ‬،‫ ﺧﻨﻚ ﻛﺮدن‬.‫ﻛﻨﻨﺪه ﻫﺎي ﻣﻴﺎﻧﻲ ﺑﻴﻦ ﻣﺮاﺣﻞ ﺗﻌﺒﻴﻪ ﺷﻮد‬
،‫واﻗﻌﻲ ﮔﺎز را ﻛﻪ ﺑﻪ ﺳﻴﻠﻨﺪر ﻓﺸﺎر ﺑﺎﻻ ﻣﻴﺮود ﻛﺎﻫﺶ ﻣﻴﺪﻫﺪ‬
‫ﺗﻮان ﻻزم ﺑﺮاي ﺗﺮاﻛﻢ را ﻛﺎﻫﺶ داده و دﻣﺎ را در ﻣﺤﺪوده ﻫﺎي‬
.‫ﻋﻤﻠﻴﺎﺗﻲ اﻳﻤﻦ ﻧﮕﻪ ﻣﻴﺪارد‬
9.2.4 Reciprocating compressors should be
supplied with clean gas as they cannot
satisfactorily handle liquids and solid particles
that may be entrained in the gas.
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺎ ﮔﺎز‬4-2-9
9.2.5 In evaluating the work of compression, the
enthalpy change is the best way. If a P-H
diagram is available, the work of compression
should always be calculated by the enthalpy
change of the gas in going from suction to
discharge conditions.
.‫ ﺗﻐﻴﻴﺮ آﻧﺘﺎﻟﭙﻲ ﺑﻬﺘﺮﻳﻦ راه اﺳﺖ‬،‫ در ارزﻳﺎﺑﻲ ﻛﺎر ﺗﺮاﻛﻢ‬5-2-9
9.2.6 The k value of a gas is associated with
adiabatic compression or expansion. The change
in gas properties at different states is related by:
‫" ﻳﻚ ﮔﺎز ﺑﺎ ﺗﺮاﻛﻢ ﻳﺎ اﻧﺒﺴﺎط ﺑﻲ دررو‬K" ‫ ﻣﻘﺪار‬6-2-9
(Eq. 23)
‫ ﻣﻤﻜﻦ اﺳﺖ ﺧﻨﻚ‬،‫ در ﻣﺎﺷﻴﻨﻬﺎي ﭼﻨﺪ ﻣﺮﺣﻠﻪاي‬3-2-9
‫ﺗﻤﻴﺰ ﺗﻐﺬﻳﻪ ﺷﻮﻧﺪ زﻳﺮا آﻧﻬﺎ ﻣﺎﻳﻌﺎت ﻳﺎ ذرات ﺟﺎﻣﺪي را ﻛﻪ‬
.‫ﻣﻤﻜﻦ اﺳﺖ ﻫﻤﺮاه ﮔﺎز ﺑﺎﺷﺪ ﺑﻪ ﻃﻮر رﺿﺎﻳﺖ ﺑﺨﺶ ﻧﻤﻲ ﭘﺬﻳﺮﻧﺪ‬
‫ ﻣﻮﺟﻮد ﺑﺎﺷﺪ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻛﺎر ﺗﺮاﻛﻢ ﻫﻤﻴﺸﻪ‬P-H ‫اﮔﺮ ﻧﻤﻮدار‬
‫ﺑﺎ ﺗﻐﻴﻴﺮ آﻧﺘﺎﻟﭙﻲ ﮔﺎزي ﻛﻪ از ﺷﺮاﻳﻂ ﻣﻜﺶ ﺑﻪ ﺧﺮوﺟﻲ ﻣﻴﺮود‬
.‫ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬
‫ راﺑﻄﻪ ﺗﻐﻴﻴﺮ در ﺧﻮاص ﮔﺎز در ﺣﺎﻟﺘﻬﺎي ﻣﺨﺘﻠﻒ ﺑﻪ‬.‫ﻣﺮﺗﺒﻂ اﺳﺖ‬
:‫اﻳﻦ ﺻﻮرت اﺳﺖ‬
P1 .V1K  P2 .V2K  P3 .V3K
(23 ‫)ﻣﻌﺎدﻟﻪ‬
For a polytropic compression the actual value of
"n" (polytropic exponent) is a function of the gas
properties such as specific heats, degree of
external cooling during compression and
operating features of the cylinder. Usual
reciprocating compressor performance is
evaluated using adiabatic Cp/Cv.
(‫" )ﻧﻤﺎي ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬n" ‫ﺑﺮاي ﺗﺮاﻛﻢ ﭘﻠﻲ ﺗﺮوﭘﻴﻚ ﻣﻘﺪار واﻗﻌﻲ‬
‫ درﺟﻪ ﺧﻨﻚ ﻛﺮدن‬،‫ﺗﺎﺑﻌﻲ از ﺧﻮاص ﮔﺎز ﻣﺜﻞ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬
.‫ﺑﻴﺮوﻧﻲ در ﻃﻮل ﺗﺮاﻛﻢ و وﻳﮋﮔﻲﻫﺎي ﻋﻤﻠﻴﺎﺗﻲ ﺳﻴﻠﻨﺪر اﺳﺖ‬
‫ﻛﺎرآﻳﻲ ﻣﻌﻤﻮل ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺎ اﺳﺘﻔﺎده از‬
9.2.7 "Power Rating" or kilowatt rating of a
compressor frame is the measure of the ability of
the supporting structure and crankshaft to
withstand torque and the ability of the bearings,
to dissipate frictional heat. The rated power
includes the effect of equipment such as
pulsation suppression devices, process piping,
intercoolers, after coolers, and separators.
‫ " ﺗﻮان اﺳﻤﻲ" ﻳﺎ ﻛﻴﻠﻮ وات اﺳﻤﻲ ﭘﻮﺳﺘﻪ ﻛﻤﭙﺮﺳﻮر‬7-2-9
.‫ﺑﻲ دررو ارزﻳﺎﺑﻲ ﻣﻲ ﺷﻮد‬
CP
CV
‫ﺷﺎﺧﺼﻲ از ﺗﻮاﻧﺎﻳﻲ ﺳﺎﺧﺘﺎر ﻧﮕﻬﺪارﻧﺪه و ﻣﻴﻞ ﻟﻨﮓ ﺑﺮاي ﺗﺤﻤﻞ‬
.‫ﮔﺸﺘﺎور و ﺗﻮاﻧﺎﻳﻲ ﻳﺎﺗﺎﻗﺎن ﺑﺮاي ﭘﺮاﻛﻨﺪن ﮔﺮﻣﺎي اﺻﻄﻜﺎﻛﻲ اﺳﺖ‬
،‫ﺗﻮان اﺳﻤﻲ ﺷﺎﻣﻞ اﺛـﺮ ﺗﺠﻬﻴﺰاﺗﻲ ﻣﺜﻞ ﺗﺠﻬﻴﺰ ﻛﺎﻫﺶ ارﺗﻌﺎش‬
‫ ﺧﻨﻚ ﻛﻨﻨﺪه‬،‫ ﺧﻨﻚ ﻛﻨﻨﺪه ﻫﺎي ﻣﻴﺎﻧﻲ‬،‫ﻟﻮﻟﻪﻛﺸﻲ ﻓﺮآﻳﻨﺪي‬
.‫ﻫﺎي ﻧﻬﺎﻳﻲ و ﺟﺪاﻛﻨﻨﺪهﻫﺎ ﻣﻴﺸﻮد‬
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[ ‫ "ﺑﺎرﻫﺎي ﻣﻴﻠﻪ اي" ﺑﺮاي ﻣﺤﺪود ﻛﺮدن ﺑﺎر اﻳﺴﺘﺎ و‬8-2-9
9.2.8 "Rod Loads" are established to limit the
static and internal loads on the crankshaft,
connecting rod, frame, piston rod, bolting and
projected bearing surfaces.
،‫ دﺳﺘﻪ ﭘﻴﺴﺘﻮن‬،‫ ﭘﻮﺳﺘﻪ‬،‫ ﻣﻴﻠﻪ اﺗﺼﺎل‬،‫داﺧﻠﻲ روي ﻣﻴﻞ ﻟﻨﮓ‬
.‫ﭘﻴﭽﻬﺎ و ﺳﻄﻮح در ﻣﻌﺮض ﻳﺎﺗﺎﻗﺎنﻫﺎ ﺗﻌﺒﻴﻪ ﺷﺪهاﻧﺪ‬
9.2.9 Performance calculation
‫ ﻣﺤﺎﺳﺒﻪ ﻋﻤﻠﻜﺮد‬9-2-9
9.2.9.1 Determination of properties pertaining
to compression
‫ ﺗﻌﻴﻴﻦ ﺧﻮاص ﻣﺮﺑﻮط ﺑﻪ ﺗﺮاﻛﻢ‬1-9-2-9
Compressibility factor (Z factor), ratio of
specific heats (Cp/Cv or k value), and molecular
mass are three major physical properties for
compression which must be clarified. Mollier
diagrams should be used if available.
‫ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه )ﻣﻘﺎدﻳﺮ‬،(Z ‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي) ﺿﺮﻳﺐ‬
‫( و ﺟﺮم ﻣﻠﻜﻮﻟﻲ ﺳﻪ ﺧﺎﺻﻴﺖ ﻓﻴﺰﻳﻜﻲ اﺻﻠﻲ ﺑﺮاي‬K ‫ ﻳﺎ‬Cp/Cv
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد از‬.‫ﺗﺮاﻛﻢ ﻫﺴﺘﻨﺪ ﻛﻪ ﺑﺎﻳﺪ روﺷﻦ ﺷﻮﻧﺪ‬
.‫ﻧﻤﻮدارﻫﺎي ﻣﻮﻟﻴﺮ در ﺻﻮرت وﺟﻮد اﺳﺘﻔﺎده ﺷﻮد‬
The k value, may be calculated from the ideal
gas equation:
:‫ ﻣﻤﻜﻦ اﺳﺖ از ﻣﻌﺎدﻟﻪ ﮔﺎز اﻳﺪهآل ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬K ‫ﻣﻘﺪار‬
(Eq. 24)
.
K= C  M C
P
CV
P
MC P  R
(24 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛــــﻪ‬
MCp
is molar heat capacity at
constant pressure (kJ/kmol.K);
R
is
gas
constant,
kJ/kmol.K.
(kJ/kmol.K) ‫ ﻇﺮﻓﻴﺖ ﺣﺮارﺗﻲ ﻣﻮﻟﻲ در ﻓﺸﺎر ﺛﺎﺑﺖ‬MCp
. kJ/kmol.K 8/3143 ‫ﺛﺎﺑﺖ ﮔﺎز‬
8.3143
Method presented in Tables A.3 and A.4 of
Appendix A can be used for calculation of k
value of hydrocarbon gases and vapors.
‫ ﭘﻴﻮﺳﺖ اﻟﻒ‬4-‫ و اﻟﻒ‬3-‫روش ﻣﺸﺨﺺ ﺷﺪه در ﺟﺪوﻟﻬﺎي اﻟﻒ‬
‫ ﮔﺎزﻫﺎ و ﺑﺨﺎرات ﻫﻴﺪروﻛﺮﺑﻨﻲ‬K ‫ﻣﻴﺘﻮاﻧﺪ ﺑﺮاي ﻣﺤﺎﺳﺒﻪ ﻣﻘﺪار‬
.‫اﺳﺘﻔﺎده ﺷﻮد‬
9.2.9.2 Determination of suction conditions
‫ ﺗﻌﻴﻴﻦ ﺷﺮاﻳﻂ ﻣﻜﺶ‬2-9-2-9
The following conditions at the suction flange
should be determined:
.‫ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﺷﺮاﻳﻂ زﻳﺮ در ﻓﻠﻨﺞ ﻣﻜﺶ ﺗﻌﻴﻴﻦ ﺷﻮد‬
a) Temperature
‫اﻟﻒ( دﻣﺎ‬
b) Pressure
‫ب ( ﻓﺸﺎر‬
In case of air taken from atmosphere,
corrections should be made for elevation. Air
humidity should also be considered.
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد اﺻﻼﺣﺎﺗﻲ‬،‫در ﺣﺎﻟﺖ ﻣﻜﺶ ﻫﻮا از ﻣﺤﻴﻂ‬
‫ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد رﻃﻮﺑﺖ ﻫﻮا ﻧﻴﺰ در‬.‫ﺑﺮاي ارﺗﻔﺎع اﻧﺠﺎم ﺷﻮد‬
.‫ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﻮد‬
c) Flow rate
R
‫ج ( ﻣﻴﺰان ﺟﺮﻳﺎن‬
Since the maximum and minimum flow rates
are important parameters in compressor
selection in some cases, studies must be
conducted carefully.
‫از آﻧﺠﺎﻳﻲ ﻛﻪ ﻣﻴﺰان ﺟﺮﻳﺎن ﺣﺪاﻗﻞ و ﺣﺪاﻛﺜﺮ در ﺑﺮﺧﻲ‬
،‫ﻣﻮارد ﭘﺎراﻣﺘﺮﻫﺎي ﻣﻬﻤﻲ در اﻧﺘﺨﺎب ﻛﻤﭙﺮﺳﻮر ﻫﺴﺘﻨﺪ‬
.‫ﻣﻄﺎﻟﻌﺎت اﻧﺠﺎم ﺷﺪه ﺑﺎﻳﺪ ﺑﺎ دﻗﺖ ﺑﺎﺷﺪ‬
For the purpose of performance calculations,
compressor capacity is expressed as the
‫ ﻇﺮﻓﻴﺖ ﻛﻤﭙﺮﺳﻮر ﺑﻪ ﺻﻮرت‬،‫ﺑﻪ ﻣﻨﻈﻮر ﻣﺤﺎﺳﺒﺎت ﻛﺎرآﻳﻲ‬
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actual volumetric quantity of gas at inlet to
each stage of compression on a per hour basis
(Im³/h).
‫ﻣﻘﺪار ﺣﻘﻴﻘﻲ ﺣﺠﻤﻲ ﮔﺎز ورودي در ﺳﺎﻋﺖ در ﻫﺮ‬
(Im³/h) .‫ﻣﺮﺣﻠﻪ ﺗﺮاﻛﻢ ﺑﻴﺎن ﻣﻴﺸﻮد‬
1) Inlet volume
‫( ﺣﺠﻢ ورودي‬1
From mass (weight) flow W, (kg/h):
Q
(Eq. 25)
(kg/h)(‫از ﺟﺮﻳﺎن ﺟﺮﻣﻲ )وزﻧﻲ‬
R W.T1 .Z1
(
)
M P1 Z L
(25 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــــﻪ‬
R
Is gas constant;
M
Is
molecular
(kg/kmol);
P1
‫ﺛﺎﺑﺖ ﮔﺎز؛‬
R
‫(؛‬kg/kmol) ‫ﺟﺮم ﻣﻠﻜﻮﻟﻲ‬
M
Is absolute pressure, in (kPa);
‫(؛‬kPa) ‫ﻓﺸﺎر ﻣﻄﻠﻖ‬
P1
T1
Is absolute temperature, in (K);
‫(؛‬K) ‫دﻣﺎي ﻣﻄﻠﻖ‬
T1
Z1
Is gas compressibility factor at
inlet condition;
‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﮔﺎز در ﺷﺮاﻳﻂ ورودي؛‬
Z1
ZL
Is gas compressibility factor at
standard condition.
.‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﮔﺎز در ﺷﺮاﻳﻂ اﺳﺘﺎﻧﺪارد‬
ZL
mass,
in
:(Sm³/h) ‫از‬
From (Sm³/h):
Q  q ( Sm 3 / h)(
(Eq. 26)
101.34 T1 .Z 1
)(
)
288.15 P1 Z L
(26 ‫)ﻣﻌﺎدﻟﻪ‬
:(Nm³/h)‫از‬
From (Nm³/h):
Q  q( Nm3 / h )(
(Eq. 27)
101.34 T1.Z1
)(
)
273.15 P1Z L
(27 ‫)ﻣﻌﺎدﻟﻪ‬
2) Piston displacement
‫( ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن‬2
Piston displacement is equal to the net piston
area multiplied by the length of the piston
sweep in a given period of time:
‫ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن ﻣﻌﺎدل ﺳﻄﺢ ﺧﺎﻟﺺ ﭘﻴﺴﺘﻮن‬
‫ﺿﺮﺑﺪر ﻃﻮل رﻓﺖ و ﺑﺮﮔﺸﺖ ﭘﻴﺴﺘﻮن در ﺑﺎزهاي از‬
:‫زﻣﺎن اﺳﺖ‬
For a single-acting piston compressing on the
outer end only:
‫ﺑﺮاي ﭘﻴﺴﺘﻮن ﻳﻚ ﻃﺮﻓﻪ ﻛﻪ ﺗﺮاﻛﻢ ﻓﻘﻂ در اﻧﺘﻬﺎي‬
:‫ﺧﺎرﺟﻲ اﻧﺠﺎم ﻣﻲ ﺷﻮد‬
(Eq. 28)
PD 
S(r / min)(D 2 )  60
 47.124  10 9  S(r / min)D 2
9
4  10
‫ﺑﺮاي ﭘﻴﺴﺘﻮن ﻳﻚ ﻃﺮﻓﻪ ﻛﻪ ﺗﺮاﻛﻢ ﻓﻘﻂ در اﻧﺘﻬﺎي‬
For a single acting piston compressing on the
(28 ‫)ﻣﻌﺎدﻟﻪ‬
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crank end only:
:‫ﻣﻴﻞ ﻟﻨﮓ اﻧﺠﺎم ﻣﻲ ﺷﻮد‬
(Eq. 29)
PD 
S(r / min)(D 2  d 2 )  60
 47.124  10 9  S(r / min)(D 2  d 2 ) (29 ‫)ﻣﻌﺎدﻟﻪ‬
9
4  10
and for a double acting piston (other than rod
tail type):
(Eq. 30) PD 
:(‫و ﺑﺮاي ﭘﻴﺴﺘﻮن دو ﻃﺮﻓﻪ )ﻏﻴﺮ از ﻧﻮع دﺳﺘﻪ اﻧﺘﻬﺎﻳﻲ‬
S ( r / min)( 2 D 2  d 2 )  60
 47.124  10 9  S ( r / min)( 2 D 2  d 2 ) (30 ‫)ﻣﻌﺎدﻟﻪ‬
9
4  10
Where:
:‫ﻛـــــﻪ‬
:(m³/h) ‫ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن‬
PD
‫(؛‬mm) ‫ﻃﻮل ﺿﺮﺑﻪ‬
S
PD
Is piston displacement, in
(m³/h);
S
Is stroke length, in (mm);
D
Is cylinder inside diameter, in
(mm);
‫(؛‬mm) ‫ﻗﻄﺮ داﺧﻠﻲ ﺳﻴﻠﻨﺪر‬
D
d
Is piston rod diameter, in
(mm);
‫(؛‬mm) ‫ﻗﻄﺮ دﺳﺘﻪ ﭘﻴﺴﺘﻮن‬
d
r/min
Is compressor speed,
(rotations per minute).
in
.(‫ ﺳﺮﻋﺖ ﻛﻤﭙﺮﺳﻮر )دور ﺑﺮ دﻗﻴﻘﻪ‬r/min
3) Cylinder clearance
‫( ﻓﺎﺻﻠﻪ ﻣﺠﺎز در ﺳﻴﻠﻨﺪر‬3
In a reciprocating compressor the piston does
not travel completely to the end of the
cylinder at the end of the discharge stroke.
Some clearance volume is necessary and it
includes the space between the end of the
piston and the cylinder head when the piston
is at the end of its stroke. It also includes the
volume in the valve ports, the volume in the
suction valve guards and the volume around
the discharge valve seats.
‫ ﭘﻴﺴﺘﻮن ﺑﻪ ﻃﻮر ﻛﺎﻣﻞ‬،‫در ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬
‫ زﻣﺎﻧﻲ ﻛﻪ ﭘﻴﺴﺘﻮن‬.‫ﺗﺎ اﻧﺘﻬﺎي ﺳﻴﻠﻨﺪر ﺣﺮﻛﺖ ﻧﻤﻴﻜﻨﺪ‬
‫ ﺷﺎﻣﻞ‬،‫ ﻣﻘﺪاري ﻓﺎﺻﻠﻪ‬،‫در اﻧﺘﻬﺎي ﺟﺎﺑﺠﺎﻳﻲ ﺧﻮد اﺳﺖ‬
.‫ﺣﺠﻢ ﺑﻴﻦ اﻧﺘﻬﺎي ﭘﻴﺴﺘﻮن و ﺳﺮ ﺳﻴﻠﻨﺪر ﻻزم اﺳﺖ‬
‫ ﺣﺠﻢ‬،‫ﻫﻤﭽﻨﻴﻦ اﻳﻦ ﻓﺎﺻﻠﻪ ﺷﺎﻣﻞ ﺣﺠﻢ درﮔﺎه ﺷﻴﺮ‬
‫درﮔﺎه ﻣﺤﺎﻓﻆ ﺷﻴﺮ ورودي و ﺣﺠﻢ دور ﻧﺸﻴﻤﻨﮕﺎه ﺷﻴﺮ‬
.‫ﺧﺮوﺟﻲ اﺳﺖ‬
Clearance volume is usually expressed as
percent of piston displacement and referred to
as percent clearance, or cylinder clearance, C.
‫ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺣﺠﻤﻲ ﻋﻤﻮﻣﺎً ﺑﻪ ﺻﻮرت درﺻﺪي از‬
‫ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن ﺑﻴﺎن ﻣﻴﺸﻮد و ﺑﻪ درﺻﺪ ﻓﺎﺻﻠﻪ‬
.‫ اﺗﻼق ﻣﻴﺸﻮد‬C ،‫ﻣﺠﺎز ﻳﺎ ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺳﻴﻠﻨﺪر‬
(Eq. 31)
C=
(31 ‫)ﻣﻌﺎدﻟﻪ‬
clearance volume
 100
piston displacement
C=
For double acting cylinders, the percent
clearance is based on the total clearance
volume for both the head end and the crank
end of a cylinder. These two clearance
volumes are not the same due to the presence
‫ﺣﺠﻢ ﻓﺎﺻﻠﻪ ﻣﺠﺎز‬
‫ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن‬
×
100
‫ﺑﺮاي ﺳﻴﻠﻨﺪرﻫﺎي دو ﻃﺮﻓﻪ درﺻﺪ ﻓﺎﺻﻠﻪ ﻣﺠﺎز‬
‫ﺣﺠﻤﻲ ﻋﻤﻮﻣﺎً ﺑﻪ ﺻﻮرت ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺑﺮاﺳﺎس ﻛﻞ‬
‫ﺣﺠﻢ ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺑﺮاي ﻫﺮ دو اﻧﺘﻬﺎي ﺳﺮ و اﻧﺘﻬﺎي‬
34
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
of the piston rod in the crank end of the
cylinder. Sometimes additional clearance
volume (external) is intentionally added to
reduce cylinder capacity.
‫ اﻳﻦ دو ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺣﺠﻢ‬.‫ﻣﻴﻞ ﻟﻨﮓ ﺳﻴﻠﻨﺪر ﻣﻴﺒﺎﺷﺪ‬
‫ﺑﻪ ﺧﺎﻃﺮ وﺟﻮد ﻣﻴﻠﻪ ﭘﻴﺴﺘﻮن در اﻧﺘﻬﺎي ﻣﻴﻞ ﻟﻨﮓ‬
‫ ﮔﺎﻫﻲ ﺣﺠﻢ ﻓﺎﺻﻠﻪ ﻣﺠﺎز‬.‫ﺳﻴﻠﻨﺪر ﻳﻜﺴﺎن ﻧﻤﻴﺒﺎﺷﻨﺪ‬
‫اﺿﺎﻓﻲ )ﺧﺎرﺟﻲ( ﻋﻤﺪاً اﺿﺎﻓﻪ ﻣﻴﺸﻮد ﺗﺎ ﻇﺮﻓﻴﺖ‬
.‫ﺳﻴﻠﻨﺪر را ﻛﻢ ﻛﻨﺪ‬
4) Volumetric efficiency
‫( راﻧﺪﻣﺎن ﺣﺠﻤﻲ‬4
The term "volumetric efficiency" refers to the
actual pumping capacity of a cylinder
compared to the piston displacement.
Without a clearance volume for the gas to
expand and delay the opening of the suction
valve(s), the cylinder could deliver its entire
piston displacement as gas capacity. The
effect of the gas contained in the clearance
volume on the pumping capacity of a cylinder
can be represented by:
‫اﺻﻄﻼح "راﻧﺪﻣﺎن ﺣﺠﻤﻲ" ﺑﻪ ﻇﺮﻓﻴﺖ ﺣﻘﻴﻘﻲ ﺗﻠﻤﺒﻪ‬
‫ﻛﺮدن ﺳﻴﻠﻨﺪر در ﻣﻘﺎﻳﺴﻪ ﺑﺎ ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن اﺗﻼق‬
‫ ﺑﺪون ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺣﺠﻤﻲ ﺑﺮاي اﻧﺒﺴﺎط ﮔﺎز و‬.‫ﻣﻴﺸﻮد‬
‫ ﺳﻴﻠﻨﺪر ﺗﻮاﻧﺎﻳﻲ‬،‫ﺗﺄﺧﻴﺮ در ﺑﺎز ﺷﺪن ﺷﻴﺮ)ﻫﺎي( ﻣﻜﺶ‬
‫ﭘﺬﻳﺮش ﻛﻞ ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن ﺑﻪ ﻋﻨﻮان ﻇﺮﻓﻴﺖ ﮔﺎز را‬
‫ اﺛﺮ ﮔﺎز ﻣﻮﺟﻮد در ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺣﺠﻢ در ﻇﺮﻓﻴﺖ‬.‫دارد‬
:‫ﺗﻠﻤﺒﻪ ﻛﺮدن ﺳﻴﻠﻨﺪر ﻣﻴﺘﻮاﻧﺪ ﺑﻪ ﺻﻮرت زﻳﺮ ﺑﻴﺎن ﺷﻮد‬
VE  100  r  C
(Eq. 32)

ZS
Zd

(r ) 1 k  1
(32 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــــﻪ‬
VE
Is volumetric efficiency;
R
Is compression ratio, P2/P1;
C
Is percent clearance;
Zs & Zd
Are gas compressibility at
suction and discharge.
for valve losses,
5%
for gas slippage (for nonlubricated compressors),
4%
for heavy gases (propane and
similar).
VE
‫ ؛‬P2/P1‫ﻧﺴﺒﺖ ﺗﺮاﻛﻢ‬
R
‫درﺻﺪ ﻓﺎﺻﻠﻪ ﻣﺠﺎز‬
C
.‫ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي در ﻣﻜﺶ و ﺧﺮوﺟﻲ‬Zs & Zd
Note that volumetric efficiencies as
determined by the above equation are
theoretical in that they do not account for
suction and discharge losses. One method for
accounting for losses is to reduce the
volumetric efficiency in the following
manner:
4%
‫ﻓﺎﺻﻠﻪ ﻣﺠﺎز ﺣﺠﻤﻲ؛‬
‫ﺗﻮﺟﻪ داﺷﺘﻪ ﺑﺎﺷﻴﺪ ﻛﻪ راﻧﺪﻣﺎنﻫﺎي ﺣﺠﻤﻲ ﻛﻪ ﺑﺎ‬
‫ﻣﻌﺎدﻟﻪ ﺑﺎﻻ ﺗﻌﻴﻴﻦ ﻣﻴﺸﻮﻧﺪ ﺗﺌﻮري ﺑﻮده و اﺗﻼفﻫﺎي‬
‫ ﻳﻚ روش ﺑﺮاي‬.‫ﻣﻜﺶ و ﺗﺨﻠﻴﻪ را ﺑﻪ ﺣﺴﺎب ﻧﻤﻲ آورد‬
‫ ﻛﺎﻫﺶ راﻧﺪﻣﺎن ﺣﺠﻤﻲ ﺑﻪ‬،‫ﺣﺴﺎب ﻛﺮدن اﺗﻼفﻫﺎ‬
:‫ﻃﺮﻳﻖ زﻳﺮ اﺳﺖ‬
،‫ﺑﺮاي اﺗﻼف در ﺷﻴﺮﻫﺎ‬
%4
‫ ﺑﺮاي ﻧﺸﺘﻲ ﺷﻴﺮ )ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺑﺪون‬%5
،(‫رواﻧﻜﺎري‬
.(‫ﺑﺮاي ﮔﺎزﻫﺎي ﺳﻨﮕﻴﻦ )ﭘﺮوﭘﺎن و ﻣﺸﺎﺑﻪ‬
%4
5) Actual capacity (actual flow rate)
(‫( ﻇﺮﻓﻴﺖ ﺣﻘﻴﻘﻲ )ﻣﻴﺰان ﺟﺮﻳﺎن ﺣﻘﻴﻘﻲ‬5
This is the volume of gas measured at intake
to the first stage of a single or multistage
compressor, at stated intake temperature and
‫ﻇﺮﻓﻴﺖ ﺣﻘﻴﻘﻲ ﺣﺠﻢ ﮔﺎز اﻧﺪازهﮔﻴﺮي ﺷﺪه در ورودي‬
‫ﺑﻪ ﻣﺮﺣﻠﻪ اول ﻛﻤﭙﺮﺳﻮر ﺗﻚ ﻳﺎ ﭼﻨﺪ ﻣﺮﺣﻠﻪاي در دﻣﺎ‬
35
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
pressure.
.‫و ﻓﺸﺎر اﻋﻼم ﺷﺪه ورودي اﺳﺖ‬
(Eq. 33)
Va = PD × VE/100 m³/h
6) Equivalent capacity
‫( ﻇﺮﻓﻴﺖ ﻣﻌﺎدل‬6
‫ ﺑﺮﺣﺴﺐ ﻣﺘﺮ ﻣﻜﻌﺐ در‬،‫ﻇﺮﻓﻴﺖ ﺧﺎﻟﺺ ﻛﻤﭙﺮﺳﻮر‬
،‫ ﻛﻴﻠﻮ ﭘﺎﺳﻜﺎل و دﻣﺎي ﻣﻜﺶ‬101/325 ‫ﺳﺎﻋﺖ در‬
:‫ﻣﻤﻜﻦ اﺳﺖ ﺗﻮﺳﻂ ﻣﻌﺎدﻟﻪ زﻳﺮ ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬
The net capacity of a compressor, in m³/h at
101.325 kPa and suction temperature, may be
calculated by equation:
(Eq. 34)
(33 ‫)ﻣﻌﺎدﻟﻪ‬
Qeq =
PD. VE. Ps
100  101.325  Z ave
(34 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــــﻪ‬
Qeq
is equivalent capacity at 101.325
kPa (abs), in (m³/h);
PD
is piston displacement, in (m³/h);
VE
is volumetric efficiency (see 4
above);
PS
is suction pressure, in [kPa (abs)];
Zave
is average compressibility.
‫ﻛﻴﻠﻮ ﭘﺎﺳﻜﺎل‬101/325 ‫ﻇﺮﻓﻴﺖ ﻣﻌﺎدل در‬
‫( ؛‬m³/h)
Qeq
‫(؛‬m³/h) ‫ﺟﺎﺑﺠﺎﻳﻲ ﭘﻴﺴﺘﻮن‬
PD
‫ ﺑﺎﻻ را ﺑﺒﻴﻨﻴﺪ(؛‬4 ‫راﻧﺪﻣﺎن ﺣﺠﻤﻲ )ﺑﻨﺪ‬
VE
‫ )ﻣﻄﻠﻖ(؛‬kPa ‫ﻓﺸﺎر ﻣﻜﺶ‬
PS
.‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﻣﻴﺎﻧﮕﻴﻦ‬
Zave
‫( اﺳﺘﻔﺎده‬m³/h) ‫اﮔﺮ از ﺗﺮاﻛﻢ ﭘﺬﻳﺮي در ﻣﺤﺎﺳﺒﻪ‬
‫ﻧﺸﻮد ﭘﺲ ﺗﻮﺻﻴﻪ ﻣﻴﺸﻮد ﻋﺒﺎرت "ﺑﺮاﺳﺎس ﺗﺮاﻛﻢ‬
‫ اﺳﺘﻔﺎده از ﻣﻘﺪار‬.‫ﭘﺬﻳﺮي اﺻﻼح ﻧﺸﺪه" اﺿﺎﻓﻪ ﺷﻮد‬
‫ ﺑﻪ‬34 ‫ ﻛﻴﻠﻮﭘﺎﺳﻜﺎل )ﻣﻄﻠﻖ( در ﻣﻌﺎدﻟﻪ‬101/325
‫ﻋﻠﺖ اﻳﻦ اﺳﺖ ﻛﻪ ﻓﺸﺎر ﭘﺎﻳﻪ ﻣﺘﺪاول ﺑﺮاي ﻧﻤﻮدارﻫﺎي‬
.(‫ را ﺑﺒﻴﻨﻴﺪ‬2-4-9-2-8 ‫ﺗﻮان ﺗﺮاﻛﻢ ﭘﺬﻳﺮ اﺳﺖ )ﺑﻨﺪ‬
If compressibility is not used as a divisor
in calculating m³/h, then the statement
"not corrected for compressibility" should
be added. The figure 101.325 kPa (abs) is
used in Eq. 34, because it is the common
base pressure for the compression power
charts (see 8.2.9.4.2).
9.2.9.3 Determination of discharge conditions
‫ ﺗﻌﻴﻴﻦ ﺷﺮاﻳﻂ ﺧﺮوﺟﻲ‬3-9-2-9
9.2.9.3.1 Discharge temperature
‫ دﻣﺎي ﺧﺮوﺟﻲ‬1-3-9-2-9
The temperature of the gas discharged from the
cylinder can be estimated from the equation:
(Eq. 35)
‫دﻣﺎي ﮔﺎزي ﻛﻪ از ﺳﻴﻠﻨﺪر ﺧﺎرج ﻣﻴﺸﻮد ﻣﻴﺘﻮاﻧﺪ از ﻣﻌﺎدﻟﻪ زﻳﺮ‬
:‫ﺗﺨﻤﻴﻦ زده ﺷﻮد‬
Td  TS (r ( k 1) / k )
Although the result of this equation is theoretical
value and heat from friction, irreversibility
effects etc., are neglected, use of it has been
recommended by many sources. Polytropic
exponent "n" may be used instead of "k" in the
above equation and will give better results.
(35 ‫)ﻣﻌﺎدﻟﻪ‬
‫اﮔﺮ ﭼﻪ ﻧﺘﻴﺠﻪ اﻳﻦ ﻣﻌﺎدﻟﻪ ﻣﻘﺪاري ﺗﺌﻮري ﺑﻮده و از اﺛﺮات‬
‫ ﺑﺎزﮔﺸﺖ ﻧﺎﭘﺬﻳﺮي وﻏﻴﺮه ﺻﺮف ﻧﻈﺮ ﺷﺪه‬،‫ﮔﺮﻣﺎي اﺻﻄﻜﺎك‬
‫ ﻧﻤﺎي‬.‫ اﺳﺘﻔﺎده از آن ﺗﻮﺳﻂ اﻛﺜﺮ ﻣﻨﺎﺑﻊ ﺗﻮﺻﻴﻪ ﻣﻲ ﮔﺮدد‬،‫اﺳﺖ‬
‫" در ﻣﻌﺎدﻟﻪ ﺑﺎﻻ‬k" ‫" ﻣﻤﻜﻦ اﺳﺖ ﺑﻪ ﺟﺎي‬n" ‫ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬
.‫اﺳﺘﻔﺎده ﺷﺪه و ﻧﺘﺎﻳﺞ ﺑﻬﺘﺮي ﺑﺪﻫﺪ‬
36
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
‫ج‬ 9.2.9.3.2
Limitations
temperature
discharge
‫ ﻣﺤﺪودﻳﺖ ﻫﺎي دﻣﺎي ﺧﺮوﺟﻲ‬2-3-9-2-9
Limitations on the discharge temperature are as
shown in API Std. 618, 2.3.
‫ از اﺳﺘﺎﻧﺪارد‬3-2 ‫ﻣﺤﺪودﻳﺖ ﻫﺎي دﻣﺎي ﺧﺮوﺟﻲ در ﺑﻨﺪ‬
.‫ ﻧﺸﺎن داده ﺷﺪه اﺳﺖ‬API 618
9.2.9.3.3
Estimation
compression stages
on
of
number
of
‫ ﺗﺨﻤﻴﻦ ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺗﺮاﻛﻢ‬3-3-9-2-9
a) Number of compression stages is a
function of compression ratio per stage
(Rcs), these parameters are related by the
equations:
R cs  (
(Eq. 36)
‫اﻟﻒ( ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺗﺮاﻛﻢ ﺗﺎﺑﻌﻲ از ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﺑﻪ ﻫﺮ‬
‫ راﺑﻄﻪ اﻳﻦ ﭘﺎراﻣﺘﺮﻫﺎ ﺑﻪ ﺻﻮرت‬.‫( اﺳﺖ‬Rcs) ‫ﻣﺮﺣﻠﻪ‬
:‫زﻳﺮ اﺳﺖ‬
Pf 1
)
P1
(36 ‫)ﻣﻌﺎدﻟﻪ‬
and
‫و‬
RCO  (
(Eq. 37)
Pf
P1
)
(37 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــــﻪ‬
Rco
is overall compression
ratio;
‫ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﻛﻠﻲ‬
Rco
P1 & Pf
are absolute initial and
final pressures
respectively;
‫ﺑﻪ ﺗﺮﺗﻴﺐ ﻓﺸﺎر ﻣﻄﻠﻖ اوﻟﻴﻪ و ﻧﻬﺎﻳﻲ‬
P1 & Pf
.‫ ﺗﻌﺪاد ﻣﺮاﺣﻞ ﺗﺮاﻛﻢ‬ (gamma)
 (gamma) is number of compression
stages.
b) The maximum ratio of compression
permissible in one stage is determined
considering and limited by the discharge
temperature (see 8.2.9.3.2), or by rod
loading (see 8.2.8), particularly in the first
stage. Economic considerations are also
involved, because a high ratio of
compression will mean a low volumetric
efficiency.
‫ب( ﺣﺪاﻛﺜﺮ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﻣﺠﺎز در ﻳﻚ ﻣﺮﺣﻠﻪ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ‬
c) In multi-stage operation, equal ratio of
compression per stage shall be used,
unless otherwise stated by process design.
This will result minimum power
requirement.
‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ ﻣﺴﺎوي ﺑﺮاي‬،‫ج( در ﻋﻤﻠﻴﺎت ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
،(‫ را ﺑﺒﻴﻨﻴﺪ‬2-3-9-2-8) ‫ﻣﺤﺪودﻳﺖ دﻣﺎي ﺧﺮوﺟﻲ‬
ً‫ را ﺑﺒﻴﻨﻴﺪ( ﻣﺨﺼﻮﺻﺎ‬8-2-8) ‫ﻳﺎ ﺑﺎ ﺑﺎر دﺳﺘﻪ ﭘﻴﺴﺘﻮن‬
‫ ﺑﻪ دﻟﻴﻞ اﻳﻨﻜﻪ ﻧﺴﺒﺖ‬.‫در ﻣﺮﺣﻠﻪ اول ﺗﻌﻴﻴﻦ ﻣﻴﺸﻮد‬
،‫ راﻧﺪﻣﺎن ﺣﺠﻤﻲ ﻛﻤﻲ ﺧﻮاﻫﺪ داﺷﺖ‬،‫ﺑﺎﻻي ﺗﺮاﻛﻢ‬
.‫ﻣﻼﺣﻈﺎت اﻗﺘﺼﺎدي ﻧﻴﺰ در ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﻲ ﺷﻮﻧﺪ‬
‫ ﻣﮕﺮ ﺟﺎﻳﻴﻜﻪ ﻃﺮاﺣﻲ‬،‫ﻫﺮ ﻣﺮﺣﻠﻪ ﺑﺎﻳﺪ اﺳﺘﻔﺎده ﺷﻮد‬
‫ﻓﺮآﻳﻨﺪ ﻣﺸﺨﺺ ﻛﻨﺪ و اﻳﻦ اﻣﺮ ﻣﻨﺠﺮ ﺑﻪ ﺣﺪاﻗﻞ ﺗﻮان‬
.‫ﻣﻮرد ﻧﻴﺎز ﺧﻮاﻫﺪ ﺷﺪ‬
9.2.9.3.4 Interstage cooling
‫ ﺧﻨﻚ ﻛﺮدن ﺑﻴﻦ ﻣﺮﺣﻠﻪاي‬4-3-9-2-9
a) Interstage cooling operations affect the
cumulative power required to do the work
of compression.
‫اﻟﻒ( ﻋﻤﻠﻴﺎت ﺧﻨﻚ ﻛﺮدن ﺑﻴﻦ ﻣﺮﺣﻠﻪاي ﻣﺠﻤﻮع ﺗﻮان‬
.‫ﻣﻮرد ﻧﻴﺎز ﻋﻤﻞ ﺗﺮاﻛﻢ را ﺗﺤﺖ ﺗﺄﺛﻴﺮ ﻗﺮار ﻣﻴﺪﻫﺪ‬
Note that if condensate forms in interstage
‫ ﻣﻴﻌﺎﻧﺎت‬،‫ﺗﻮﺟﻪ ﮔﺮدد اﮔﺮ در ﺧﻨﻚ ﻛﻨﻨﺪه ﻫﺎي ﻣﻴﺎﻧﻲ‬
37
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
coolers and is to be removed, the flow rate
and properties of the fluid will vary.
‫ ﻣﻴﺰان ﺟﺮﻳﺎن و ﺧﻮاص‬،‫ﺗﺸﻜﻴﻞ ﺷﺪه و ﺣﺬف ﺷﻮﻧﺪ‬
.‫ﺳﻴﺎل ﺗﻐﻴﻴﺮ ﺧﻮاﻫﺪ ﻛﺮد‬
b) Cooling water system, where necessary,
shall be designed as per Section 2.1.3 of
API Standard 618.
‫ در ﺻﻮرت ﻧﻴﺎز ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ‬،‫ب( ﺳﺎﻣﺎﻧﻪ آب ﺧﻨﻚ ﻛﻨﻨﺪه‬
c) Compression ratio across stage with
intercooling.
.‫ج ( ﻧﺴﺒﺖ ﺗﺮاﻛﻢ در ﻃﻮل ﻣﺮاﺣﻞ ﺑﺎ ﺧﻨﻚ ﻛﻨﻨﺪه ﻣﻴﺎﻧﻲ‬
.‫ ﻃﺮاﺣﻲ ﺷﻮد‬API 618 ‫ اﺳﺘﺎﻧﺪارد‬3-1-2‫ﻗﺴﻤﺖ‬
Pressure drop in the interstage cooler shall
be regarded to be 20 to 35 kPa. Ratio of
compression per stage (R) may be
calculated by:
(Eq. 38)
Pf = P1. R 
- (  P1). R 
‫اﻓﺖ ﻓﺸﺎر در ﺧﻨﻚ ﻛﻨﻨﺪه ﻫﺎي ﺑﻴﻦ ﻣﺮﺣﻠﻪاي ﺑﺎﻳﺪ‬
‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ در‬.‫ ﻛﻴﻠﻮﭘﺎﺳﻜﺎل ﻟﺤﺎظ ﺷﻮد‬35 ‫ ﺗﺎ‬20
‫( ﻣﻤﻜﻦ اﺳﺖ از ﻃﺮﻳﻖ زﻳﺮ ﻣﺤﺎﺳﺒﻪ‬R) ‫ﻫﺮ ﻣﺮﺣﻠﻪ‬
:‫ﺷﻮد‬
-1
- (  P2). R 
-2
-  (P3). R 
Where:
‫ اﻓﺖ ﻓﺸﺎر ﺧﻨﻚ ﻛﻨﻨﺪه ﺑﻴﻦ‬:‫ و ﻏﻴﺮه‬ΔP2 ‫ و‬ΔP1
.‫ﻣﺮﺣﻠﻪاي ﻣﺮاﺣﻞ ﻣﺨﺘﻠﻒ ﻫﺴﺘﻨﺪ‬
pressure drops of different
stages.
Other variables are defined earlier.
.‫ﻣﺘﻐﻴﺮﻫﺎي دﻳﮕﺮ ﻗﺒﻼً ﺗﻌﺮﻳﻒ ﺷﺪهاﻧﺪ‬
Number of terms on right side of this
equation should be equal to the number of
stages. This equation shall be solved by trial
and error method for the case of multi-stage
compression.
‫ﺗﻌﺪاد ﻋﺒﺎرات در ﺳﻤﺖ راﺳﺖ اﻳﻦ ﻣﻌﺎدﻟﻪ ﻣﻲ ﺑﺎﻳﺴﺖ‬
‫ اﻳﻦ ﻣﻌﺎدﻟﻪ ﺑﺎﻳﺪ ﺗﻮﺳﻂ‬.‫ﺑﺎ ﺗﻌﺪاد ﻣﺮاﺣﻞ ﻣﺴﺎوي ﺑﺎﺷﺪ‬
‫روش ﺣﺪس و ﺧﻄﺎ ﺑﺮاي ﺗﺮاﻛﻢ ﭼﻨﺪ ﻣﺮﺣﻠﻪاي ﺣﻞ‬
.‫ﺷﻮد‬
9.2.9.4 Determination of power required
‫ ﺗﻌﻴﻴﻦ ﺗﻮان ﻻزم‬4-9-2-9
Brake horse power is the actual power input at
the crankshaft of the compressor drive. It does
not include the losses in the driver itself, but is
rather the actual power which the driver must
deliver to the compressor crankshaft. There are
three methods for determination of power
required for compression. These methods are
described in the following section.
‫ ﺗﻮان ﺣﻘﻴﻘﻲ وارده ﺑﻪ ﻣﻴﻞ ﻟﻨﮓ‬،‫ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي‬
‫ﮔﺮداﻧﻨﺪه ﻛﻤﭙﺮﺳﻮر اﺳﺖ ﻛﻪ ﺷﺎﻣﻞ اﺗﻼفﻫﺎي دروﻧﻲ ﮔﺮداﻧﻨﺪه‬
‫ ﺑﻠﻜﻪ ﺗﻮان ﺣﻘﻴﻘﻲ اﺳﺖ ﻛﻪ ﮔﺮداﻧﻨﺪه ﺑﺎﻳﺪ ﺑﻪ ﻣﻴﻞ ﻟﻨﮓ‬،‫ﻧﺒﻮده‬
‫ ﺳﻪ روش ﺑﺮاي ﺗﻌﻴﻴﻦ ﺗﻮان ﻻزم ﺑﺮاي‬.‫ﻛﻤﭙﺮﺳﻮر اﻋﻤﺎل ﻛﻨﺪ‬
‫ اﻳﻦ روﺷﻬﺎ در ﺑﺨﺶ زﻳﺮ ﺷﺮح داده ﺷﺪه‬.‫ﺗﺮاﻛﻢ وﺟﻮد دارد‬
.‫اﺳﺖ‬
9.2.9.4.1 Calculation method
‫ روش ﻣﺤﺎﺳﺒﻪ‬1-4-9-2-9
a) Single stage compression
‫اﻟﻒ( ﺗﺮاﻛﻢ ﺗﻚ ﻣﺮﺣﻠﻪ اي‬
Use basic equation to determine brake horse
power:
‫از ﻣﻌﺎدﻟﻪ ﭘﺎﻳﻪ زﻳﺮ ﺑﺮاي ﺗﻌﻴﻴﻦ ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي‬
:‫اﺳﺘﻔﺎده ﻛﻨﻴﺪ‬
( k 1) / k

P1V 1k  P2 
 
Bhp 
 1 ( Lo )( FL )( Z1 )
3600(k  1)  P1 


Where:
(38 ‫)ﻣﻌﺎدﻟﻪ‬
:‫ﻛـــــﻪ‬
 P1,  P2, etc., are interstage cooler
(Eq. 39)
-3
(39 ‫)ﻣﻌﺎدﻟﻪ‬
:‫ﻛـــــﻪ‬
38
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
P1
is brake horse power,in
kilowatt (kW);
is suction pressure, in (kPa);
P2
is discharge pressure, in (kPa);
V1
is suction volume, in (m³/h), at
suction conditions;
is loss factor, comprised of
losses due to pressure drop
through friction of piston rings,
rod packing, valves, and
manifold (see Fig. 10);
Bhp
Lo
FL
is frame loss for motor driven
compressors only, values range
from 1.0 to 1.05;
is compressibility factor, based
on inlet conditions.
Bhp
‫(؛‬kPa) ‫ﻓﺸﺎر ﻣﻜﺶ‬
P1
‫(؛‬kPa) ‫ﻓﺸﺎر ﺧﺮوﺟﻲ‬
P2
‫( در ﺷﺮاﻳﻂ ﻣﻜﺶ؛‬m³/h) ‫ﺣﺠﻢ ﻣﻜﺶ‬
V1
‫ ﻣﺘﺸﻜﻞ از اﺗﻼفﻫﺎ ﺑﻪ ﺧﺎﻃﺮ اﻓﺖ‬،‫ﺿﺮﻳﺐ اﺗﻼف‬
،‫ﻓﺸﺎر از ﻃﺮﻳﻖ اﺻﻄﻜﺎك ﺣﻠﻘﻪ ﻫﺎي ﭘﻴﺴﺘﻮن‬
‫ و ﭼﻨﺪ راﻫﻪ )ﺷﻜﻞ‬،‫ ﺷﻴﺮﻫﺎ‬،‫ﻛﺎﺳﻪ ﻧﻤﺪ ﭘﻴﺴﺘﻮن‬
‫ را ﺑﺒﻴﻨﻴﺪ(؛‬10
Lo
‫ اﺗﻼف ﭘﻮﺳﺘﻪ ﻓﻘﻂ ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺑﺎ ﮔﺮداﻧﻨﺪه‬FL
‫ اﺳﺖ؛‬1/05 ‫ ﺗﺎ‬1/0 ‫ ﻣﻘﺎدﻳﺮ ﻓﻘﻂ ﺑﻴﻦ‬،‫ﻣﻮﺗﻮري‬
.‫ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﺑﺮاﺳﺎس ﺷﺮاﻳﻂ ورودي‬
‫ﺿﺮﻳﺐ اﺗﻼف‬
Z1
‫ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي )ﻛﻴﻠﻮوات( ؛‬
Fig. 10-Pressure Ratio
‫ ﻧﺴﺒﺖ ﻓﺸﺎر‬-10 ‫ﺷﻜﻞ‬
b) Multi-Stage compression
‫ب ( ﺗﺮاﻛﻢ ﭼﻨﺪ ﻣﺮﺣﻠﻪاي‬
Multi-Stage power is the sum of the
power requirements of the individual
cylinders on the compressor unit.
‫ ﻣﺠﻤﻮع ﺗﻮاﻧﻬﺎي ﻻزم ﺑﺮاي ﺗﻚ‬،‫ﺗﻮان ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
.‫ﺳﻴﻠﻨﺪرﻫﺎ در واﺣﺪ ﻛﻤﭙﺮﺳﻮر اﺳﺖ‬
39
Z1
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
(Eq. 40)




Fl k
Achual Bhp 

3600 ( k  1)  P iV






k  1 / k 
 P ni 

 1 L O1 
i 

 P i 





PV
i



k  1 / k 
 P ni 

 1 L O 2  .... 
i 

 P i 





PV
i



k  1 / k 
 P i 


i 

 P i 









L O 1




(40 ‫)ﻣﻌﺎدﻟﻪ‬
Where:
:‫ﻛـــــﻪ‬
‫( ؛‬kPa ) : i‫ﻓﺸﺎر ﺧﺮوﺟﻲ ﻣﺮﺣﻠﻪ‬
Pni
is discharge pressure of
stage i, in (kPa);
Pi
is inlet pressure to stage i,
in (kPa);
‫( ؛‬kPa ) : i‫ﻓﺸﺎر ورودي ﻣﺮﺣﻠﻪ‬
Pi
Vi
is inlet volume to stage i,
in (Am³/h);
‫ (؛‬Am³/h) : i‫ﺣﺠﻢ ورودي ﻣﺮﺣﻠﻪ‬
Vi
Pni
‫ ﺿﺮاﻳﺐ اﺗﻼف ﻫﺴﺘﻨﺪ ﻛﻪ ﺑﺮاي ﻣﺮاﺣﻞ‬Lo1, Lo2,... Lof
‫ ﺗﺼﺤﻴﺤﺎت ﺑﺮاي‬.‫ﺳﻴﻠﻨﺪر ﻃﺮاﺣﻲ ﺷﺪهاﻧﺪ‬
‫ﺗﺮاﻛﻢ ﭘﺬﻳﺮي ﻣﻤﻜﻦ اﺳﺖ ﻣﺸﺎﺑﻪ ﺳﻴﻠﻨﺪر‬
.‫ﺗﻚ ﻣﺮﺣﻠﻪاي ﺑﺎﺷﺪ‬
Lo1, Lo2,.. Lof are
loss
factors
designated by cylinder
stages. Correction for
compressibility may be
incorporated as described
for the single stage
cylinder.
9.2.9.4.2 Power determination by chart
‫ ﺗﻌﻴﻴﻦ ﺗﻮان ﺗﻮﺳﻂ ﻧﻤﻮدار‬2-4-9-2-9
Detailed compressor power calculations can
be made through the use Fig. 13-9 of GPSA.
‫ﻣﺤﺎﺳﺒﺎت ﺟﺰﺋﻴﺎت ﺗﻮان از ﻛﻤﭙﺮﺳﻮر ﺑﺎ اﺳﺘﻔﺎده از ﺷﻜﻞ‬
.‫ ﻗﺎﺑﻞ اﻧﺠﺎم اﺳﺖ‬GPSA ‫ از‬9-13
9.2.9.4.3 Power calculation by Mollier
diagram
‫ ﻣﺤﺎﺳﺒﻪ ﺗﻮان ﻧﻤﻮدار ﻣﻮﻟﻴﺮ‬3-4-9-2-9
Power calculations can be worked out most
easily and that accurately if the P-H
(Mollier) diagram is available. The
procedure is as follows:
‫ ﻣﺤﺎﺳﺒﻪ ﺗﻮان ﺑﻪ راﺣﺘﻲ‬،‫ )ﻣﻮﻟﻴﺮ( ﻣﻮﺟﻮد ﺑﺎﺷﺪ‬P-H ‫اﮔﺮ ﻧﻤﻮدار‬
:‫ دﺳﺘﻮراﻟﻌﻤﻞ ﺑﻪ ﺻﻮرت زﻳﺮ اﺳﺖ‬.‫و ﺑﺎ دﻗﺖ اﻧﺠﺎم ﻣﻲ ﮔﻴﺮد‬
a) The enthalpy at the inlet pressure and
temperature shall be calculated. The
enthalpy at the outlet pressure shall be
found from the diagram following the
line of constant entropy:
(Eq. 41)
.‫اﻟﻒ( آﻧﺘﺎﻟﭙﻲ در دﻣﺎ و ﻓﺸﺎر ورودي ﺑﺎﻳﺪ ﻣﺤﺎﺳﺒﻪ ﺷﻮد‬
‫آﻧﺘﺎﻟﭙﻲ در ﻓﺸﺎر ﺧﺮوﺟﻲ ﺑﺎ دﻧﺒﺎل ﻛﺮدن ﺧﻂ‬
:‫آﻧﺘﺮوﭘﻲ ﺛﺎﺑﺖ ﺑﻪ دﺳﺖ ﻣﻲ آﻳﺪ‬
amount of work = h2 - h1
(41 ‫)ﻣﻌﺎدﻟﻪ‬
‫ ﺑﻪ ﺗﺮﺗﻴﺐ آﻧﺘﺎﻟﭙﻲ در ﺷﺮاﻳﻂ ورودي و‬h2 ‫ و‬h1
.‫( اﺳﺖ‬kJ/kg) ‫ﺧﺮوﺟﻲ ﺑﺮﺣﺴﺐ‬
Where h1 and h2 are enthalpies at inlet
and outlet conditions respectively in
(kJ/kg).
‫ از ﻣﻌﺎدﻟﻪ زﻳﺮ‬kW ‫ب ( ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي ﺑﺮﺣﺴﺐ‬
b) Brake horse power in kW (Bhp) is
calculated from the equation:
(Eq. 42)
:‫ﻣﺤﺎﺳﺒﻪ ﻣﻴﺸﻮد‬
Bhp  2.78  10 4  W (h 2  h1 )(L o )(FL )
40
(42 ‫)ﻣﻌﺎدﻟﻪ‬
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
Where:
:‫ﻛـــــﻪ‬
Bhp
is in kilowatts;
W
is mass flow rate of gas, in
(kg/h).
‫ﺑﺮﺣﺴﺐ ﻛﻴﻠﻮوات؛‬
‫( ؛‬kg/h) ‫ﻣﻴﺰان ﺟﺮﻳﺎن ﺟﺮﻣﻲ ﮔﺎز‬
Bhp
W
9.2.10 Reciprocating compressor control
devices
‫ ﺗﺠﻬﻴﺰات ﻛﻨﺘﺮل ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬10-2-9
Output of compressors must be controlled
(regulated) to match system demand.
Compressor capacity, speed, or pressure,
may be varied in accordance with the
requirements. The nature of the control
device will depend on the regulating
variable;
whether
pressure,
flow,
temperature, or some other variable; and on
type of compressor driver.
‫ﺧﺮوﺟﻲ ﻛﻤﭙﺮﺳﻮرﻫﺎ ﺑﺮاي ﺗﻄﺎﺑﻖ ﺑﺎ ﻧﻴﺎز ﺳﺎﻣﺎﻧﻪ ﺑﺎﻳﺪ ﻛﻨﺘﺮل‬
Compressor control system may be
pneumatic,
hydraulic,
Electrical
or
electronic, and they may be operated either
manually or automatically .When variable–
speed driver is specified the speed of the
drive shall vary linearly with the control
signal. And an increase in signal will
increase driver speed. Unless otherwise
specified, the full range of the purchaser’s
signal shall correspond to the required
operating range of the compressor for all
specified operating conditions. Reciprocating
compressors are usually specified for
constant-speed operation.
‫ ﺑﺮﻗﻲ‬،‫ ﻫﻴﺪروﻟﻴﻚ‬،‫ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل ﻛﻤﭙﺮﺳﻮر ﻣﻤﻜﻦ اﺳﺖ ﻫﻮاﻳﻲ‬
‫ ﻣﻤﻜﻦ اﺳﺖ‬،‫ ﺳﺮﻋﺖ ﻳﺎ ﻓﺸﺎر‬،‫ ﻇﺮﻓﻴﺖ ﻛﻤﭙﺮﺳﻮر‬.‫)ﺗﻨﻈﻴﻢ( ﺷﻮد‬
‫ ﻣﺎﻫﻴﺖ دﺳﺘﮕﺎه ﻛﻨﺘﺮل ﺑﻪ ﺗﻨﻈﻴﻢ‬.;‫ﺑﺮاﺳﺎس ﻧﻴﺎز ﺗﻐﻴﻴﺮ ﻛﻨﻨﺪ‬
‫ دﻣﺎ ﻳﺎ ﺳﺎﻳﺮ ﻣﺘﻐﻴﺮﻫﺎ و ﺑﻪ ﻧﻮع ﮔﺮداﻧﻨﺪه‬،‫ ﺟﺮﻳﺎن‬،‫ﻣﺘﻐﻴﺮ ﻓﺸﺎر‬
.‫ﻛﻤﭙﺮﺳﻮر ﺑﺴﺘﮕﻲ دارد‬
‫ﻳﺎ اﻟﻜﺘﺮوﻧﻴﻜﻲ ﺑﺎﺷﺪ و ﻣﻤﻜﻦ اﺳﺖ ﺑﻪ ﺻﻮرت دﺳﺘﻲ ﻳﺎ ﺧﻮدﻛﺎر‬
،‫ زﻣﺎﻧﻲ ﻛﻪ ﮔﺮداﻧﻨﺪه دور ﻣﺘﻐﻴﺮ ﻣﺸﺨﺺ ﺷﺪ‬.‫ﻋﻤﻞ ﻛﻨﻨﺪ‬
‫ﺳﺮﻋﺖ ﮔﺮداﻧﻨﺪه ﺑﺎ ﺳﻴﮕﻨﺎل ﻛﻨﺘﺮل ﺑﻪ ﺻﻮرت ﺧﻄﻲ ﺗﻐﻴﻴﺮ‬
‫ﻣﻴﻜﻨﺪ و اﻓﺰاﻳﺶ ﺳﻴﮕﻨﺎل ﻣﻨﺠﺮ ﺑﻪ اﻓﺰاﻳﺶ ﺳﺮﻋﺖ ﮔﺮداﻧﻨﺪه‬
‫ داﻣﻨﻪ ﻛﺎﻣﻞ ﺳﻴﮕﻨﺎل‬،‫ ﺑﻪ ﻏﻴﺮ از ﻣﻮارد ﻣﺸﺨﺺ‬.‫ﺧﻮاﻫﺪ ﺷﺪ‬
‫ﻛﻤﭙﺮﺳﻮر) ﻣﻄﺎﺑﻖ ﻧﻈﺮ ﺧﺮﻳﺪار( ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ ﻣﺤﺪوده ﻋﻤﻠﻴﺎﺗﻲ‬
.‫ﻻزم ﻛﻤﭙﺮﺳﻮر ﺑﺮاي ﻛﻞ ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ ﻣﺸﺨﺺ ﺷﺪه ﺑﺎﺷﺪ‬
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ اﻏﻠﺐ ﺑﺮاي ﻋﻤﻠﻴﺎت ﺳﺮﻋﺖ ﺛﺎﺑﺖ‬
.‫ﻣﺸﺨﺺ ﻣﻲ ﺷﻮﻧﺪ‬
9.2.10.1 Capacity control
‫ ﻛﻨﺘﺮل ﻇﺮﻓﻴﺖ‬1-10-2-9
The most common requirement is regulation
of capacity. Many capacity controls, or
unloading devices, as they are usually
termed, are actuated by the pressure on the
discharge side of the compressor.
‫ اﻛﺜﺮ ﻛﻨﺘﺮﻟﻬﺎي ﻇﺮﻓﻴﺖ‬.‫ ﺗﻨﻈﻴﻢ ﻇﺮﻓﻴﺖ اﺳﺖ‬،‫راﻳﺞ ﺗﺮﻳﻦ اﻟﺰام‬
،‫ ﻫﻤﺎﻧﻄﻮر ﻛﻪ ﻣﻌﻤﻮﻻً ﻧﺎﻣﻴﺪه ﻣﻴﺸﻮﻧﺪ‬،‫ﻳﺎ دﺳﺘﮕﺎﻫﻬﺎي ﺑﺎرﺑﺮداري‬
.‫در ﺳﻤﺖ ﺧﺮوﺟﻲ ﻛﻤﭙﺮﺳﻮر روي ﻓﺸﺎر ﻋﻤﻞ ﻣﻴﻜﻨﻨﺪ‬
A common method of controlling the
capacity of a compressor is varying the
speed. This method is applicable to steam
driven compressors and to units driven by
internal-combustion engines.
.‫ ﺗﻐﻴﻴﺮ ﺳﺮﻋﺖ اﺳﺖ‬،‫ﻳﻚ روش راﻳﺞ ﻛﻨﺘﺮل ﻇﺮﻓﻴﺖ ﻛﻤﭙﺮﺳﻮر‬
‫اﻳﻦ روش ﺑﻪ ﻛﻤﭙﺮﺳﻮرﻫﺎي ﺑﺎ ﮔﺮداﻧﻨﺪه ﺑﺨﺎري و در واﺣﺪﻫﺎﻳﻲ‬
‫ ﻗﺎﺑﻞ‬،‫ﻛﻪ ﮔﺮداﻧﻨﺪه آﻧﻬﺎ از ﻧﻮع ﻣﻮﺗﻮرﻫﺎي اﺣﺘﺮاق داﺧﻠﻲ اﺳﺖ‬
.‫اﺟﺮا ﻣﻲ ﺑﺎﺷﺪ‬
On reciprocating compressors up to about 75
kW, two types of control are usually available.
These are automatic start-and-stop control and
‫ دو ﻧﻮع‬،‫ ﻛﻴﻠﻮوات‬75 ‫در ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺗﺎ‬
‫ ﻛﻨﺘﺮل ﺧﻮدﻛﺎر ﺷﺮوع و ﺗﻮﻗﻒ و‬.‫ﻛﻨﺘﺮل ﻣﻌﻤﻮﻻً ﻣﻮﺟﻮد اﺳﺖ‬
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constant-speed control.
.‫ﻛﻨﺘﺮل دورﺛﺎﺑﺖ‬
9.2.10.1.1 Step control
‫ ﻛﻨﺘﺮل ﭘﻠﻪاي‬1-1-10-2-9
Motor-driven
reciprocating
compressors
above 75 kW in size are usually equipped with
a step control. This is in reality a variation of
constant-speed control in which unloading is
accomplished in a series of steps, varying
from full load down to no load.
‫ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﺎ ﮔﺮداﻧﻨﺪه ﻣﻮﺗﻮري ﺑﺎ ﺗﻮان‬
.‫ ﻛﻴﻠﻮ وات اﻏﻠﺐ ﻣﺠﻬﺰ ﺑﻪ ﻛﻨﺘﺮل ﭘﻠﻪاي ﻫﺴﺘﻨﺪ‬75 ‫ﺑﺎﻻﺗﺮ از‬
‫اﻳﻦ ﻧﻮع ﻛﻨﺘﺮل در ﺣﻘﻴﻘﺖ ﻳﻚ ﻧﻮع از ﻛﻨﺘﺮل دور ﺛﺎﺑﺖ اﺳﺖ‬
‫ﻛﻪ در آن ﺑﺎرﺑﺮداري از ﻳﻚ ﺳﺮي ﻣﺮاﺣﻞ ﺗﺸﻜﻴﻞ ﺷﺪه ﻛﻪ از ﺑﺎر‬
.‫ﻛﺎﻣﻞ ﺗﺎ ﺑﺪون ﺑﺎر ﺗﻐﻴﻴﺮ ﻣﻴﻜﻨﺪ‬
9.2.10.1.2 Manual contorl
‫ ﻛﻨﺘﺮل دﺳﺘﻲ‬2-1-10-2-9
Although control devices are often
automatically operated, manual operation is
satisfactory for many services.
‫ اﻣﺎ ﻋﻤﻠﻜﺮد‬،‫اﮔﺮﭼﻪ ﺗﺠﻬﻴﺰات ﻛﻨﺘﺮﻟﻲ اﻏﻠﺐ ﺧﻮدﻛﺎر ﻫﺴﺘﻨﺪ‬
.‫دﺳﺘﻲ ﺑﺮاي اﻛﺜﺮ ﻛﺎرﺑﺮدﻫﺎ رﺿﺎﻳﺖ ﺑﺨﺶ اﺳﺖ‬
9.2.10.2 Instrumentation
‫ ادوات اﺑﺰار دﻗﻴﻖ‬2-10-2-9
‫ ﻳﻚ ﺗﺎﺑﻠﻮ ﺑﺎﻳﺪ ﺗﻌﺒﻴﻪ ﺷﻮد ﻛﻪ ﺷﺎﻣﻞ ﺗﻤﺎم‬،‫در ﺻﻮرت ﺗﺸﺨﻴﺺ‬
.‫ادوات اﺑﺰار دﻗﻴﻖ روي ﺗﺎﺑﻠﻮ ﺑﺮاي ﻛﻤﭙﺮﺳﻮر و ﮔﺮداﻧﻨﺪه ﺑﺎﺷﺪ‬
‫ادوات اﺑﺰار دﻗﻴﻖ روي ﺗﺎﺑﻠﻮ ﺑﺎﻳﺪ ﺑﻪ وﺿﻮح از ﻣﺤﻞ ﻛﻨﺘﺮل‬
‫ ﻛﻠﻴﺪ ﻓﺸﺎري‬.‫ ﺑﺮاي ﻣﺘﺼﺪي واﺣﺪ ﻗﺎﺑﻞ روﻳﺖ ﺑﺎﺷﺪ‬،‫ﮔﺮداﻧﻨﺪه‬
.‫آزﻣﺎﻳﺶ ﻻﻣﭗ ﺑﺎﻳﺪ ﺗﻌﺒﻴﻪ ﺷﻮد‬
When specified, a panel shall be provided and
shall include all panel-mounted instruments
for the compressor and the driver. The
instruments on the panel shall be clearly
visible to the operator from the driver control
point; A lamp-test push bottom shall be
supplied.
،‫ ﻧﻮع‬.‫ ﻳﻚ ﺳﺮﻋﺖ ﺳﻨﺞ ﺑﺎﻳﺪ ﺗﻌﺒﻴﻪ ﺷﻮد‬،‫در ﺻﻮرت ﺗﺸﺨﻴﺺ‬
‫ زﻣﺎﻧﻲ‬،‫ﻣﺤﺪوده و ﺗﻬﻴﻪ ﻧﺸﺎﻧﮕﺮ ﺑﺎﻳﺪ ﺗﻮﺳﻂ ﺧﺮﻳﺪار اﻋﻼم ﺷﻮد‬
‫ ﻓﺮوﺷﻨﺪه ﺗﻮرﺑﻴﻦ ﺑﺎﻳﺪ‬،‫ﻛﻪ از ﮔﺮداﻧﻨﺪه ﺗﻮرﺑﻴﻨﻲ اﺳﺘﻔﺎده ﺷﻮد‬
.‫ﺣﺴﮕﺮ ﺳﺮﻋﺖ و ﻧﺸﺎﻧﮕﺮ آن را ﻓﺮاﻫﻢ ﻛﻨﺪ‬
A tachometer shall be provided when
specified. The type, range, and indicator
provision shall be stated by the purchaser.
When a turbine driver is to be used, the
turbine vendor shall furnish the speed sensor
and indictor.
9.2.10.3 Control by spill-back
‫ ﻛﻨﺘﺮل ﺗﻮﺳﻂ ﺑﺮﮔﺸﺖ ﺟﺮﻳﺎن‬3-10-2-9
In some cases, spill-back from discharge to
suction will be required for flow or pressure
control. This flow rate depends on the design
of the unloader. Minimum flow rates are as
shown below.
‫ ﺑﺮﮔﺸﺖ ﺟﺮﻳﺎن‬،‫ ﺑﺮاي ﻛﻨﺘﺮل ﻓﺸﺎر ﻳﺎ ﺟﺮﻳﺎن‬،‫در ﺑﺮﺧﻲ ﻣﻮاﻗﻊ‬
‫ اﻳﻦ ﻣﻴﺰان ﺟﺮﻳﺎن ﺑﻪ‬.‫از ﺧﺮوﺟﻲ ﺑﻪ ﻣﻜﺶ ﻻزم ﺧﻮاﻫﺪ ﺑﻮد‬
‫ ﺣﺪاﻗﻞ ﻣﻴﺰان ﻫﺎي ﺟﺮﻳﺎن‬.‫ﻃﺮاﺣﻲ ﺑﺎر ﺑﺮدار ﺑﺴﺘﮕﻲ دارد‬
:‫ﻣﻄﺎﺑﻖ زﻳﺮ ﻧﺸﺎن داده ﻣﻲ ﺷﻮد‬
Unloader Design
Spill Back
Flow Rate
‫ﻃﺮاﺣﻲ ﺑﺎر ﺑﺮدار‬
‫ﻣﻴﺰان‬
‫ﺑﺮﮔﺸﺖ ﺟﺮﻳﺎن‬
5-stage
4-stage
3-stage
2-stage
100
100
100
100
75
75
-----
25
-------
50
50
50
---
9.2.11 Gas pulsation control
25%
25%
50%
100%
‫ ﻛﻨﺘﺮل ﺿﺮﺑﺎن ﮔﺎز‬11-2-9
Pulsation is inherent in reciprocating
compressors because suction and discharge
0%
0%
0%
0%
‫ﺿﺮﺑﺎن در ﻛﻤﭙﺮﺳﻮرﻫﺎي رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﺑﻪ ﺧﺎﻃﺮ ﺑﺎز ﺑﻮدن‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
valves are open during only part of the
stroke.
‫ ذاﺗﻲ‬،‫ﺷﻴﺮﻫﺎي ﻣﻜﺶ و ﺧﺮوﺟﻲ ﻓﻘﻂ در ﻃﻮل ﺑﺨﺸﻲ از ﺿﺮﺑﻪ‬
.‫اﺳﺖ‬
Pulsation must be damped (controlled) in
order to:
:‫ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ ﻣﻮارد زﻳﺮ ﺿﺮﺑﺎن ﺑﺎﻳﺪ ﺣﺬف )ﻛﻨﺘﺮل( ﺷﻮد ﺗﺎ‬
a) Provide smooth flow of gas to and
from the compressor;
‫و از ﻛﻤﭙﺮﺳﻮر ﻓﺮاﻫﻢ ﻛﻨﺪ؛‬/‫اﻟﻒ( ﺟﺮﻳﺎن ﻳﻜﻨﻮاﺧﺖ ﮔﺎز ﺑﻪ‬
b) Prevent overloading or underloading of
the compressors, and;
‫ب( از ﺑﺎر اﺿﺎﻓﻲ ﻳﺎ ﺑﺎر ﻛﻤﺘﺮ در ﻛﻤﭙﺮﺳﻮر ﺟﻠﻮﮔﻴﺮي‬
‫ﻛﻨﺪ؛‬
c) Reduce overall vibration.
.‫ج ( ارﺗﻌﺎش ﻛﻠﻲ را ﻛﺎﻫﺶ دﻫﺪ‬
9.2.11.1 Pulsation dampeners (snubbers)
(‫ ﺣﺬف ﻛﻨﻨﺪه ﻫﺎي ﺿﺮﺑﺎن )ﻛﻤﻜﻲ ﻫﺎ‬1-11-2-9
A pulsation dampener is an internally-baffled
device. The design of the pulsation
dampening equipment is based on acoustical
analog evaluation which takes into account
the specified operating speed range,
conditions of unloading, and variations in gas
composition.
Detailed
discussion
of
recommended design approaches for
pulsation suppression devices is presented in
API Std. 618.
‫ﺣﺬف ﻛﻨﻨﺪه ﺿﺮﺑﺎن ﻳﻚ دﺳﺘﮕﺎه داراي ﺻﻔﺤﺎت ﻣﻮج ﮔﻴﺮ‬
‫ ﻃﺮاﺣﻲ ﺗﺠﻬﻴﺰات ﺣﺬف ﻛﻨﻨﺪه ﺿﺮﺑﺎن ﺑﺮاﺳﺎس‬.‫داﺧﻠﻲ اﺳﺖ‬
‫ارزﻳﺎﺑﻲ آﻧﺎﻟﻮگ ﺻﺪاﻳﻲ ﻣﻲ ﺑﺎﺷﺪ ﻛﻪ ﻣﺤﺪوده ﺳﺮﻋﺖ ﻋﻤﻠﻴﺎﺗﻲ‬
‫ ﺷﺮاﻳﻂ ﺑﺎرﺑﺮداري و ﺗﻐﻴﻴﺮات در ﺗﺮﻛﻴﺐ ﮔﺎز را‬،‫ﻣﺸﺨﺺ ﺷﺪه‬
‫ ﺑﺤﺚ ﺗﻔﺼﻴﻠﻲ در ﻣﻮرد روﺷﻬﺎي ﻃﺮاﺣﻲ‬.‫در ﻧﻈﺮ ﻣﻴﮕﻴﺮد‬
‫ﺗﻮﺻﻴﻪ ﺷﺪه ﺑﺮاي دﺳﺘﮕﺎﻫﻬﺎي ﺣﺬف ﻛﻨﻨﺪه ﺿﺮﺑﺎن در‬
.‫ ﺑﻴﺎن ﺷﺪه اﺳﺖ‬API 618 ‫اﺳﺘﺎﻧﺪارد‬
10. ROTARY COMPRESSORS
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ‬-10
10.1 General
‫ ﻋﻤﻮﻣﻲ‬1-10
10.1.1 Rotary compressors are positive
displacement gas (or vapor) compressing
machines. Rotary compressors cover lobetype, screw-type, vane-type and liquid ring
type, each having a casing with one or more
rotating elements that either mesh with each
other such as lobes or screws, or that displace
a fixed volume with each rotation.
‫ ﻣﺎﺷﻴﻨﻬﺎي ﺗﺮاﻛﻢ ﺟﺎﺑﺠﺎﻳﻲ‬،‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ‬1-1-10
‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ ﺷﺎﻣﻞ ﻧﻮع‬.‫ﻣﺜﺒﺖ ﮔﺎز )ﻳﺎ ﺑﺨﺎر( ﻫﺴﺘﻨﺪ‬
‫ ﻧﻮع ﭘﺮهاي و ﻧﻮع ﺣﻠﻘﻪ ﻣﺎﻳﻊ‬،‫ ﻧﻮع ﭘﻴﭽﻲ‬،(lobe)‫ﺑﺎداﻣﻜﻲ‬
‫ﻫﺴﺘﻨﺪ ﻛﻪ ﻫﺮﻛﺪام ﻳﻚ ﭘﻮﺳﺘﻪ ﺑﺎ ﻳﻚ ﻳﺎ ﭼﻨﺪ ﺟﺰء ﭼﺮﺧﻨﺪه‬
‫دارﻧﺪ ﻛﻪ ﻫﺮﻛﺪام ﺑﺎ دﻳﮕﺮي ﻣﺜﻞ ﭘﺮهﻫﺎ ﻳﺎ ﭘﻴﭻﻫﺎ درﻫﻢ ﮔﻴﺮ‬
.‫ﻣﻴﺸﻮﻧﺪ ﻳﺎ آﻧﻜﻪ ﻳﻚ ﺣﺠﻢ ﺛﺎﺑﺖ در ﻫﺮ ﭼﺮﺧﺶ ﺟﺎﺑﺠﺎ ﻣﻴﻜﻨﺪ‬
10.1.2 Rotary compressors shall conform to
API Std. No. 619 for all services handling air
or gas, except those machines which this
Standard does not cover.
‫ ﺑﺮاي ﺗﻤﺎم ﻛﺎرﺑﺮيﻫﺎي ﺣﺎوي‬،‫ ﻛﻤﭙﺮﺳﻮرﻫﺎي دوراﻧﻲ‬2-1-10
‫ﻫﻮا ﻳﺎ ﮔﺎز ﺑﻪ ﻏﻴﺮ از ﻣﺎﺷﻴﻨﻬﺎﻳﻲ ﻛﻪ اﻳﻦ اﺳﺘﺎﻧﺪارد ﺷﺎﻣﻞ آﻧﻬﺎ‬
.‫ ﺑﺎﺷﺪ‬API 619 ‫ ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ اﺳﺘﺎﻧﺪارد‬،‫ﻧﻤﻴﺸﻮد‬
10.1.3 Performance
‫ ﻋﻤﻠﻜﺮد‬3-1-10
10.1.3.1 Compressor shall be guaranteed for
satisfactory performance at all specified
operating conditions.
‫ ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﺑﺮاي ﻋﻤﻠﻜﺮد رﺿﺎﻳﺖ ﺑﺨﺶ در‬1-3-1-10
10.1.3.2 Compressor performance shall be
guaranteed at the rated point unless otherwise
specified. At this point no negative tolerance
is permitted on capacity and power may not
exceed 104% of the quoted power.
‫ ﺑﻪ ﻏﻴﺮ از ﻣﻮارد ﻣﺸﺨﺺ ﺷﺪه ﻋﻤﻠﻜﺮد ﻛﻤﭙﺮﺳﻮر‬2-3-1-10
.‫ﺗﻤﺎم ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ ﻣﺸﺨﺺ ﺗﻀﻤﻴﻦ ﺷﻮﻧﺪ‬
‫ در اﻳﻦ ﻧﻘﻄﻪ ﻫﻴﭻ رواداري‬.‫ﺑﺎﻳﺪ در ﻧﻘﻄﻪ ﻃﺮاﺣﻲ ﺗﻀﻤﻴﻦ ﺷﻮد‬
‫ درﺻﺪ‬104 ‫ﻣﻨﻔﻲ در ﻇﺮﻓﻴﺖ ﻣﺠﺎز ﻧﺒﻮده و ﺗﻮان ﻧﻤﻴﺘﻮاﻧﺪ از‬
.‫ﺗﻮان اﻋﻼﻣﻲ ﺑﻴﺸﺘﺮ ﺷﻮد‬
43
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
10.1.4 Cooling water
‫ آب ﺧﻨﻚﻛﻨﻨﺪه‬4-1-10
The compressor cooling water jacket shall be
designed for the specified cooling water
pressure but not less than 618 kilopascals
(absolute). The maximum pressure drop shall
be 70 kPa and provisions shall be included for
complete draining and venting of the jackets
(Modification to API Std. 619). The cooling
water design conditions shall be in accordance
with API Std. 619.
‫ﺟﺪاره آب ﺧﻨﻚﻛﻨﻨﺪه ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﺑﺮاي ﻓﺸﺎر آب‬
‫ ﻛﻴﻠﻮﭘﺎﺳﻜﺎل‬618 ‫ﺧﻨﻚﻛﻨﻨﺪه ﺗﻌﻴﻴﻦ ﺷﺪه ﻛﻪ ﻧﺒﺎﻳﺪ از‬
‫ ﻛﻴﻠﻮﭘﺎﺳﻜﺎل‬70 ‫ ﺣﺪاﻛﺜﺮ اﻓﺖ ﻓﺸﺎر ﺑﺎﻳﺪ‬.‫)ﻣﻄﻠﻖ( ﻛﻤﺘﺮ ﺷﻮد‬
‫ﺑﻮده و ﺑﺮاي ﺗﺨﻠﻴﻪ ﻛﺎﻣﻞ زﻣﻴﻨﻲ و ﻫﻮاﻳﻲ ﺟﺪاره ﺑﺎﻳﺪ‬
.(API 619 ‫ﺗﻤﻬﻴﺪاﺗﻲ دﻳﺪه ﺷﻮد )اﺻﻼﺣﻴﻪ ﺑﻪ اﺳﺘﺎﻧﺪارد‬
‫ﺷﺮاﻳﻂ ﻃﺮاﺣﻲ آب ﺧﻨﻚﻛﻨﻨﺪه ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ اﺳﺘﺎﻧﺪارد‬
.‫ ﺑﺎﺷﺪ‬API 619
10.2 Design Criteria
‫ﻣﻌﻴﺎرﻫﺎي ﻃﺮاﺣﻲ‬ 2-10
10.2.1 The vendor shall assume unit
responsibility for all equipment and all
auxiliary systems included in the scope of the
order.
‫ ﻓﺮوﺷﻨﺪه ﺑﺎﻳﺪ ﻣﺴﺌﻮﻟﻴﺖ ﺗﻤﺎم ﺗﺠﻬﻴﺰات و ﺳﺎﻣﺎﻧﻪ‬1-2-10
. ‫ﻫﺎي ﻛﻤﻜﻲ در ﻣﺤﺪوده ﺳﻔﺎرش ﺧﺮﻳﺪ را داﺷﺘﻪ ﺑﺎﺷﺪ‬
10.2.2 Equipment shall be designed to run
without damage to the relief valve set
pressure, specified maximum differential
pressure, and trip speed, simultaneously.
‫ ﺗﺠﻬﻴﺰات ﺑﺎﻳﺪ ﺑﺮاي ﻛﺎرﻛﺮد ﺑﺪون آﺳﻴﺐ ﺗﺎ ﻓﺸﺎر‬2-2-10
‫ ﺣﺪاﻛﺜﺮ اﺧﺘﻼف ﻓﺸﺎر ﺗﻌﻴﻴﻦ ﺷﺪه و‬،‫ﺗﻌﻴﻴﻦ ﺷﺪه ﺷﻴﺮ ﺗﺨﻠﻴﻪ‬
. ‫ ﺑﻪ ﻃﻮر ﻫﻤﺰﻣﺎن ﻃﺮاﺣﻲ ﺷﻮد‬،‫ﺳﺮﻋﺖ ﻗﻄﻊ‬
10.2.2.1 There may be insufficient driver
power to operate under these conditions.
‫ ﻣﻤﻜﻦ اﺳﺖ ﺗﻮان ﮔﺮداﻧﻨﺪه ﺑﺮاي ﻛﺎر ﻛﺮدن در‬1-2-2-10
. ‫اﻳﻦ ﺷﺮاﻳﻂ ﻛﺎﻓﻲ ﻧﺒﺎﺷﺪ‬
10.2.2.2 For machines operating with variable
suction and discharge pressure levels,
maximum allowable temperature can occur
before maximum allowable pressure or
maximum allowable differential pressure
occurs. In such cases the manufacturer and the
purchaser should jointly consider and apply
suitable safeguarding controls to avoid any
damage. Controls may include but are not
limited to discharge temperature or differential
pressure.
10.2.3 Unless otherwise specified, cooling
water systems shall be designed for the
following conditions:
‫ ﺑﺮاي ﻣﺎﺷﻴﻦ ﻫﺎﻳﻲ ﻛﻪ ﺑﺎ ﻣﻘﺎدﻳﺮ ﻣﺘﻐﻴﺮ ﻓﺸﺎر در‬2-2-2-10
‫ ﺣﺪاﻛﺜﺮ دﻣﺎي ﻣﺠﺎز ﻗﺒﻞ از‬،‫ﻣﻜﺶ و ﺧﺮوﺟﻲ ﻛﺎر ﻣﻲ ﻛﻨﻨﺪ‬
‫ﺣﺪاﻛﺜﺮ ﻓﺸﺎر ﻣﺠﺎز ﻳﺎ ﺣﺪاﻛﺜﺮ اﺧﺘﻼف ﻓﺸﺎر ﻣﺠﺎز اﺗﻔﺎق‬
‫ در ﭼﻨﻴﻦ ﺷﺮاﻳﻄﻲ ﺑﻪ ﺳﺎزﻧﺪه و ﺧﺮﻳﺪار ﺗﻮﺻﻴـﻪ‬.‫ﻣﻲ اﻓﺘﺪ‬
‫ﻣﻲ ﺷﻮد ﺑﻪ ﻃﻮر ﻣﺸﺘﺮك ﻛﻨﺘﺮل اﻳﻤﻨﻲ ﻣﻨﺎﺳﺒﻲ ﺑﺮاي‬
‫ ﻛﻨﺘﺮل ﻫﺎ ﺷﺎﻣﻞ اﻣﺎ ﻧﻪ‬.‫ﺟﻠﻮﮔﻴﺮي از آﺳﻴﺐ را در ﻧﻈﺮ ﺑﮕﻴﺮﻧﺪ‬
. ‫ﻣﺤﺪود ﺑﻪ دﻣﺎي ﺧﺮوﺟﻲ ﻳﺎ اﺧﺘﻼف ﻓﺸﺎر ﻣﻲ ﺑﺎﺷﺪ‬
‫ ﺳﺎﻣﺎﻧﻪ ﻫﺎي آب‬،‫ ﺑﻪ ﻏﻴﺮ از ﻣﻮارد ﻣﺸﺨﺺ ﺷﺪه‬3-2-10
.‫ﺧﻨﻚ ﻛﻨﻨﺪه ﺑﺎﻳﺪ ﺑﺮاي ﺷﺮاﻳﻂ زﻳﺮ ﻃﺮاﺣﻲ ﺷﻮﻧﺪ‬
‫ﺳﺮﻋﺖ آب روي ﺳﻄﻮح اﻧﺘﻘﺎل ﺣﺮارت‬ pressure (MAWP) ‫ﺣﺪاﻛﺜﺮ ﻓﺸﺎر ﻛﺎري ﻣﺠﺎز‬
1.5-2.5 m/s
(MAWP ‫ ﺑﺮاﺑﺮ‬1/5) ‫ﻓﺸﺎر آزﻣﻮن‬
‫ﺣﺪاﻛﺜﺮ اﻓﺖ ﻓﺸﺎر‬ ‫ﺣﺪاﻛﺜﺮ دﻣﺎي ورودي‬ ‫ﺣﺪاﻛﺜﺮ دﻣﺎي ﺧﺮوﺟﻲ‬ ‫ﺣﺪاﻛﺜﺮ اﻓﺰاﻳﺶ دﻣﺎ‬ ‫ﺣﺪاﻗﻞ اﻓﺰاﻳﺶ دﻣﺎ‬ ‫ﺿﺮﻳﺐ رﺳﻮب ﮔﺬاري در ﺳﻤﺖ آب‬
‫ﺧﻮردﮔﻲ ﻣﺠﺎز ﭘﻮﺳﺘﻪ‬
>10.5 barg
Water velocity over heat exchange surfaces
Maximum allowable working
(MAWP)
Test pressure (1.5 times MAWP)
Maximum pressure drop
Maximum inlet temperature
Maximum outlet temperature
Maximum temperature rise
Minimum temperature rise
Fouling factor on water side
Shell corrosion allowance
44
>7.0 barg
1 bar
32°C
50°C
17K
10K
0.35 m-K/kW
3.0 mm
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
The vendor shall notify the purchaser if the
criteria for minimum temperature rise and
velocity over heat exchange surfaces result in a
conflict. The criteria for velocity over heat
exchange surfaces is intended to minimize waterside fouling; the criterion for minimum
temperature rise is intended to minimize the use
of cooling water. If such a conflict exists, the
purchaser will approve the final selection.
‫در ﺻﻮرﺗﻲ ﻛﻪ ﺑﻴﻦ ﻣﻌﻴﺎر ﺣﺪاﻗﻞ اﻓﺰاﻳﺶ دﻣﺎ و ﺳﺮﻋﺖ روي‬
‫ ﻓﺮوﺷﻨﺪه‬،‫ﺳﻄﻮح اﻧﺘﻘﺎل ﺣﺮارت ﻣﻐﺎﻳﺮﺗﻲ وﺟﻮد داﺷﺘﻪ ﺑﺎﺷﺪ‬
‫ ﻣﻌﻴﺎر ﺳﺮﻋﺖ روي ﺳﻄﻮح اﻧﺘﻘﺎل‬.‫ﺑﺎﻳﺪ ﺧﺮﻳﺪار را ﻣﻄﻠﻊ ﻛﻨﺪ‬
‫ﺣﺮارت ﺑﻪ ﻣﻨﻈﻮر ﺑﻪ ﺣﺪاﻗﻞ رﺳﺎﻧﺪن رﺳﻮب ﮔﺬاري در ﺳﻤﺖ‬
‫ ﻣﻌﻴﺎر ﺣﺪاﻗﻞ اﻓﺰاﻳﺶ دﻣﺎ ﺑﺎ ﻫﺪف ﺑﻪ ﺣﺪاﻗﻞ‬،‫آب ﻣﻲ ﺑﺎﺷﺪ‬
‫ در ﺻﻮرت وﺟﻮد‬.‫رﺳﺎﻧﺪن اﺳﺘﻔﺎده از آب ﺧﻨﻚ ﻛﻨﻨﺪه اﺳﺖ‬
.‫ ﺧﺮﻳﺪار اﻧﺘﺨﺎب ﻧﻬﺎﻳﻲ را ﺗﺄﻳﻴﺪ ﺧﻮاﻫﺪ ﻛﺮد‬،‫ﻣﻐﺎﻳﺮت‬
10.2.4 All equipment shall be designed to permit
rapid and economical maintenance. Major parts
such as casing components and bearing housings
shall be designed and manufactured to ensure
accurate alignment on reassembly. This may be
accomplished by the use of shouldering,
cylindrical dowels or keys.
‫ ﺗﻤﺎم ﺗﺠﻬﻴﺰات ﺑﺎﻳﺪ ﺑﺮاي اﻣﻜﺎن ﺗﻌﻤﻴﺮات ﺳﺮﻳﻊ و‬4-2-10
‫ اﺟﺰاء اﺻﻠﻲ ﻣﺜﻞ اﺟﺰاء ﭘﻮﺳﺘﻪ و‬.‫اﻗﺘﺼﺎدي ﻃﺮاﺣﻲ ﺷﻮﻧﺪ‬
‫ﻣﺤﻔﻈﻪ ﻫﺎي ﻳﺎﺗﺎﻗﺎن ﺑﺎﻳﺪ ﺑﺮاي اﻃﻤﻴﻨﺎن از ﺗﺮاز دﻗﻴﻖ در ﻣﻮﻧﺘﺎژ‬
‫ ﻃﺮاﺣﻲ و ﺳﺎﺧﺘﻪ ﺷﻮﻧﺪ ﻛﻪ ﺑﺎ اﺳﺘﻔﺎده از اﺗﺼﺎل‬،‫دوﺑﺎره‬
.‫ﺗﻮﭘﻲ ﻫﺎي اﺳﺘﻮاﻧﻪاي ﻳﺎ ﻛﻠﻴﺪﻫﺎ اﻣﻜﺎن ﭘﺬﻳﺮ اﺳﺖ‬
10.2.5 The equipment’s maximum continuous
speed shall be not less than 105% of the rated
speed for variable speed machines and shall be
equal to the rated speed for constant speed motor
drives.
105 ‫ ﺣﺪاﻛﺜﺮ ﺳﺮﻋﺖ ﻣﺪاوم ﺗﺠﻬﻴﺰات ﻧﺒﺎﻳﺪ ﻛﻤﺘﺮ از‬5-2-10
‫درﺻﺪ ﺳﺮﻋﺖ ﻃﺮاﺣﻲ ﺑﺮاي ﻣﺎﺷﻴﻦﻫﺎي دور ﻣﺘﻐﻴﺮ و ﺑﺎﻳﺪ‬
‫ﻣﺴﺎوي ﺳﺮﻋﺖ ﻃﺮاﺣﻲ ﺑﺮاي ﮔﺮداﻧﻨﺪه ﻫﺎي ﻣﻮﺗﻮري دور ﺛﺎﺑﺖ‬
.‫ﺑﺎﺷﺪ‬
10.2.6 The equipment’s trip speed shall not be
less than the values in Table 3.
3 ‫ ﺳﺮﻋﺖ ﺗﻮﻗﻒ ﺗﺠﻬﻴﺰات ﻧﺒﺎﻳﺪ از ﻣﻘﺎدﻳﺮ ﺟﺪول‬6-2-10
. ‫ﻛﻤﺘﺮ ﺑﺎﺷﺪ‬
TABLE 3—DRIVER TRIP SPEEDS
‫ ﺳﺮﻋﺖ ﻫﺎي ﺗﻮﻗﻒ ﮔﺮداﻧﻨﺪه‬-3 ‫ﺟﺪول‬
Driver Type
Trip Speed (% of maximum Continuous Speed)
‫ﻧﻮع ﮔﺮداﻧﻨﺪه‬
(‫ﺳﺮﻋﺖ ﺗﻮﻗﻒ )درﺻﺪ از ﺣﺪاﻛﺜﺮ ﺳﺮﻋﺖ ﻣﺪام‬
Steam Turbine
‫ﺗﻮرﺑﻴﻦ ﺑﺨﺎر‬
Nema Class Aa
Aa ‫ﻃﺒﻘﻪ ﺑﻨﺪي‬Nema
115%
B,C,D a ‫ ﻃﺒﻘﻪ ﺑﻨﺪي‬Nema
110%
‫ﺗﻮرﺑﻴﻦ ﮔﺎزي‬
105%
Variable Speed Motor
‫ﻣﻮﺗﻮر دور ﻣﺘﻐﻴﺮ‬
110%
Constant Speed Motor
‫ﻣﻮﺗﻮر دور ﺛﺎﺑﺖ‬
100%
Reciprocating Engine
‫ﻣﻮﺗﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬
110%
Nema Class B,C,Da
Gas Turbine
a0 Indicates Governor class as specified in NEMA SM 23.
NEMA SM23 ‫ ﻧﺸﺎن دﻫﻨﺪه ﻃﺒﻘﻪ ﺑﻨﺪي ﮔﺎورﻧﺮ ﻣﻄﺎﺑﻖ‬:‫اﻟﻒ‬
10.2.7 Oil reservoirs and housings that enclose
moving lubricated parts such as bearings, shaft
seals, highly polished parts, instruments, and
control elements shall be designed to minimize
contamination by moisture, dust, and other
foreign matter during periods of operation and
idleness.
‫ ﻣﺨﺎزن روﻏﻦ و ﻣﺤﻔﻈﻪ ﻫﺎﻳﻲ ﻛﻪ اﺟﺰاء ﻣﺘﺤﺮك‬7-2-10
،‫ ﻧﺸﺖ ﺑﻨﺪي ﻫﺎي ﻣﺤﻮر‬،‫روﻏﻦ ﻛﺎري ﺷﺪه ﻣﺜﻞ ﻳﺎﺗﺎﻗﺎن ﻫﺎ‬
‫ و اﺟﺰاء ﻛﻨﺘﺮﻟﻲ را‬،‫ اﺑﺰاردﻗﻴﻖ ﻫﺎ‬،‫اﺟﺰاء ﺑﺴﻴﺎر ﺻﻴﻘﻠﻲ‬
‫ﻣﻲ ﭘﻮﺷﺎﻧﺪ ﺑﺎﻳﺪ ﻃﻮري ﻃﺮاﺣﻲ ﺷﻮﻧﺪ ﻛﻪ ﺣﺪاﻗﻞ آﻟﻮدﮔﻲ ﺑﺎ‬
‫ ﻏﺒﺎر و ﺳﺎﻳﺮ ﻣﻮاد ﺧﺎرﺟﻲ در ﻃﻮل دوره ﻋﻤﻠﻴﺎت و ﻛﺎر‬،‫رﻃﻮﺑﺖ‬
.‫ﻧﻜﺮدن را داﺷﺘﻪ ﺑﺎﺷﻨﺪ‬
45
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
10.2.8 The power at the certified point shall not
exceed 104% of the quoted value with no
negative tolerance on required capacity.
10.2.9 The purchaser shall specify gas
composition(s). The purchaser may also specify
molecular weight, ratio of specific heats (Cp/Cv),
and compressibility factor (Z).
‫ درﺻﺪ ﻣﻘﺪار‬104 ‫ ﺗﻮان در ﻧﻘﻄﻪ ﺗﻀﻤﻴﻨﻲ ﻧﺒﺎﻳﺪ از‬8-2-10
. ‫ﻣﺸﺨﺺ ﺑﺪون رواداري ﻣﻨﻔﻲ در ﻇﺮﻓﻴﺖ ﻻزم ﺑﻴﺸﺘﺮ ﺷﻮد‬
.‫ ﺧﺮﻳﺪار ﺑﺎﻳﺪ ﺗﺮﻛﻴﺐ)ﻫﺎي( ﮔﺎز را ﻣﺸﺨﺺ ﻛﻨﺪ‬9-2-10
‫ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي‬،‫ﺧﺮﻳﺪار ﻫﻤﭽﻨﻴﻦ ﻣﻤﻜﻦ اﺳﺖ ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ‬
. ‫( را ﻣﺸﺨﺺ ﻛﻨﺪ‬Z) ‫( وﻳﮋه و ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬Cp/Cv)
10.2.10 Unless otherwise specified, the vendor
shall use the specified values of flow, the
specified gas composition, and the gas conditions
to calculate molecular weight, ratio of specific
heats (Cp/Cv), and compressibility factor (Z).
The compressor vendor shall indicate his values
on the data sheets with the proposal and use them
to calculate performance data.
‫ ﻓﺮوﺷﻨﺪه ﺑﺎﻳﺪ از‬،‫ ﺑﻪ ﻏﻴﺮ از ﻣﻮارد ﻣﺸﺨﺺ ﺷﺪه‬10-2-10
‫ ﺗﺮﻛﻴﺐ ﻣﺸﺨﺺ ﮔﺎز و ﺷﺮاﻳﻂ‬، ‫ﻣﻘﺎدﻳﺮ ﻣﺸﺨﺺ ﺷﺪه ﺟﺮﻳﺎن‬
‫ ﻧﺴﺒﺖ ﮔﺮﻣﺎﻫﺎي وﻳﮋه‬،‫ﮔﺎز ﺑﺮاي ﻣﺤﺎﺳﺒﻪ ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ‬
‫ ﻓﺮوﺷﻨﺪه‬.‫( اﺳﺘﻔﺎده ﻛﻨﺪ‬Z) ‫( و ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي‬Cp/Cv)
‫ﻛﻤﭙﺮﺳﻮر ﺑﺎﻳﺪ ﻣﻘﺎدﻳﺮ ﺧﻮدش را در ﺑﺮﮔﻪﻫﺎي اﻃﻼﻋﺎت ﺑﺎ‬
‫ﭘﻴﺸﻨﻬﺎد ﺑﻴﺎن ﻛﻨﺪ و از آﻧﻬﺎ ﺑﺮاي ﻣﺤﺎﺳﺒﻪ اﻃﻼﻋﺎت ﻋﻤﻠﻜﺮد‬
.‫اﺳﺘﻔﺎده ﻛﻨﺪ‬
10.2.11 The equipment, including all auxiliaries,
shall be suitable for operation under the
environmental conditions specified by the
purchaser. These conditions shall include
whether the installation is indoors (heated or
unheated) or outdoors (with or without a roof),
maximum and minimum temperatures, unusual
humidity, and dusty or corrosive conditions.
10.2.12 The equipment, including all auxiliaries,
shall be suitable for operation, using the utility
stream conditions specified by the purchaser.
‫ ﺷﺎﻣﻞ ﺗﻤﺎم ﻟﻮازم ﻛﻤﻜﻲ ﺑﺎﻳﺪ ﺑﺮاي ﻛﺎر‬،‫ ﺗﺠﻬﻴﺰات‬11-2-10
‫ﻛﺮد در ﺷﺮاﻳﻂ ﻣﺤﻴﻄﻲ ﻣﺸﺨﺺ ﺷﺪه ﺗﻮﺳﻂ ﺧﺮﻳﺪار ﻣﻨﺎﺳﺐ‬
‫ اﻳﻦ ﺷﺮاﻳﻂ ﺑﺎﻳﺪ ﺷﺎﻣﻞ ﻧﺼﺐ داﺧﻠﻲ )ﮔﺮم ﺷﺪه ﻳﺎ ﮔﺮم‬، ‫ﺑﺎﺷﻨﺪ‬
، ‫ ﺣﺪاﻛﺜﺮ و ﺣﺪاﻗﻞ دﻣﺎ‬، (‫ﻧﺸﺪه( ﻳﺎ ﺧﺎرﺟﻲ )ﺑﺎ ﻳﺎ ﺑﺪون ﺳﻘﻒ‬
. ‫رﻃﻮﺑﺖ ﻏﻴﺮ ﻋﺎدي و ﺷﺮاﻳﻂ ﻏﺒﺎر ﻳﺎ ﺧﻮرﻧﺪﮔﻲ ﺑﺎﺷﺪ‬
‫ ﺑﺎﻳﺪ ﺑﺮاي ﻛﺎر در‬،‫ ﺗﺠﻬﻴﺰات ﺷﺎﻣﻞ ﺗﻤﺎم ﻟﻮازم ﺟﺎﻧﺒﻲ‬12-2-10
‫ﺷﺮاﻳﻂ ﻋﻤﻠﻴﺎﺗﻲ و ﻣﺸﺨﺼﺎت ﺳﺮوﻳﺲ ﻫﺎي ﺟﺎﻧﺒﻲ ﻣﺸﺨﺺ‬
. ‫ ﻣﻨﺎﺳﺐ ﺑﺎﺷﺪ‬،‫ﺷﺪه ﺗﻮﺳﻂ ﺧﺮﻳﺪار‬
10.2.13 The allowable tensile stress used in the
design of the pressure casing (excluding bolting)
for any material shall not exceed 0.25 times the
minimum ultimate tensile strength for the
material at the maximum specified operating
temperature. For cast materials, the allowable
tensile stress shall be multiplied by the
appropriate casting factor as shown in Table 4.
‫ ﺗﻨﺶ ﻛﺸﺸﻲ ﻣﺠﺎز ﻣﻮرد اﺳﺘﻔﺎده در ﻃﺮاﺣﻲ ﭘﻮﺳﺘﻪ‬13-2-10
‫ ﺑﺮاﺑﺮ‬0/25 ‫ﻓﺸﺎري )ﺑﻪ ﻏﻴﺮ از ﭘﻴﭻ ﻫﺎ( ﺑﺮاي ﻫﺮ ﻣﺎده ﻧﺒﺎﻳﺪ از‬
‫ﺣﺪاﻗﻞ ﻣﻘﺎوﻣﺖ ﺗﻨﺸﻲ ﻧﻬﺎﻳﻲ ﺑﺮاي ﻣﺎده در ﺣﺪاﻛﺜﺮ دﻣﺎي‬
‫ ﺗﻨﺶ‬،‫ ﺑﺮاي ﻣﻮاد رﻳﺨﺘﻪ ﮔﺮي ﺷﺪه‬. ‫ﻋﻤﻠﻴﺎﺗﻲ ﺗﺠﺎوز ﻧﻤﺎﻳﺪ‬
‫ﻛﺸﺸﻲ ﻣﺠﺎز ﺑﺎﻳﺪ در ﺿﺮﻳﺐ رﻳﺨﺘﻪ ﮔﺮي ﻣﻨﺎﺳﺐ ﻧﺸﺎن داده‬
. ‫ ﺿﺮب ﺷﻮد‬4 ‫ﺷﺪه در ﺟﺪول‬
TABLE 4—CASTING FACTORS
‫ – ﺿﺮاﻳﺐ رﻳﺨﺘﻪ ﮔﺮي‬4 ‫ﺟﺪول‬
Type of NDE
Casting factor
‫ﻧﻮع ﺗﺴﺘﻬﺎي ﻏﻴﺮﻣﺨﺮب‬
‫ﻋﺎﻣﻞ رﻳﺨﺘﻪ ﮔﺮي‬
0.8
Visual, magnetic particle and/or liquid penetrant
‫ ذره ﻣﻐﻨﺎﻃﻴﺴﻲ و ﻳﺎ ﻣﺎﻳﻊ ﻧﻔﻮذي‬،‫ﺑﺎزدﻳﺪ ﭼﺸﻤﻲ‬
Spot radiography
Ultrasonic
Full radiography
‫رادﻳﻮﮔﺮاﻓﻲ ﻧﻘﻄﻪ اي‬
0.9
‫ﻓﺮاﺻﻮت‬
0.9
‫رادﻳﻮﮔﺮاﻓﻲ ﻛﺎﻣﻞ‬
1.0
10.2.14 The maximum allowable working
pressure of the casing shall be at least equal to
the specified relief valve set pressure. If a relief
valve set pressure is not specified by the
،‫ ﺣﺪاﻛﺜﺮ ﻓﺸﺎر ﻛﺎري ﻣﺠﺎز ﭘﻮﺳﺘﻪ ﺑﺎﻳﺪ ﺣﺪاﻗﻞ‬14-2-10
‫ اﮔﺮ ﻓﺸﺎر ﺗﻨﻈﻴﻤﻲ‬.‫ﻣﺴﺎوي ﻓﺸﺎر ﺗﻨﻈﻴﻤﻲ ﺷﻴﺮ ﺗﺨﻠﻴﻪ ﺑﺎﺷﺪ‬
‫ﺷﻴﺮ ﺗﺨﻠﻴﻪ ﺗﻮﺳﻂ ﺧﺮﻳﺪار ﻣﺸﺨﺺ ﻧﺸﺪه ﺑﺎﺷﺪ ﺑﺎﻳﺪ ﺗﻮﺳﻂ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
purchaser, it must be specified by the vendor.
. ‫ﻓﺮوﺷﻨﺪه ﻣﺸﺨﺺ ﺷﻮد‬
10.2.15 Casings designed for more than one
maximum allowable working pressure are not
permitted. When a cooling jacket is utilized, this
jacket shall have only external connections
between the upper and lower housings.
‫ ﭘﻮﺳﺘﻪﻫﺎﻳﻲ ﻛﻪ ﺑﺮاي ﺑﻴﺶ از ﻳﻚ ﻓﺸﺎر ﻛﺎري‬15-2-10
‫ زﻣﺎﻧﻲ ﻛﻪ از‬.‫ ﻣﺠﺎز ﻧﻤﻲ ﺑﺎﺷﻨﺪ‬،‫ﺣﺪاﻛﺜﺮ ﻃﺮاﺣﻲ ﻣﻲ ﺷﻮﻧﺪ‬
‫ اﻳﻦ ﺟﺪاره ﺑﺎﻳﺪ ﻓﻘﻂ‬،‫ﺟﺪاره ﺧﻨﻚ ﻛﻨﻨﺪه اﺳﺘﻔﺎده ﺷﻮد‬
‫اﺗﺼﺎﻻت ﺧﺎرﺟﻲ ﺑﻴﻦ ﻣﺤﻔﻈﻪ ﻫﺎي ﺑﺎﻻﻳﻲ و ﭘﺎﻳﻴﻨﻲ داﺷﺘﻪ‬
. .‫ﺑﺎﺷﺪ‬
10.2.16 Rotor stiffness shall be adequate to
prevent contact between the rotor bodies and the
casing and between gear-timed rotor bodies at the
most unfavorable specified conditions. Rotor
bodies not integral with the shaft shall be
permanently attached to the shaft to prevent
relative motion under any condition. Structural
welds on rotors shall be full-penetration
continuous welds and shall be stress relieved,
with appropriate ASTM heat treatment
procedure.
‫ ﺳﺨﺘﻲ ﻗﺴﻤﺖ ﮔﺮدﻧﺪه ﺑﺎﻳﺪ ﺑﺮاي ﺟﻠﻮﮔﻴﺮي از‬16-2-10
‫ﺗﻤﺎس ﺑﻴﻦ ﺑﺪﻧﻪ ﻫﺎي ﮔﺮدﻧﺪه و ﭘﻮﺳﺘﻪ و ﺑﻴﻦ ﺑﺪﻧﻪ ﻫﺎي ﮔﺮدﻧﺪه‬
‫ ﺑﺪﻧﻪ ﻫﺎي‬.‫ ﻣﻨﺎﺳﺐ ﺑﺎﺷﺪ‬،‫زﻣﺎﻧﻲ در ﺷﺮاﻳﻂ ﻧﺎﻣﺴﺎﻋﺪ‬-‫دﻧﺪه‬
‫ﮔﺮدﻧﺪه ﻛﻪ ﺑﺎ ﻣﺤﻮر ﻳﻜﭙﺎرﭼﻪ ﻧﻴﺴﺘﻨﺪ ﺑﺎﻳﺪ ﺣﺘﻤﺎً ﺑﺮاي ﺟﻠﻮﮔﻴﺮي‬
.‫از ﺣﺮﻛﺖ ﻧﺴﺒﻲ در ﻫﺮ ﺷﺮاﻳﻄﻲ ﺑﻪ ﻣﺤﻮر ﻣﺘﺼﻞ ﺷﻮﻧﺪ‬
– ‫ﺟﻮﺷﻬﺎي ﺳﺎزه اي در ﮔﺮدﻧﺪه ﺑﺎﻳﺪ ﺟﻮﺷﻬﺎي ﭘﻴﻮﺳﺘﻪ ﺗﻤﺎم‬
‫ﻧﻔﻮذي ﺑﺎﺷﻨﺪ و ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ ﺑﺎ دﺳﺘﻮراﻟﻌﻤﻞ ﻋﻤﻠﻴﺎت ﺣﺮارﺗﻲ‬
.‫ ﺗﻨﺶ زداﻳﻲ ﺷﻮﻧﺪ‬ASTM
10.2.17 Shafts shall be forged steel unless
otherwise approved by the purchaser.
‫ ﻣﺤﻮر ﺑﺎﻳﺪ از ﻓﻮﻻد رﻳﺨﺘﻪ ﮔﺮي ﺷﺪه ﺑﺎﺷﺪ ﻣﮕﺮ ﻏﻴﺮ‬17-2-10
.‫از اﻳﻨﻜﻪ ﺑﻪ ﺗﺎﺋﻴﺪ ﻛﺎرﻓﺮﻣﺎ ﺑﺮﺳﺪ‬
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Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
APPENDICES
‫ﭘﻴﻮﺳﺖ ﻫﺎ‬
APPENDIX A
‫ﭘﻴﻮﺳﺖ اﻟﻒ‬
TABLE A.1 – GENERAL COMPRESSOR LIMITS
‫ ﻣﺤﺪوده ﻫﺎي ﻋﻤﻮﻣﻲ ﻛﻤﭙﺮﺳﻮر‬-1-‫ﺟﺪول اﻟﻒ‬
COMPRESSOR
APPROX. max.
APPROX. max.
APPROX. max.
TYPE
COMMERCIALLY
COMPRESSION
COMPRESSION
‫ﻧﻮع ﻛﻤﭙﺮﺳﻮر‬
USED DISCH.
RATIO PER STAGE
RATIO PER CASE
PRESS. kPa
‫ﻧﺴﺒﺖ ﺣﺪاﻛﺜﺮ ﺗﺮاﻛﻢ ﺗﻘﺮﻳﺒﻲ در‬
OR MACHINE
‫ﺣﺪاﻛﺜﺮ ﻓﺸﺎر ﺧﺮوﺟﻲ ﺗﺠﺎري‬
‫ﻫﺮ ﻣﺮﺣﻠﻪ‬
‫ﻧﺴﺒﺖ ﺣﺪاﻛﺜﺮ ﺗﺮاﻛﻢ ﺗﻘﺮﻳﺒﻲ در‬
‫ﺗﻘﺮﻳﺒﻲ ﻣﻮرد اﺳﺘﻔﺎده‬
Reciprocating
‫ﻫﺮ ﭘﻮﺳﺘﻪ ﻳﺎ ﻣﺎﺷﻴﻦ‬
240,000-345,000
10
‫رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬
Centrifugal
As required
‫ﺑﺮ اﺳﺎس ﻧﻴﺎز‬
20,600-34.500
3-4.5
8-10
690-896
4
4
550-896
1.2-1.5
5-6.5
‫ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬
Rotary displacement
‫ﺟﺎﺑﺠﺎﻳﻲ دوراﻧﻲ‬
Axial flow
‫ﺟﺮﻳﺎن ﻣﺤﻮري‬
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‫)‪IPS-E-PR-750(1‬‬
‫‪ ‬‬
‫‪ ‬‬
‫‪ ‬ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
‫‪ ‬ﻧﻮع ﺣﺮارﺗﻲ‬
‫‪ ‬ﻣﻜﻨﺪه‬
‫‪ ‬ﻧﻮع ﻣﺘﺤﺮك‬
‫‪ ‬ﻧﻮع ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ‬
‫ﺟﺮﻳﺎن ﺷﻌﺎﻋﻲ )ﮔﺮﻳﺰ‬
‫‪ ‬ﺟﺮﻳﺎن ﻣﺤﻮري‬
‫‪ ‬دوراﻧﻲ‬
‫‪ ‬رﻓﺖ و ﺑﺮﮔﺸﺖ‬
‫‪ ‬از ﻣﺮﻛﺰ(‬
‫ﺗﻚ ﻣﺮﺣﻠﻪ اي‬
‫‪ ‬ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫ﺗﻚ ﻣﺮﺣﻠﻪ اي‬
‫ﺑﺎداﻣﻜﻲ)‪ (Lobe‬ﻣﺴﺘﻘﻴﻢ‬
‫ﺗﻚ ﻣﺮﺣﻠﻪاي‬
‫ﺗﻴﻐﻪ ﻫﺎي اﺳﺘﺎﺗﻮر ﺛﺎﺑﺖ‬
‫ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫ﻗﻄﻌﻪ ﺣﻠﺰوﻧﻲ‬
‫ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫‪ ‬ﺗﻴﻐﻪ ﻫﺎي اﺳﺘﺎﺗﻮر ﻣﺘﻐﻴﺮ‬
‫دو ﻧﻴﻤﻪ ﺷﺪه اﻓﻘﻲ‬
‫)ﭘﻴﭽﺸﻲ(‬
‫ﮔﺮداﻧﻨﺪه ﻣﻮﺗﻮر ﮔﺎزي‬
‫دو ﻧﻴﻤﻪ ﺷﺪه ﻋﻤﻮدي)ﺑﺸﻜﻪ اي(‬
‫ﭘﺮه اي ﻟﻐﺰان‬
‫ﻳﻜﭙﺎرﭼﻪ‬
‫‪ ‬دﻧﺪه ﻳﻜﭙﺎرﭼﻪ‬
‫ﺣﻠﻘﻪ‪-‬ﻣﺎﻳﻊ‬
‫‪ ‬‬
‫ﺗﺮاز ﺟﺪا ﺷﺪﻧﻲ‪/‬ﻣﻘﺎﺑﻞ‬
‫‪ ‬ﺟﺮﻳﺎن ﻣﺨﺘﻠﻂ‬
‫‪ ‬‬
‫‪ ‬دﻳﺎﻓﺮاﮔﻢ‬
‫‪Fig. A.1-TYPES OF COMPRESSORS‬‬
‫ﺷﻜﻞ اﻟﻒ‪ -1-‬اﻧﻮاع ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
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TABLE A.2 – ATMOSPHERIC PRESSURE vs ELEVATION
‫ ﻓﺸﺎر آﺗﻤﺴﻔﺮﻳﻚ ﺑﺮﺣﺴﺐ ارﺗﻔﺎع‬-2 -‫ﺟﺪول اﻟﻒ‬
ALTITUDE
(meters)
‫ارﺗﻔﺎع‬
(‫)ﻣﺘﺮ‬
AVERAGE ATMOSPHERIC
PRESSURE [kPa (abs)]
(‫ ﻣﻄﻠﻖ‬kPa) ‫ﻓﺸﺎر ﻣﺘﻮﺳﻂ آﺗﻤﺴﻔﺮ‬
0
100
200
300
400
500
600
700
800
1000
1200
1400
1600
2000
2500
3000
3500
4000
4500
5000
101.325
99.97
98.84
97.93
96.60
95.44
94.54
93.49
92.04
90.03
87.77
85.51
83.42
79.41
74.58
70.06
65.54
61.40
57.71
54.31
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‫)‪IPS-E-PR-750(1‬‬
‫‪ ‬‬
‫‪ ‬‬
‫ﻓﺸﺎر ﺧﺮوﺟﻲ)‪ psi‬ﻧﺴﺒﻲ(‬
‫ﺟﺮﻳﺎن ورودي‬
‫‪ -1‬رﻓﺖ و ﺑﺮﮔﺸﺘﻲ ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫‪1-recip- multi stage‬‬
‫‪ -2‬رﻓﺖ و ﺑﺮﮔﺸﺖ ﺗﻚ ﻣﺮﺣﻠﻪ اي‬
‫‪2- recip single stage‬‬
‫‪ -3‬ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﺗﻚ ﻣﺮﺣﻠﻪ اي‬
‫‪3- center single stage‬‬
‫‪ -4‬ﮔﺮﻳﺰ از ﻣﺮﻛﺰ ﭼﻨﺪ ﻣﺮﺣﻠﻪ اي‬
‫‪4- center multi stage‬‬
‫‪ -5‬ﭼﺮﺧﺸﻲ‪-‬ﻣﺎرﭘﻴﭽﻲ‬
‫‪5- rotary-screw‬‬
‫‪ -6‬ﻣﺤﻮري‬
‫‪6- axial‬‬
‫‪ -7‬دوراﻧﻲ ﺣﻠﻘﻪ‪-‬ﻣﺎﻳﻊ‬
‫‪7- rotary liquid ring‬‬
‫‪ -8‬ﺑﺎداﻣﻜﻲ دوراﻧﻲ ﻣﺴﺘﻘﻴﻢ‬
‫‪8-rotary straight lobe‬‬
‫‪-9‬دوراﻧﻲ ﭘﺮه اي ﻟﻐﺰان‬
‫‪9-rotary sliding vane‬‬
‫‪ -10‬دﻳﺎﻓﺮاﮔﻢ‬
‫‪10-diafragm‬‬
‫‪Fig. A.2-COMPRESSOR COVERAGE CHART‬‬
‫ﺷﻜﻞ اﻟﻒ‪ -2-‬ﻧﻤﻮدار ﭘﻮﺷﺶ ﻋﻤﻠﻴﺎﺗﻲ ﻛﻤﭙﺮﺳﻮر‬
‫‪51‬‬
‫‪ ‬‬
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
TABLE A.3 - CALCULATION OF k
k ‫ ﻣﺤﺎﺳﺒﻪ‬-3-‫ﺟﺪول اﻟﻒ‬
EXAMPLE GAS
DETERMINATION
DETERMINATION
DETERMINATION OF PSEUDO
MIXTURE
OF MIXTURE
OF MCp. MOLAR
CRITICAL PRESSURE pPc AND
‫ﻧﻤﻮﻧﻪ ﻣﺨﻠﻮط ﮔﺎز‬
MOL. MASS
HEAT CAPACITY
TEMPERATURE pTc
‫ﺗﻌﻴﻴﻦ ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ‬
‫ ﻇﺮﻓﻴﺖ ﮔﺮﻣﺎﻳﻲ ﻣﻮﻟﻲ‬MCp. ‫ﺗﻌﻴﻴﻦ‬
pTC ‫ و‬pPc ‫ﺗﻌﻴﻴﻦ ﻓﺸﺎر و دﻣﺎي ﺑﺤﺮاﻧﻲ ﻛﺎذب‬
‫ﻣﺨﻠﻮط‬
Component
Mole
Individual
Name
Farction
Component
y ‫ﺟﺰء ﻣﻮﻟﻲ‬
Mol. Mass
MCp at
‫ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ ﻫﺮ ﺟﺰء‬
70°C
‫اﺳﻢ ﺗﺮﻛﻴﺐ‬
M
Individual Component
p
Y×MC ‫ ﻫﺮ ﺟﺰء در‬MCp
y × MCp
at 70°C
y×M
Component
Component
Critical
Critical
Pressure
Temperature
‫ﻓﺸﺎر ﺑﺤﺮاﻧﻲ ﺟﺰء‬
‫دﻣﺎي ﺑﺤﺮاﻧﻲ ﺟﺰء‬
(‫ ﻣﻄﻠﻖ‬kpa) PC
Pc, kPa (abs)
y × Pc
Tc k
y × Tc
Methane
0.9216
16.04
14.782
37.471
34.533
4640.4
4276.5
190.6
175.6
Ethane
0.0488
30.07
1.467
58.39
2.850
4944.4
241.3
305.6
14.9
Propane
0.0185
44.10
0.816
82.85
1.533
4256.4
78.7
370.0
6.8
i-Butane
0.0039
58.12
0.227
109.397
0.427
3749.0
14.6
406.9
1.6
n-Butane
0.0055
58.12
0.320
109.497
0.602
3658.6
20.1
425.2
2.3
i-Pentane
0.0017
72.15
0.123
134.379
0.228
3333.2
5.7
460.9
0.8
Total=
1.0000
M=
17.735
MCp =
40.173
pP c =
4036.9
pTc =
202.1
MCv = MCp - 8.3143 = 31.859
k = MCp/MCv = 40.173/31.859 = 1.261
Note:
:‫ﻳﺎدآوري‬
For values of MCp other than at 70°C refer
to Table A.4.
‫ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد ﺑﻪ ﺟﺪول‬70 ‫ ﺑﻪ ﻏﻴﺮ از‬MCp ‫ﺑﺮاي ﻣﻘﺎدﻳﺮ‬
.‫ ﻣﺮاﺟﻌﻪ ﺷﻮد‬4-‫اﻟﻒ‬
52
Feb. 2010/ 1388 ‫ﺑﻬﻤﻦ‬ IPS-E-PR-750(1)
TABLE A.4 – MOLAR HEAT CAPACITY MCp (IDEAL-GAS STATE) kJ/(kmol.K)
(‫ )ﺣﺎﻟﺖ ﮔﺎز اﻳﺪه آل‬MCp‫ﻇﺮﻓﻴﺖ ﮔﺮﻣﺎﻳﻲ ﻣﻮﻟﻲ‬-4-‫ﺟﺪول اﻟﻒ‬
53
IPS-E-PR-750(0)
APPENDIX B
‫ﭘﻴﻮﺳﺖ ب‬
B.1 Process Specification Sheet for
Rotadynamic Compressors:
‫ ﺻﻔﺤﻪ ﻣﺸﺨﺼﺎت ﻓﺮآﻳﻨﺪي ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي‬1-‫ب‬
The minimum required information to be
included in process specification sheet shall
be as follows:
‫ﺣﺪاﻗﻞ اﻃﻼﻋﺎت ﻻزم ﻛﻪ ﺑﻪ ﺻﻔﺤﻪ ﻣﺸﺨﺼﺎت ﻓﺮآﻳﻨﺪي اﻓﺰوده‬
:‫ﻣﻴﺸﻮد ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ زﻳﺮ ﺑﺎﺷﺪ‬
‫دوراﻧﻲ ﻣﺘﺤﺮك‬
a) Process requirements
‫اﻟﻒ( اﻟﺰاﻣﺎت ﻓﺮآﻳﻨﺪي‬
- Flow at 1.013 bar (abs) and 0°C,
‫ ﺑﺎر )ﻣﻄﻠﻖ( و ﺻﻔﺮ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬1/013 ‫ ﺟﺮﻳﺎن در‬- Flow at Suction Conditions,
‫ ﺟﺮﻳﺎن در ﺷﺮاﻳﻂ ﻣﻜﺶ‬- Suction Temperature,
‫ دﻣﺎي ﻣﻜﺶ‬- Suction Pressure
‫ ﻓﺸﺎر ﻣﻜﺶ‬- Discharge Pressure
‫ ﻓﺸﺎر ﺧﺮوﺟﻲ‬-
m³/h,
m³/h,
°C ,
kPa(abs),
kPa(abs),
- Discharge Temperature Limitation (if any)
(Normal & Design).
(‫)ﻋﺎدي و ﻃﺮاﺣﻲ‬
(Normal & Design).
(Normal & Design).
(Normal & Design).
(Normal & Design).
(Normal & Design).
(‫ ﻣﺤﺪوده دﻣﺎي ﺧﺮوﺟﻲ )در ﺻﻮرت وﺟﻮد‬- Compression Ratio
(Normal & Design).
‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ‬- Approx. Cp/Cv (at Suction)
(Normal & Design).
(‫ ﺗﻘﺮﻳﺒﻲ )در ﻣﻜﺶ‬Cp/Cv - Compressibility Factor (at Suction)
(Normal & Design).
(‫ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي )در ﻣﻜﺶ‬- Mass Flow
‫ ﺟﺮﻳﺎن ﺟﺮﻣﻲ‬- Estimated Polytropic Head
‫ ﻓﺸﺎر ﻣﻌﺎدل ارﺗﻔﺎع ﺗﻘﺮﻳﺒﻲ ﭘﻠﻲ ﺗﺮوﭘﻴﻚ‬-
kg/h,
m,
(Normal & Design).
(Normal & Design).
- Estimated Bhp Required
‫ ﺗﻮان ﻻزم اﺳﺐ ﺑﺨﺎر‬‫ﺗﺮﻣﺰي ﺗﺨﻤﻴﻨﻲ‬
kW,
(Normal & Design).
- Estimated Gear Loss
‫ اﺗﻼف ﺗﺨﻤﻴﻨﻲ دﻧﺪه‬-
kW,
(Normal & Design).
- Recommended Driver kW
‫ ﺗﻮان ﺗﻮﺻﻴﻪ ﺷﺪه ﮔﺮداﻧﻨﺪه‬- Compressor Speed
‫ ﺳﺮﻋﺖ ﻛﻤﭙﺮﺳﻮر‬-
kW,
r/min,
(Normal & Design).
(Normal & Design).
b) Service
‫ب( ﻛﺎرﺑﺮي‬
- Approximate Gas Composition
(vol% or mol%).
(‫ ﺗﺮﻛﻴﺐ ﺗﻘﺮﻳﺒﻲ ﮔﺎز )درﺻﺪ ﻣﻮﻟﻲ ﻳﺎ درﺻﺪ ﺣﺠﻤﻲ‬54
IPS-E-PR-750(0)
- Average Molecular Mass.
.‫ ﺟﺮم ﻣﻠﻜﻮﻟﻲ ﻣﻴﺎﻧﮕﻴﻦ‬.(‫ ﭼﮕﺎﻟﻲ ﻧﺴﺒﻲ)وزن ﻣﺨﺼﻮص‬.‫ ﺧﻮرﻧﺪﮔﻲ و ﻣﻼﺣﻈﺎت‬-
- Relative Density (Specific Gravity).
- Corrosiveness & Remarks.
c) Site informations
‫ج( اﻃﻼﻋﺎت ﻣﺤﻞ‬
- Elevation of Plant Site from Sea Level,
،‫ ارﺗﻔﺎع ﻣﺤﻞ واﺣﺪ از ﺳﻄﺢ درﻳﺎ‬- Minimum Winter Temperature,
،‫ ﺣﺪاﻗﻞ دﻣﺎي زﻣﺴﺘﺎن‬- Maximum Summer Temperature,
،‫ ﺣﺪاﻛﺜﺮ دﻣﺎي ﺗﺎﺑﺴﺘﺎن‬- Normal Barometer,
‫ ﻓﺸﺎر ﻧﺮﻣﺎل ﺟﻮي‬- Relative Humidity for Process Design
‫ رﻃﻮﺑﺖ ﻧﺴﺒﻲ ﺑﺮاي ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي‬-
d) Available utilities
m.
°C.
°C.
kPa.
%
‫د ( ﺳﺮوﻳﺲ ﻫﺎي ﺟﺎﻧﺒﻲ ﻣﻮﺟﻮد‬
- Cooling water:
max. Inlet Temperature,
‫ آب ﺧﻨﻚ ﻛﻦ‬-
‫ﺣﺪاﻛﺜﺮ دﻣﺎي ورودي‬
max. Outlet Temperature,
‫ﺣﺪاﻛﺜﺮ دﻣﺎي ﺧﺮوﺟﻲ‬
Pressure,
‫ﻓﺸﺎر‬
°C
°C
kPa
Fouling Factor.
‫ﺿﺮﻳﺐ رﺳﻮب ﮔﺬاري‬
- Instrument Air Pressure,
‫ ﻓﺸﺎر ﻫﻮاي اﺑﺰار دﻗﻴﻖ‬- Electric Power for Instruments, volts, Phase
‫ وﻟﺖ و ﻓﺎز‬، ‫ ﺗﻮان اﻟﻜﺘﺮﻳﻜﻲ ﺑﺮاي ادوات اﺑﺰار دﻗﻴﻖ‬-
kPa
Hz.
e) Compressor Location (Outdoor, Indoor).
(‫ ﺧﺎرﺟﻲ‬،‫ﻫ( ﻣﺤﻞ ﻛﻤﭙﺮﺳﻮر )داﺧﻠﻲ‬
f) Instrument Graduation System.
‫و ( ﺳﺎﻣﺎﻧﻪ ﺗﻜﻤﻴﻠﻲ اﺑﺰار دﻗﻴﻖ‬
g) Remarks on Control System.
‫ز ( ﻣﻼﺣﻈﺎت ﺑﺮ روي ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل‬
B.2 Process Specification Sheet for Positive
Displacement Compressors
‫ ﺻﻔﺤﻪ ﻣﺸﺨﺼﺎت ﻓﺮآﻳﻨﺪي ﺑﺮاي ﻛﻤﭙﺮﺳﻮرﻫﺎي‬2-‫ب‬
‫ﺟﺎﺑﺠﺎﻳﻲ ﻣﺜﺒﺖ‬
The minimum required information to be
included in process specification sheet shall be
as follows:
‫ﺣﺪاﻗﻞ اﻃﻼﻋﺎت ﻻزم ﻛﻪ ﺑﻪ ﺻﻔﺤﻪ ﻣﺸﺨﺼﺎت ﻓﺮآﻳﻨﺪي‬
:‫اﻓﺰوده ﻣﻴﺸﻮد ﺑﺎﻳﺪ ﻣﻄﺎﺑﻖ زﻳﺮ ﺑﺎﺷﺪ‬
55
IPS-E-PR-750(0)
a) Process requirements
‫اﻟﻒ( اﻟﺰاﻣﺎت ﻓﺮآﻳﻨﺪي‬
- Flow at 1.013 bar (abs) and 0°C,
m³/h, Normal.
‫ﻋﺎدي‬
،‫ ﺑﺎر )ﻣﻄﻠﻖ( و ﺻﻔﺮ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬1/013 ‫ ﺟﺮﻳﺎن در‬- Flow at 1.013 bar (abs) and 0°C,
m³/h, Rated.
،‫ ﺑﺎر )ﻣﻄﻠﻖ( و ﺻﻔﺮ درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬1/013 ‫ ﺟﺮﻳﺎن در‬- Flow at Suction Conditions,
،‫ ﺟﺮﻳﺎن در ﺷﺮاﻳﻂ ﻣﻜﺶ‬- Suction Temperature
،‫ دﻣﺎي ﻣﻜﺶ‬- Suction Pressure,
،‫ ﻓﺸﺎر ﻣﻜﺶ‬- Discharge Pressure,
‫ﻃﺮاﺣﻲ‬
m³/h, Normal.
°C.
kPa (abs).
kPa (abs) Normal
،‫ ﻓﺸﺎر ﺧﺮوﺟﻲ‬- Discharge Pressure,
‫ﻋﺎدي‬
kPa (abs) Rated.
،‫ ﻓﺸﺎر ﺧﺮوﺟﻲ‬- Differential Pressure,
‫ﻃﺮاﺣﻲ‬
kPa, rated.
،‫ اﺧﺘﻼف ﻓﺸﺎر‬-
‫ﻃﺮاﺣﻲ‬
- Compression Ratio.
،‫ ﻧﺴﺒﺖ ﺗﺮاﻛﻢ‬- Approx. Cp/Cv (at Suction).
،(‫ ﺗﻘﺮﻳﺒﻲ )در ﻣﻜﺶ‬Cp/Cv - Compressibility Factor (at Suction).
،(‫ ﺿﺮﻳﺐ ﺗﺮاﻛﻢ ﭘﺬﻳﺮي )در ﻣﻜﺶ‬- Mass Flow Molecular Mass,
kg/h, Normal.
،‫ ﺟﺮﻳﺎن ﺟﺮﻣﻲ و ﺟﺮم ﻣﻠﻜﻮﻟﻲ‬- Mass Flow Molecular Mass,
‫ﻧﺮﻣﺎل‬
kg/h, Rated.
،‫ ﺟﺮﻳﺎن ﺟﺮﻣﻲ و ﺟﺮم ﻣﻠﻜﻮﻟﻲ‬- Estimated Power Required,
‫اﺳﻤﻲ‬
kW, Normal.
،‫ ﺗﻮان ﺗﺨﻤﻴﻨﻲ ﻻزم‬- Estimated Power Required,
‫ﻧﺮﻣﺎل‬
kW, Rated.
،‫ ﺗﻮان ﺗﺨﻤﻴﻨﻲ ﻻزم‬- Estimated Gear loss,
،‫ اﺗﻼف ﺗﺨﻤﻴﻨﻲ دﻧﺪه‬- Recommended Driver Bhp.,
،‫ ﺗﻮان اﺳﺐ ﺑﺨﺎر ﺗﺮﻣﺰي ﺗﻮﺻﻴﻪ ﺷﺪه ﻣﺤﺮك‬- Compressor Speed Limitation (if any),
،(‫ ﻣﺤﺪودﻳﺖ ﺳﺮﻋﺖ ﻛﻤﭙﺮﺳﻮر )در ﺻﻮرت وﺟﻮد‬- Piston Speed Limitation, (if any),
،(‫ ﻣﺤﺪودﻳﺖ ﺳﺮﻋﺖ ﭘﻴﺴﺘﻮن )در ﺻﻮرت وﺟﻮد‬-
‫اﺳﻤﻲ‬
kW.
kW.
r/min.
m/s.
b) Service
‫ب( ﻛﺎرﺑﺮي‬
- Approximate Gas Composition
(vol% or mol%).
‫ ﺗﺮﻛﻴﺐ ﺗﻘﺮﻳﺒﻲ ﮔﺎز‬- Average Molecular Mass.
.‫ ﺟﺮم ﻣﻠﻜﻮﻟﻲ ﻣﻴﺎﻧﮕﻴﻦ‬- Relative Density (Specific Gravity).
.(‫ ﭼﮕﺎﻟﻲ ﻧﺴﺒﻲ )ﺟﺮم وﻳﮋه‬- Corrosiveness and Relevant Remarks.
.‫ ﺧﻮرﻧﺪﮔﻲ و ﻣﻼﺣﻈﺎت‬-
56
IPS-E-PR-750(0)
c) Site informations
‫ج( اﻃﻼﻋﺎت ﻣﺤﻞ‬
- Elevation of Plant Site From See Level,
m.
،‫ ارﺗﻔﺎع ﻣﺤﻞ واﺣﺪ از ﺳﻄﺢ درﻳﺎ‬- Minimum Winter Temperature,
،‫ ﺣﺪاﻗﻞ دﻣﺎي زﻣﺴﺘﺎن‬-
°C.
- Maximum Summer Temperature,
،‫ ﺣﺪاﻛﺜﺮ دﻣﺎي ﺗﺎﺑﺴﺘﺎن‬-
°C.
- Normal Barometer,
kPa.
،‫ ﻓﺸﺎر ﻧﺮﻣﺎل ﺟﻮي‬- Relative Humidity for Process Design
%
،‫ رﻃﻮﺑﺖ ﻧﺴﺒﻲ ﺑﺮاي ﻃﺮاﺣﻲ ﻓﺮآﻳﻨﺪي‬-
d) Available utilities
‫د( ﺳﺮوﻳﺲ ﻫﺎي ﺟﺎﻧﺒﻲ ﻣﻮﺟﻮد‬
- Cooling water: max. Inlet Temperature,
°C
،‫ ﺣﺪاﻛﺜﺮ دﻣﺎي ورودي‬، ‫آب ﺧﻨﻚ ﻛﻦ‬
max. Outlet Temperature
‫درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬
°C
،‫ﺣﺪاﻛﺜﺮ دﻣﺎي ﺧﺮوﺟﻲ‬
Pressure,
‫درﺟﻪ ﺳﺎﻧﺘﻴﮕﺮاد‬
kPa.
،‫ﻓﺸﺎر‬
‫ﻛﻴﻠﻮﭘﺎﺳﻜﺎل‬
Fouling Factor.
،‫ﺿﺮﻳﺐ رﺳﻮب ﮔﺬاري‬
- Instrument Air Pressure,
،‫ ﻓﺸﺎر ﻫﻮاي اﺑﺰار دﻗﻴﻖ‬- Fuel Gas for Engine :
،‫ ﮔﺎزﺳﻮﺧﺖ ﺑﺮاي ﻣﻮﺗﻮر‬-
mol. mass.
‫ﺟﺮم ﻣﻮﻟﻜﻮﻟﻲ‬
Rel. Density.
‫ﭼﮕﺎﻟﻲ ﻧﺴﺒﻲ‬
kJ/m³, Gross
‫ﺧﺎﻟﺺ‬
- Calorific value,
- Pressure,
،‫ ارزش ﺣﺮارﺗﻲ‬،‫ ﻓﺸﺎر‬-
- Electric Power for Instruments,
kPa
‫ﻛﻴﻠﻮﭘﺎﺳﻜﺎل‬
volt, Phase, Hz.
،‫ ﺗﻮان اﻟﻜﺘﺮﻳﻜﻲ ﺑﺮاي ادوات اﺑﺰار دﻗﻴﻖ‬-
‫ ﺑﺴﺎﻣﺪ‬،‫ ﻓﺎز‬،‫وﻟﺖ‬
e) Compressor Location, Outdoor,
Indoor.
(‫ ﺧﺎرﺟﻲ‬،‫ﻫ( ﻣﺤﻞ ﻛﻤﭙﺮﺳﻮر )داﺧﻠﻲ‬
f) Instrument Graduation System.
‫و ( ﺳﺎﻣﺎﻧﻪ ﺗﻜﻤﻴﻠﻲ اﺑﺰار دﻗﻴﻖ‬
g) Remarks on Control System.
‫ز ( ﻣﻼﺣﻈﺎت ﺑﺮ روي ﺳﺎﻣﺎﻧﻪ ﻛﻨﺘﺮل‬
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‫‪APPENDIX C‬‬
‫ﭘﻴﻮﺳﺖ ج‬
‫‪TYPICAL COMPRESSORS‬‬
‫‪FIGURES‬‬
‫ﻧﻤﻮﻧﻪ ﺷﻜﻠﻬﺎي ﻛﻤﭙﺮﺳﻮرﻫﺎ‬
‫ﻛﻠﻴﺪ‪:‬‬
‫‪ -1‬ﺑﺪﻧﻪ ‪ -2‬ﮔﺮدﻧﺪه ﻧﺮي ‪ -3‬ﮔﺮدﻧﺪه ﻣﺎدﮔﻲ‪ -4‬ﻧﺸﺖ ﺑﻨﺪي ﻣﺤﻮر ‪ -5‬ﻳﺎﺗﺎﻗﺎن ﻣﺤﻮري ‪ -6‬دﻧﺪه زﻣﺎﻧﻲ ‪ -7‬ﭘﻮﺷﺶ اﻧﺘﻬﺎﻳﻲ ‪ -8‬ﻣﺤﻮر ﮔﺮداﻧﻨﺪه‬
‫‪Fig. C.1-TYPICAL SCREW COMPRESSOR‬‬
‫ﺷﻜﻞ ج‪-1-‬ﻧﻤﻮﻧﻪ ﻛﻤﭙﺮﺳﻮر ﭘﻴﭽﺸﻲ‬
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‫‪ ‬ﭘﻮﺳﺘﻪ‬
‫‪ ‬اﺗﺼﺎل اﺳﺘﺎﺗﻮر‬
‫‪ ‬ﻣﺤﻔﻈﻪ ورودي‬
‫ﭘﺮه راﻫﻨﻤﺎي ورودي‬
‫‪ ‬ﻣﺤﻔﻈﻪ ﺧﺮوﺟﻲ‬
‫‪ ‬ﭘﺮواﻧﻪ‬
‫ﻣﺠﻤﻮﻋﻪ ﻳﺎﺗﺎﻗﺎن و‬
‫‪ ‬ﻓﻠﻨﺞ ﻣﻜﺶ‬
‫ﻧﺸﺖ ﺑﻨﺪ ﺧﺮوﺟﻲ ‪ ‬‬
‫ﭘﻴﺴﺘﻮن ﺗﻮازن‬
‫‪ ‬ﻓﻠﻨﺞ ﺧﺮوﺟﻲ‬
‫‪ ‬اﺳﺘﺎﺗﻮر‬
‫ﻃﻮﻗﻪ اﺗﺼﺎل ﻏﻼف‬
‫ﻣﺴﻴﺮ ﺗﻮزﻳﻊ ‪ ‬‬
‫ﻣﺠﻤﻮﻋﻪ ﻳﺎﺗﺎﻗﺎن و‬
‫ﺗﻮازن ‪ ‬‬
‫ﻧﺸﺖ ﺑﻨﺪ ورودي ‪ ‬‬
‫‪Fig. C.2-TYPICAL CENTRIFUGAL COMPRESSOR‬‬
‫ﺷﻜﻞ ج‪ -2-‬ﻧﻮع ﻛﻤﭙﺮﺳﻮر ﮔﺮﻳﺰ از ﻣﺮﻛﺰ‬
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‫‪ ‬روﻏﻦ ﻛﺎري ﺳﻴﻠﻨﺪر‬
‫‪ ‬ﺷﻴﺮ ﻣﻜﺶ‬
‫ﻛﺎﺳﻪ ﻧﻤﺪ‬
‫‪ ‬روﻏﻨﻜﺎري ﺷﺪه‬
‫ﻧﮕﻬﺪارﻧﺪه‬
‫اﻧﺘﻬﺎي ﻣﻴﻠﻪ‬
‫ﻧﮕﻬﺪارﻧﺪه‬
‫‪ ‬ﺳﻴﻠﻨﺪر‬
‫‪ ‬ﺷﻴﺮﻫﺎي ﺗﺨﻠﻴﻪ‬
‫ﺑﺪﻧﻪ ﺳﻴﻠﻨﺪر‬
‫‪ ‬ﻓﻮﻻدي‬
‫‪Fig. C-3-TYPICAL RECIPROCATING COMPRESSOR‬‬
‫ﺷﻜﻞ ج‪-3-‬ﻧﻤﻮﻧﻪ ﻛﻤﭙﺮﺳﻮر رﻓﺖ و ﺑﺮﮔﺸﺘﻲ‬
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