EP2199723A1 - Wärmetauscher - Google Patents

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Publication number
EP2199723A1
EP2199723A1 EP08171770A EP08171770A EP2199723A1 EP 2199723 A1 EP2199723 A1 EP 2199723A1 EP 08171770 A EP08171770 A EP 08171770A EP 08171770 A EP08171770 A EP 08171770A EP 2199723 A1 EP2199723 A1 EP 2199723A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plate
plates
compensation
end plate
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.)
Granted
Application number
EP08171770A
Other languages
English (en)
French (fr)
Other versions
EP2199723B1 (de
Inventor
Ralf Blomgren
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.)
Alfa Laval Vicarb SAS
Alfa Laval Corporate AB
Original Assignee
Alfa Laval Vicarb SAS
Alfa Laval Corporate AB
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
Priority to EP08171770A priority Critical patent/EP2199723B1/de
Application filed by Alfa Laval Vicarb SAS, Alfa Laval Corporate AB filed Critical Alfa Laval Vicarb SAS
Priority to AT08171770T priority patent/ATE553349T1/de
Priority to KR1020117013880A priority patent/KR101286360B1/ko
Priority to JP2011541286A priority patent/JP5405589B2/ja
Priority to PCT/EP2009/066144 priority patent/WO2010069756A1/en
Priority to CN2009801516518A priority patent/CN102265109A/zh
Priority to US13/133,423 priority patent/US20110259562A1/en
Publication of EP2199723A1 publication Critical patent/EP2199723A1/de
Application granted granted Critical
Publication of EP2199723B1 publication Critical patent/EP2199723B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to a heat exchanger comprising a plurality of compensation plates that will improve the resistance to thermal fatigue of the heat exchanger.
  • Plate heat exchangers are used throughout industry as standard equipment for efficient heating, cooling, heat recovery, condensation and evaporation. Heat exchangers may be of different types and designs, depending on the type of medium that is to be heated or cooled.
  • a plate-and-shell heat exchanger is the plate-and-shell type. This type is well suited for uses involving high pressures and high temperatures.
  • a plate-and-shell heat exchanger comprises a pack of corrugated, circular metal plates housed in a vessel.
  • the heat transfer surface of the heat exchanger is formed by thin corrugated discs stacked and welded on top of each other, which creates a process channel between the plates.
  • the fluid for the process channel is led into the plate pack via ports welded into the discs and to an end plate of the vessel, and is distributed into the process channel between the plates.
  • the corrugated discs are alternately welded at the outer circumference of the discs and at the port holes, thereby creating alternate fluid channels.
  • the inlet and outlet ports for the process channel are positioned in the end plates, either in the same end plate or in both end plates.
  • the inlet and outlet ports for the shell side of the heat exchanger are welded in the side wall of the vessel.
  • the flow through the heat exchanger may be of either a counter-current, a cocurrent or a cross flow type.
  • US 7004237 B2 describes a plate-and-shell type heat exchanger for fluids, in which a spring device compensates for longitudinal thermal expansion of the heat exchanger core.
  • An object of the invention is therefore to provide a heat exchanger where stress due to thermal expansion at the inlet and outlet region is minimized.
  • a heat exchanger comprising a housing having a first end plate, a second end plate and a shell, where the first end plate is provided with an inlet port and the first or the second end plate is provided with an outlet port, and further comprising a plurality of corrugated heat exchanger plates having ridges and grooves, where the heat exchanger plates are fixedly attached to each other, such that a first flow channel is created between the heat exchanger plates, the object of the invention is achieved in that the heat exchanger further comprises a plurality of compensation plates positioned between the heat exchanger plates and at least one of the end plates.
  • a heat exchanger is obtained in which the stress on the joints between the inlet and outlet ports and the heat exchanger plates are reduced. This will allow the heat exchanger to be able to withstand a greater temperature gradient than existing heat exchangers.
  • the heat exchanger can be used in areas where fast temperature cycling is present. The heat exchanger can also be used in areas where higher temperature differences are present. The operating range of the heat exchanger is thus increased.
  • the compensation plates are fixedly attached to the heat exchanger plates on one side and to the inlet and outlet ports on the other side. This is advantageous in that a heat exchanger that can withstand high pressures is obtained, compared with heat exchangers having sealing gaskets.
  • the pattern of the compensation plates comprises concentric ridges and grooves.
  • the advantage of this is that the radial stiffness of the compensation plates is reduced compared with existing heat exchanger plate patterns.
  • the flank angle of the compensation plates is smaller than the flank angel of the heat exchanger plates.
  • the flank angle of the compensation plates is less than 30 degrees. The advantage of this is that the radial stiffness can be reduced further.
  • the compensation plate comprises a circular opening in the centre of the compensation plate.
  • the compensation plate comprises a pressure plate in the central opening of the compensation plate.
  • the compensation plate and the pressure plate are attached to each other.
  • the advantage of this is that the handling of the compensation plates and the assembly of the heat exchanger is facilitated.
  • Fig. 1 shows a heat exchanger of the plate-and-shell type.
  • a heat exchanger is suitable for most applications, such as general cooling and heating duties, condensation, evaporation, reboiling and steam heating. It is especially suitable for handling applications with high temperatures and/or high pressures.
  • the shown heat exchanger is circular, having a round housing with two fixedly attached endplates.
  • the heat exchanger 1 comprises a housing 30 made up of end plates 6, 7 and a shell 8.
  • the shell 8 is in this example circular, but other shapes, e.g. elliptical, are conceivable.
  • the heat exchanger 1 further comprises four ports 2, 3, 4, 5 that will constitute either inlet ports or outlet ports to the heat exchanger, depending on the use and configuration of the heat exchanger.
  • port 2 is the inlet port
  • port 3 is the outlet port for the first flow channel, which in this example is the flow channel on the plate side, i.e. through the heat exchanger plates.
  • Inlet port 2 and outlet port 3 are in a first embodiment both positioned in the first end plate 6, close to the outer edge of end plate 6.
  • Port 4 is the inlet port for the flow channel of the shell side of the heat exchanger and port 5 is the outlet port for the shell side flow channel. Ports 4 and 5 are positioned in the shell 8 of the heat exchanger.
  • a second end plate 7 closes the heat exchanger.
  • the end plates 6 and 7 are fixed to the shell in a rigid way, allowing for a high pressure in the heat exchanger.
  • the end plates 6, 7 may either be welded to the housing, or fixed to the housing with bolts and a flange.
  • the heat exchanger may be provided with more than one plate side flow channel.
  • the heat exchanger may in this case be divided into different flow channels, and the end plates will have more than one inlet and outlet ports.
  • Fig. 2 shows schematically the plate side flow channel for the first embodiment of the heat exchanger.
  • a flow channel can be referred to as a U-type flow pattern.
  • a fluid enters the heat exchanger through the inlet port 2 and flows through the inlet flow duct 32.
  • the fluid is distributed from the inlet flow duct 32 through the heat exchanger plate stack 17, where the heat exchange takes place. Since the pressure drop in the inlet flow duct is much lower than the pressure drop through the heat exchanger plate stack, the fluid is distributed in a substantially even way over the heat transfer surface of the heat exchanger.
  • the fluid leaves the heat exchanger through the outlet flow duct 33 and the outlet port 3.
  • the flow path is illustrated with arrows in the figure.
  • the heat exchanger further comprises a compensation plate stack 21 positioned between the first end plate 6 and the heat exchanger plate stack 17. The compensation plate will be described below.
  • Fig. 3 shows schematically the plate side flow channel for a second embodiment of the heat exchanger, in which the inlet port 2 is positioned in the first end plate 6 and the outlet port 3 is positioned in the second end plate 7.
  • a flow channel can be referred to as a Z-type flow pattern.
  • a fluid enters the heat exchanger through the inlet port 2 and flows through the inlet flow duct 32.
  • the fluid is distributed from the inlet flow duct 32 through the heat exchanger plate stack 17, where the heat exchange takes place in the same way as described above.
  • the fluid leaves the heat exchanger through the outlet flow duct 33 and the outlet port 3.
  • the flow path is illustrated with arrows in the figure.
  • a compensation plate stack 21 is positioned between the first end plate 6 and the heat exchanger plate stack 17 and another compensation plate stack 21 is positioned between the second end plate 7 and the heat exchanger plate stack 17.
  • a compensation plate stack 21 is positioned between the first end plate 6 and the heat exchanger plate stack 17 and another compensation plate stack 21 is positioned between the second end plate 7 and the heat exchanger plate stack 17.
  • the inlet port 2 is arranged along an inlet axis 34 and the outlet port 3 is arranged along an outlet axis 35.
  • the inlet axis 34 and the outlet axis 35 are arranged on opposite sides of the centre axis 36 in a symmetric way.
  • the inlet port 2 and the outlet port 3 comprise an outer flange to which the heat exchanger is connected to the system in which the heat exchanger is used.
  • Each port further comprises a short pipe that is welded to the end plate and that extends through the end plate so that it can, in this case, abut the compensation plates.
  • the pipe is fixedly attached to the compensation plate closest to the port, e.g. by welding, thereby creating a joint between the port pipe and the compensation plates. An example of this can be seen in Fig. 6 .
  • the heat exchanger comprises a number of corrugated heat exchanger plates 10, 11 having a corrugated pattern comprising ridges 12 and grooves 13.
  • the ridges and grooves enlarge the heat transfer surface of the heat exchanger and create a suitable pressure drop through the flow channel.
  • the pattern may have different shapes, depending on the use of the heat exchanger.
  • the heat exchanger plates are stacked on each other in such a way that a flow channel is created between the plates, referred to as the plate side flow channel or the first flow channel. Between two adjacent plates 10, 11, the first flow channel 14 is created. In this case, the two plates are welded at the outer periphery 9 of the heat exchanger plates, making up a heat exchanger cassette. An enclosed volume is thus created, which is part of the plate side flow channel.
  • the cassettes are welded to each other at the port openings 16 of the heat exchanger plates.
  • a second flow channel 15 also referred to as the shell side flow channel, is created on the shell side between the cassettes.
  • the number and size of the cassettes comprised in the heat exchanger is selected depending on the required heating/cooling capacity of the heat exchanger.
  • the welded heat exchanger plates make up the heat exchanger core. Such a heat exchanger core is well known in the art and is not described further.
  • the flow channels in the heat exchanger may be configured in different ways, known to the skilled person.
  • the inlet port pipe and the outlet port pipe is welded directly to the heat exchanger plate pack, i.e. to the heat exchanger plate closest to the inlet and outlet ports in order to obtain a pressure tight plate side flow channel.
  • the inlet port pipe and the outlet port pipe are also welded to the end plate of the heat exchanger in order to obtain a pressure tight flow channel on the shell side of the heat exchanger.
  • the ports opening of the heat exchanger plate will be fixedly attached to the end plate. Since the heat exchanger plate will react to thermal changes much faster than the end plate, there will be stress imposed on the joint between the inlet and outlet pipe and the heat exchanger plate. If the connection is exposed to thermal cycling, the connection will, depending e.g. on the distance between the inlet and outlet pipe, deteriorate and may eventually break.
  • the inventive heat exchanger is thus provided with a number of compensation plates 20 disposed between the first end plate 6 and the heat exchanger plate stack 17.
  • the purpose of the compensation plates is to allow the heat exchanger plates to expand or shrink due to a fast temperature change without imposing thermal fatigue to the joints between the heat exchanger plate pack and the end plate.
  • Fig. 4 shows a side view of a compensation plate 20
  • Fig. 5 shows a cross-section of a compensation plate
  • Fig. 6 shows a cross-section of the inlet region of a heat exchanger.
  • the compensation plate 20 is provided with a concentric corrugated pattern comprising ridges 18 and grooves 19. The pattern is pressed such that the height distance between the ridges and the grooves corresponds to the pressing depth of the plate.
  • the compensation plate has a reference level denoted a, with the pressing depth corresponding to the height h.
  • the grooves are at the reference level a.
  • the outer periphery 22 of the compensation plate is also at the reference level a.
  • the circumference 31 of each port opening 23 in the compensation plate will have the same height as the ridges, i.e. the height h.
  • every other compensation plate is turned so that the outer periphery of two adjacent compensation plates bear on each other, and so that the circumference of the port openings of two other adjacent compensation plates bear on each other.
  • the ridges of two adjacent compensation plates bear on each other, and the grooves of two other adjacent compensation plates bear on each other.
  • the compensation plates in a compensation plate stack 21 are fixedly attached to each other, e.g. by welding or brazing, only at the outer periphery 22 and at the circumference 31 of the port openings 23.
  • the ridges or grooves of respective adjacent compensation plates will also bear on each other, but will not be fixedly attached to each other.
  • the flank angle ⁇ of the compensation plate may be smaller than the flank angle ⁇ of the heat exchanger plates.
  • the flank angle ⁇ of a heat exchanger plate is around 45 degrees in order to provide a large heat transfer surface and at the same time a relatively stiff plate.
  • Fig. 6 the inlet port region of a heat exchanger is shown.
  • seven compensation plates are used in the compensation plate stack 21.
  • the first compensation plate is fixedly attached, e.g. by welding or brazing, to the inlet pipe 24, which in turn is welded to the end plate 6.
  • the consecutive compensation plates are fixedly attached to each other at either the outer periphery 22 or the circumference 31 of the port openings 23.
  • the last compensation plate is fixedly attached to the heat exchanger plate stack 17 at the outer periphery 22 of the compensation plate 20 and the outer periphery 9 of a heat exchanger plate.
  • the compensation plate stack 21 functions in the following way. When a quick and high temperature rise occurs in the heat exchanger, the heat exchanger plates in the heat exchanger plate stack 17 will immediately expand. The end plate 6 will expand much slower, partly because the end plate is much thicker than the heat exchanger plates and partly because the end plate is in very little contact with the media flowing through the heat exchanger. The compensation plates will expand somewhat slower than the heat exchanger plates, since most of the compensation plates are not in great contact with the flow through the heat exchanger.
  • the compensation plate stack can not expand in the same way, since a compensation plate is fixed to the end plate.
  • the compensation plates can, due to the concentric pattern, expand in a different way than the heat exchanger plates and will expand in a somewhat elliptical shape. Since the compensation plate stack is attached to the heat exchanger plate stack on one side and to the end plate on the other side, each compensation plate will expand somewhat differently. Each plate will thus help to minimize the stress imposed on the joint 25 between the inlet pipe 24 and the port opening circumference 31 of the compensation plate closest to the end plate. Since the compensation plates have a relatively low radial stiffness, the stress imposed on the plates due to the thermal expansion is divided over the complete plate stack, and the stress imposed on each plate is divided over each plate.
  • the complete core of the heat exchanger comprising the heat exchanger plate stack 17 and one or two compensation plate stacks 21, is held in position by the end plates. Since all plates are welded together, the core is stiff and can only expand in the radial direction, towards the shell. Other forms of deformation are not possible when the core is mounted in the heat exchanger housing. If the core was not mounted in a heat exchanger, the distance between the inlet axis 34 and the outlet axis 35 would increase with higher temperature. Because that the core is fixedly attached to the end plates, the distance between the inlet axis 34 and the outlet axis 35 can not change when the temperature changes. Instead, stress will be imposed on the joint between the core and the end plates.
  • the stress imposed on the joints between the core and the end plates will be the same for the two shown embodiments. Since the heat exchanger core is pressed between the end plates, the stress will be the same regardless of on which side of the inlet or outlet flow duct the inlet or outlet port is located.
  • the compensation plate 20 is provided with an opening 28 in the centre of the compensation plate.
  • the opening may be cut out during the pressing of the compensation plate or in a later process step.
  • every other compensation plate must be welded to an adjacent compensation plate also at the inner periphery 27 in order to obtain a closed channel for the plate side flow channel.
  • the advantage of having an opening in the centre of the compensation plate is that the radial stiffness of the compensation plate is decreased further.
  • the central opening 28 In order to support the heat exchanger plates, the central opening 28 must be provided with some kind of support means for the support of the centre of the heat exchanger plates.
  • a pressure plate 29 is provided in the centre of each compensation plate. It is advantageous to use the cut-out for the central opening as a pressure plate 29.
  • the pressure plate is preferably attached to the compensation plate.
  • One way of attaching the pressure plate to the compensation plate is by welding.
  • the outer and inner peripheries of the compensation plate are seal welded in order to obtain a pressure tight weld.
  • the pressure plate is preferably tack welded to the compensation plate in a few positions, in order to obtain a flexible attachment of the pressure plate.
  • the pressure plate should not be rigidly attached to the compensation plate.
  • the number of compensation plates used in a compensation plate stack may vary depending e.g. on the diameter of the heat exchanger, the temperatures that the heat exchanger is designed for and the thickness and pressing depth of the compensation plates.
  • a suitable number of compensation plates for a heat exchanger having a diameter of 1 meter is between 3 and 9. In the shown example, 7 compensation plates are used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP08171770A 2008-12-16 2008-12-16 Wärmetauscher Not-in-force EP2199723B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
AT08171770T ATE553349T1 (de) 2008-12-16 2008-12-16 Wärmetauscher
EP08171770A EP2199723B1 (de) 2008-12-16 2008-12-16 Wärmetauscher
JP2011541286A JP5405589B2 (ja) 2008-12-16 2009-12-01 熱交換器
PCT/EP2009/066144 WO2010069756A1 (en) 2008-12-16 2009-12-01 Heat exchanger
KR1020117013880A KR101286360B1 (ko) 2008-12-16 2009-12-01 열교환기
CN2009801516518A CN102265109A (zh) 2008-12-16 2009-12-01 热交换器
US13/133,423 US20110259562A1 (en) 2008-12-16 2009-12-01 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08171770A EP2199723B1 (de) 2008-12-16 2008-12-16 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP2199723A1 true EP2199723A1 (de) 2010-06-23
EP2199723B1 EP2199723B1 (de) 2012-04-11

Family

ID=40601690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08171770A Not-in-force EP2199723B1 (de) 2008-12-16 2008-12-16 Wärmetauscher

Country Status (7)

Country Link
US (1) US20110259562A1 (de)
EP (1) EP2199723B1 (de)
JP (1) JP5405589B2 (de)
KR (1) KR101286360B1 (de)
CN (1) CN102265109A (de)
AT (1) ATE553349T1 (de)
WO (1) WO2010069756A1 (de)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5690532B2 (ja) * 2010-09-10 2015-03-25 株式会社前川製作所 シェルアンドプレート式熱交換器
CN102410761A (zh) * 2011-12-09 2012-04-11 沈阳汇博热能设备有限公司 一种自支撑全焊接板式换热器
CN104296565A (zh) * 2013-07-15 2015-01-21 四平维克斯换热设备有限公司 内置板式容积热交换器
DK2988085T3 (da) 2014-08-22 2019-06-24 Alfa Laval Corp Ab Varmeoverføringsplade og pladevarmeveksler
DK3112788T3 (da) * 2015-07-01 2019-05-20 Alfa Laval Corp Ab Pladevarmeveksler
CN105444594B (zh) * 2015-12-04 2018-08-28 上海宝丰机械制造有限公司 板片式换热器
DK179767B1 (da) * 2017-11-22 2019-05-14 Danfoss A/S Varmeoverføringsplade til plade-og-skal-varmeveksler og plade-og-skal-varmeveksler med samme
FI130245B (en) * 2019-12-12 2023-05-05 Vahterus Oy Plate heat exchanger and its use as vaporizer of liquefied natural gas

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DATABASE WPI Section Ch Week 26, Derwent World Patents Index; Class J08, AN 1983-63334K, XP002527541 *

Also Published As

Publication number Publication date
JP5405589B2 (ja) 2014-02-05
ATE553349T1 (de) 2012-04-15
US20110259562A1 (en) 2011-10-27
CN102265109A (zh) 2011-11-30
KR101286360B1 (ko) 2013-07-15
KR20110083751A (ko) 2011-07-20
WO2010069756A1 (en) 2010-06-24
EP2199723B1 (de) 2012-04-11
JP2012512377A (ja) 2012-05-31

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