US20170045315A1 - Subsea cooler - Google Patents

Subsea cooler Download PDF

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Publication number
US20170045315A1
US20170045315A1 US15/307,795 US201515307795A US2017045315A1 US 20170045315 A1 US20170045315 A1 US 20170045315A1 US 201515307795 A US201515307795 A US 201515307795A US 2017045315 A1 US2017045315 A1 US 2017045315A1
Authority
US
United States
Prior art keywords
pipe
flow channel
housing
subsea cooler
cooler according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US15/307,795
Other languages
English (en)
Inventor
Erik Baggerud
Idun Bente TILLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FMC Kongsberg Subsea AS
Original Assignee
FMC Kongsberg Subsea AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by FMC Kongsberg Subsea AS filed Critical FMC Kongsberg Subsea AS
Assigned to FMC KONGSBERG SUBSEA AS reassignment FMC KONGSBERG SUBSEA AS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BAGGERUD, ERIK, Tiller, Idun Bente
Publication of US20170045315A1 publication Critical patent/US20170045315A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/004—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using protective electric currents, voltages, cathodes, anodes, electric short-circuits
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B36/00—Heating, cooling or insulating arrangements for boreholes or wells, e.g. for use in permafrost zones
    • E21B36/001—Cooling arrangements
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B41/00—Equipment or details not covered by groups E21B15/00 - E21B40/00
    • E21B41/0007—Equipment or details not covered by groups E21B15/00 - E21B40/00 for underwater installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/14—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically both tubes being bent

Definitions

  • the present invention relates to compact cooler designs for subsea applications.
  • Subsea coolers are well-known. Due to the environment in which they are used, several challenges not commonly encountered in non-subsea coolers must be addressed. Examples of subsea coolers, for cooling a well flow such as a hydrocarbon flow, are disclosed in for example the applicant's own published application WO 2011008101 A1, which is hereby incorporated by reference in its whole, or in Norwegian patent NO 330761 B1. Other known subsea coolers are described in WO 2010110674 A2 and WO 2010110676 A2.
  • a common solution for subsea coolers is the use of passive coolers.
  • the fluid to be cooled e.g. a well flow
  • the common volume of cooling fluid i.e. seawater.
  • Large amounts of seawater pass through the common volume at a relatively slow rate due to natural convection, i.e. the seawater rises through the cooler since it is heated by the fluid to be cooled.
  • the design of passive coolers makes it difficult to obtain a compact cooler due to restraints caused by the rate of heat transfer, the required distance between the cooling fluid pipes etc.
  • a potential solution to at least some of the disadvantages of a passive cooler solution is the use of active coolers having a “pipe-in-pipe” solution.
  • a first pipe containing the fluid to be cooled is surrounded by a second pipe (or an element having a channel through which the first pipe is arranged).
  • the inner wall of the second pipe (or element channel) and the outer wall of the first pipe delimit a flow channel through which the cooling fluid is passed.
  • the rate of the cooling fluid is controlled by a pump.
  • the advantages of a “pipe-in-pipe” solution are the increased temperature control (i.e. increased control of cooling effect) and, as a consequence of being an active cooler, the possibility of designing a more compact cooler.
  • the present invention provides a subsea cooler design which alleviates at least some of the disadvantages related to the use of “pipe-in-pipe” coolers subsea.
  • the present invention provides a subsea cooler design which alleviates at least some of the disadvantages of the prior art coolers.
  • the invention provides a subsea cooler comprising at least one pipe and a housing, wherein
  • fluidly connected in relation to the flow channel is intended to mean a connection, such as a conduit, which ensures that cooling fluid is transferred from the inlet to the flow channel and from the flow channel to the outlet.
  • the flow channel is formed by at least a first inner surface and at least a second inner surface of the housing, and where the first inner surface extend along a straight section of the pipe, and the second inner surface extend along at least parts of a bend section, wherein a sacrificial anode is arranged at the second inner surface.
  • the second inner surface may form at least parts of a flow channel along, and surrounding, a bend section.
  • the second inner surface may be provided at the outside of a bend to form at least parts of the flow channel around the bend.
  • the first and second inner surfaces may form a continuous flow channel for a fluid at the outside of the connected straight and bend sections of the pipe.
  • the second inner surface may also be described as being situated on the outside of a bend section.
  • the term “outside of a bend section” is intended to mean that the second inner surface of the housing is situated at a distance to the bend section pipe and also being arranged at the outside of the bend of said bend section. At least parts of the second inner surface may advantageously be perpendicular to the first inner surface.
  • the flow channel is formed by at least a first inner surface and at least a second inner surface of the housing, and where the first inner surface extend along a straight section of the pipe, and the second inner surface extend along at least parts of a bend section, wherein a sacrificial anode is arranged at the first inner surface, preferably the anode is partly embedded in the first inner surface such that a substantially unobstructed flow channel is obtained.
  • each bend section of the pipe is in electrical contact with a sacrificial anode.
  • the at least one sacrificial anode is in electrical contact with the pipe via an electrical conductor, such as a wire.
  • At least a part of at least one of the inner surfaces of the housing is made in a non-metallic material.
  • a further electrical conductor connects the at least one sacrificial anode to the pipe, such that a closed circuit is formed between the pipe and the anode.
  • the cross-sectional area of the flow channel is larger at the bend sections than at the straight sections, said cross-section in a plane perpendicular to a centerline of the pipe.
  • the flow channel comprises at least one cavity arranged such that, during use, corrosion products from the sacrificial anode may accumulate in said cavity by gravitation and/or by being pushed to said cavity by a cooling fluid flow.
  • the cavity is arranged below a bend section.
  • the straight sections of the pipe comprises multiple fins in the longitudinal direction of the corresponding straight section, preferably the height (h) of the fins is such that the fins are able to support the pipe against the first inner surface.
  • the subsea cooler comprises multiple parallel arranged pipes, wherein the outlets of the pipes are connected to a common outlet header pipe and the inlets of the pipes are connected to a common inlet header pipe.
  • the housing have multiple housing elements comprising at least a first housing element which include the first inner surface and at least a second housing element which include at least one of the second inner surfaces.
  • the first housing element comprises a block having multiple through-bores, each bore comprising a first inner surface.
  • the second housing element is arranged to enclose multiple parallel bend sections.
  • the second housing element comprises at least one cavity arranged such that, during use, corrosion products from the sacrificial anode may accumulate in said cavity by gravitation.
  • FIG. 1 shows a longitudinal and a transverse cross-section of a typical pipe-in-pipe arrangement.
  • FIG. 2 shows the transverse cross-sections of two alternative pipe-in-pipe arrangements.
  • FIGS. 3 a and 3 b is a cross-sectional view of a subsea cooler according to the invention.
  • FIGS. 4 a -4 d show different sectional views of the subsea cooler illustrated in FIGS. 3 a and 3 b.
  • FIG. 5 is a cross-sectional view of an alternative embodiment of a subsea cooler according to the invention.
  • FIGS. 6 a -6 e show different sectional views of a subsea cooler according to the invention having an alternative housing solution.
  • FIG. 7 is a cross-sectional view of a flow channel comprising a cavity for corrosion products.
  • FIG. 8 is a transverse cross-sectional view of two alternatives of pipe-in-pipe solutions comprising longitudinal fins.
  • FIG. 1 The principle of pipe-in-pipe cooler solutions is shown in FIG. 1 , wherein a first pipe 1 is surrounded by a second pipe, or housing 4 .
  • a flow channel 8 is formed between an inner surface 7 of the housing and the first pipe.
  • a cooling fluid is transported through the flow channel 8
  • a fluid to be cooled e.g. a process fluid such as gas and/or oil
  • the direction of the two separate fluid flows is opposite the other, i.e. the flows are counter-current.
  • the design of the inner surface of the housing 4 may be varied to obtain different transverse cross-sections of the flow channel 8 .
  • FIG. 3 a A cross-section of a subsea cooler according to the invention is shown in FIG. 3 a.
  • the cooler comprises a pipe 1 surrounded by a housing 4 .
  • the pipe comprises both straight sections 5 and bend sections 6 .
  • a flow channel 8 is formed between an inner surface 7 , 13 of the housing and the pipe.
  • the pipe 1 includes an inlet 2 and an outlet 3 for a fluid to be cooled, e.g. a process fluid, and the flow channel comprises an inlet 9 and an outlet 10 for a cooling fluid, e.g. seawater.
  • the inlet 9 of the flow channel is connected to a pumping element 20 .
  • corrosion is a common problem, especially when the cooler fluid is seawater.
  • a cooler according to the invention i.e.
  • sacrificial anodes 11 are arranged outside of each bend section 6 , and connected to the pipe via an electrical conductor 12 .
  • sacrificial anodes are arranged near the inlet 2 and the outlet 3 of the pipe.
  • FIG. 3 b A magnified view of a bend section 6 connected to a sacrificial anode 11 outside of said section is shown in FIG. 3 b.
  • the anode is connected to the pipe via an electrical conductor (e.g. a wire) and a clamp 23 .
  • the electrical conductor may be any connection or contact allowing an electrical current to pass between the pipe 1 and the sacrificial anode.
  • the housing 4 e.g. pipes having fins 15 , FIG. 8
  • the housing is made of a metal
  • the anode 11 is in contact with the housing 4
  • a separate connection between the anode and pipe is redundant since electrical current may pass from the pipe via the housing to the anode.
  • FIG. 4 a - 4 d Sectional views of the cooler in FIG. 3 are shown in FIG. 4 a - 4 d.
  • a top section, a mid section and a bottom section is outlined in FIG. 4 a.
  • the sectional views of FIGS. 4 b -4 d are shown in a horizontal plane perpendicular to the vertical plane of the cross-section in FIG. 4 a.
  • the use of the terms vertical and horizontal are only for illustrative purposes and does not imply any required direction for arranging the cooler during use.
  • the cooler comprises multiple parallel pipes 1 .
  • the outlet 3 of each pipe is connected to a common outlet header pipe 16
  • the inlet 2 of each pipe is connected to a common inlet header pipe 17 .
  • the flow channels 8 are fluidly connected to the flow channel inlet 9 via a common inlet header 21 , and to the flow channel outlet 10 via a common outlet header 22 .
  • FIG. 5 An alternative embodiment of a cooler according to the invention is shown in FIG. 5 .
  • the sacrificial anodes 11 are arranged along the straight sections 5 of the pipe 1 , in addition to sacrificial anodes arranged near the inlet 2 and the outlet 3 of the pipe.
  • the anodes 11 are arranged in the flow channel 8 at the straight sections 5 it is preferred that the anodes are partly embedded in the inner surface 7 of the housing.
  • the flow channel is not substantially restricted by the anodes.
  • FIG. 6 a - e A further embodiment of a cooler according to the invention is shown in FIG. 6 a - e.
  • a top section, a mid section, a bottom section and an A-A cross-section are outlined in FIG. 6 a.
  • the sectional views of FIGS. 6 b -6 d are shown in a horizontal plane perpendicular to the vertical plane of the cross-section in FIG. 6 a.
  • the use of the terms vertical and horizontal are only for illustrative purposes and does not imply any required direction for arranging the cooler during use.
  • the housing is made up of multiple housing elements 18 , 24 .
  • the first housing element is a block 18 comprising multiple through-bores 19 .
  • the through-bores are for accommodating at least parts of the straight section of each pipe.
  • a second housing element comprises longitudinal boxes 24 .
  • the boxes cover multiple parallel bend sections 6 , and form fluid tight connections with the block 18 , thereby forming multiple flow channels 8 surrounding the pipes 1 .
  • sacrificial anodes 11 are arranged at an inner surface of the boxes.
  • the cooler may advantageously comprise cavities 14 in the flow channel 8 .
  • the cavities 14 are arranged such that at least some of the corrosion products, if/when they separate from the sacrificial anode 11 , are accumulated in the cavities 14 due to gravity.
  • FIG. 7 A cross-sectional view of a bend section 6 comprising a cavity 14 in the surrounding housing element 4 , or flow channel 8 , is shown in FIG. 7 .
  • a significant part of the corrosion products formed at the sacrificial anode 11 will accumulate in the cavity 14 due to gravity.
  • Such a cavity 14 will also be beneficial when the sacrificial anode 11 is arranged along a straight section 5 of the pipe 1 . Corrosion products will then be pushed or led in the direction of the flow, and finally accumulate in the cavity 14 in a similar manner as when the sacrificial anode 11 is outside the bend section 6 .
  • the design of the cavity may also include an element which reduces turbulence in the cavity. Such element may for instance be a lip at the edge of the cavity.
  • the inner pipe 1 In pipe-in-pipe coolers, the inner pipe 1 must be supported to keep its position in the flow channel 8 .
  • a solution for obtaining such support is to provide the straight sections 5 of the pipe(s) with fins 15 , see FIG. 8 .
  • the fins 15 extend in the longitudinal direction of the pipe, and have a height (h) such that the fins 15 are able to support the pipe 1 against an inner surface of the outer pipe (or housing 4 ).
  • a further advantage of fins is an increased heat transfer area.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Geochemistry & Mineralogy (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Prevention Of Electric Corrosion (AREA)
  • Lasers (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
US15/307,795 2014-04-30 2015-04-29 Subsea cooler Abandoned US20170045315A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
NO20140561A NO338506B1 (no) 2014-04-30 2014-04-30 Undervannskjøler
NO20140561 2014-04-30
PCT/EP2015/059343 WO2015165969A2 (en) 2014-04-30 2015-04-29 Subsea cooler

Publications (1)

Publication Number Publication Date
US20170045315A1 true US20170045315A1 (en) 2017-02-16

Family

ID=53052846

Family Applications (1)

Application Number Title Priority Date Filing Date
US15/307,795 Abandoned US20170045315A1 (en) 2014-04-30 2015-04-29 Subsea cooler

Country Status (7)

Country Link
US (1) US20170045315A1 (no)
EP (1) EP3137838A2 (no)
AU (1) AU2015254666A1 (no)
BR (1) BR112016024973A2 (no)
NO (1) NO338506B1 (no)
SG (1) SG11201608394RA (no)
WO (1) WO2015165969A2 (no)

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5484651A (en) * 1977-12-19 1979-07-05 Babcock Hitachi Kk Anticorrosion apparatus for heating pipe
JPS5888598A (ja) * 1981-11-24 1983-05-26 Diesel Kiki Co Ltd アルミニウム合金製熱交換器
JPS58182096A (ja) * 1982-04-19 1983-10-24 Nissan Motor Co Ltd アルミニウム製の熱交換器
JPS60105849A (ja) * 1983-11-14 1985-06-11 Matsushita Electric Ind Co Ltd 給湯機器の熱交換器
US5802864A (en) * 1997-04-01 1998-09-08 Peregrine Industries, Inc. Heat transfer system
JPH11141997A (ja) * 1997-11-10 1999-05-28 Gastar Corp 熱交換器の腐食防止装置
JP2000248325A (ja) * 1999-02-26 2000-09-12 Denso Corp アルミニウム合金配管材
US20020108849A1 (en) * 2000-11-29 2002-08-15 Shuichi Inagaki Antifouling system for structure exposed to seawater and heat exchanger
WO2007013439A1 (ja) * 2005-07-28 2007-02-01 Showa Denko K.K. 熱交換器
US20100126698A1 (en) * 2008-11-21 2010-05-27 Caterpillar Inc. Heat exchanger including selectively activated cathodic protection useful in sulfide contaminated environments
US20120279691A1 (en) * 2011-05-06 2012-11-08 GM Global Technology Operations LLC Heat exchanger for a motor vehicle air conditioning system
WO2013002644A1 (en) * 2011-06-30 2013-01-03 Aker Subsea As Subsea compression assembly
JP2013224758A (ja) * 2012-04-20 2013-10-31 Daikin Industries Ltd 水冷式熱交換器
US8739882B2 (en) * 2007-06-01 2014-06-03 Fmc Kongsberg Subsea As Subsea cooler
US20150292824A1 (en) * 2012-02-20 2015-10-15 Aker Subsea As Subsea heat exchanger, cleaning tool and appurtenant method

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102428250B (zh) 2009-03-27 2014-11-12 弗拉莫工程公司 海底冷却器
GB2468920A (en) 2009-03-27 2010-09-29 Framo Eng As Subsea cooler for cooling a fluid flowing in a subsea flow line
NO333597B1 (no) 2009-07-15 2013-07-15 Fmc Kongsberg Subsea As Undervannskjoler
NO334268B1 (no) * 2011-04-15 2014-01-27 Apply Nemo As En undersjøisk kjøleanordning
WO2013131574A1 (en) * 2012-03-08 2013-09-12 Statoil Petroleum As Subsea processing

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5484651A (en) * 1977-12-19 1979-07-05 Babcock Hitachi Kk Anticorrosion apparatus for heating pipe
JPS5888598A (ja) * 1981-11-24 1983-05-26 Diesel Kiki Co Ltd アルミニウム合金製熱交換器
JPS58182096A (ja) * 1982-04-19 1983-10-24 Nissan Motor Co Ltd アルミニウム製の熱交換器
JPS60105849A (ja) * 1983-11-14 1985-06-11 Matsushita Electric Ind Co Ltd 給湯機器の熱交換器
US5802864A (en) * 1997-04-01 1998-09-08 Peregrine Industries, Inc. Heat transfer system
JPH11141997A (ja) * 1997-11-10 1999-05-28 Gastar Corp 熱交換器の腐食防止装置
JP2000248325A (ja) * 1999-02-26 2000-09-12 Denso Corp アルミニウム合金配管材
US20020108849A1 (en) * 2000-11-29 2002-08-15 Shuichi Inagaki Antifouling system for structure exposed to seawater and heat exchanger
WO2007013439A1 (ja) * 2005-07-28 2007-02-01 Showa Denko K.K. 熱交換器
US8739882B2 (en) * 2007-06-01 2014-06-03 Fmc Kongsberg Subsea As Subsea cooler
US20100126698A1 (en) * 2008-11-21 2010-05-27 Caterpillar Inc. Heat exchanger including selectively activated cathodic protection useful in sulfide contaminated environments
US20120279691A1 (en) * 2011-05-06 2012-11-08 GM Global Technology Operations LLC Heat exchanger for a motor vehicle air conditioning system
WO2013002644A1 (en) * 2011-06-30 2013-01-03 Aker Subsea As Subsea compression assembly
US20150292824A1 (en) * 2012-02-20 2015-10-15 Aker Subsea As Subsea heat exchanger, cleaning tool and appurtenant method
JP2013224758A (ja) * 2012-04-20 2013-10-31 Daikin Industries Ltd 水冷式熱交換器

Also Published As

Publication number Publication date
NO20140561A1 (no) 2015-11-02
NO338506B1 (no) 2016-08-29
BR112016024973A2 (pt) 2017-08-15
WO2015165969A2 (en) 2015-11-05
EP3137838A2 (en) 2017-03-08
SG11201608394RA (en) 2016-11-29
AU2015254666A1 (en) 2016-10-27
WO2015165969A3 (en) 2016-01-07

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Owner name: FMC KONGSBERG SUBSEA AS, NORWAY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BAGGERUD, ERIK;TILLER, IDUN BENTE;SIGNING DATES FROM 20161209 TO 20161214;REEL/FRAME:040938/0487

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE