EP1559981B1 - Wärmeübertrager aus runden profilierten Wärmeübertragunsplatten - Google Patents

Wärmeübertrager aus runden profilierten Wärmeübertragunsplatten Download PDF

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Publication number
EP1559981B1
EP1559981B1 EP05001668.2A EP05001668A EP1559981B1 EP 1559981 B1 EP1559981 B1 EP 1559981B1 EP 05001668 A EP05001668 A EP 05001668A EP 1559981 B1 EP1559981 B1 EP 1559981B1
Authority
EP
European Patent Office
Prior art keywords
plates
plate
heat transfer
heat exchanger
pack
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.)
Expired - Lifetime
Application number
EP05001668.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1559981A2 (de
EP1559981A3 (de
Inventor
Martin Kolbe
Joachim Schult
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.)
Tranter GmbH
Original Assignee
Tranter GmbH
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 Tranter GmbH filed Critical Tranter GmbH
Priority to PL05001668T priority Critical patent/PL1559981T3/pl
Publication of EP1559981A2 publication Critical patent/EP1559981A2/de
Publication of EP1559981A3 publication Critical patent/EP1559981A3/de
Application granted granted Critical
Publication of EP1559981B1 publication Critical patent/EP1559981B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F28D9/0018—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 without any annular circulation of the heat exchange media
    • 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
    • F28D9/0006—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 plate-like or laminated conduits being enclosed within a pressure vessel
    • 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
    • F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies

Definitions

  • the invention relates to a heat exchanger made of round profiled heat transfer plates with passages for heat transfer between media of the same or different physical state, consisting of a plate package, which is formed from at least two joined heat transfer plate pairs consisting of two gas-tight welded to the flow heat transfer plates and two Closing plates with passages for flowing through the plate package medium, which limit the joined heat transfer plate pairs on both sides, wherein the adjacent heat transfer plate pairs and the limiting closure plates are gas-tight welded to the outer periphery to form a separate pressure chamber and a pressure-stable housing with shell side arranged passage openings for a second medium , which flows through the plate package shell side t, and end-side passage openings with connecting pieces, which are welded to the passage openings of the closure plates.
  • a heat exchanger of the type mentioned in which at the periphery of the plate package fürfluß Adjusten for the shell side inflowing heat transfer medium are provided, which have an inner tube structure of the housing and are partially in communication with the plate package, wherein at least two of the flow guides are disposed opposite to an inner tube structure to the plate pack, which are supported against the inner wall of the surrounding housing.
  • the portions of the flow guides having an inner tube structure and forming the inflow and outflow regions are connected to tubes which engage the inlet and outlet ports of the surrounding housing, at least one of the tubes being leak-proof against the inner wall of the inlet and / or Outlet neck is sealed metallic.
  • a bypass-side inflow region formed in this way can prevent a bypass between the inner wall of the housing and the plate pack, for use in the high-pressure region it is necessary for the regions of the flow guides which communicate with the periphery of the plate pack to be counteracted by additional measures the housing inner wall are supported in order to achieve a corresponding pressure stability of the heat exchanger.
  • the WO 02/16852 suggest that these areas are additionally filled with a non-flowing heat transfer medium.
  • a plate heat exchanger in which the joined profiled heat transfer plates are permanently connected to the through holes by soldering to a plate package.
  • the plates are provided with at least one opening, which form a fastener channel in the soldered plate package through which a clamping screw for fixing the plate heat exchanger extends to a support member or a mounting plate, wherein the clamping screw is used simultaneously for clamping the soldered plate package intercept occurring pressure differences.
  • a trained plate heat exchanger is also completely unsuitable for the high pressure range and in a Temperaturbreich of -200 ° to + 900 °. But a shell-side influx of a medium is not possible by fully soldered execution.
  • the object of the present invention is therefore to improve the heat exchangers mentioned at the outset, that the heat exchanger as a metallically sealed and wear-free compact heat exchanger for the high pressure range and for a temperature range of - 200 ° C to + 900 ° C cost for the intended use of prefabricated standard modules can be produced and fluidically designed so that the konzepiere heat transfer surface shell side influx of the plate package is used maximally for the heat transfer.
  • the inventive feature combination creates the prerequisite that the heat exchanger can be inexpensively executed from prefabricated standard assemblies as metallically sealed and wear-free compact heat exchanger both in a fully welded embodiment and with a metallically sealed housing, for a wide industrial application, such as for the cold and air conditioning technology, power plant technology, building services, chem. Process technology, etc., at an operating temperature of - 200 ° C to + 900 ° C can be used without interference.
  • the condition is given that the shell-side inflow in the production of a heat exchanger very can be inexpensively adapted to the optimum flow conditions of the jacket medium, which ensure a uniform mantel wornes flow of the plate package and thus maximum utilization of the designed heat transfer surface for the predetermined application.
  • the assembly of the heat exchanger is very simplified and thus carried out very inexpensively , Rather, with the metallic sealing support of the U-shaped bends of the side plates against the inner diameter of the housing shell the shell-side bypass is prevented at the same time and the plate package itself is stably positioned in the housing shell.
  • the metallic sealing of the shell-side opening angle is carried out with a gauze-like metal fabric, which is inserted in strips between the clamping bolts and under the side panels in the gaps between adjacent heat transfer plate pairs.
  • the shell-side bypass can be effectively counteracted at the periphery of the plate pack and the sealing can be carried out with a thermally and chemically highly resistant sealing material, which is clearly fixed in position by the side plates.
  • the package clamping plates in the area between the clamping bolts, which are covered by the side plates, approximately offset to the diameter of the plate package.
  • each of the side plates consists of two partial side plates, wherein one of the partial side plates has a straight end, which is partially covered by the other part of the side sheet partially flat, which is provided with a Z-shaped end, which is against the inner diameter supported by the housing shell.
  • the width is variable, whereby a problem-free adjustment of the side plates can be made to the surface to be covered during assembly. Consequently, the shell-side opening angle of the inflow region can be adjusted exclusively by the changed positioning of the limiting clamping bolts on the package clamping plates during manufacture exactly to the intended use of the heat exchanger so that a maximum flow through the jacket medium takes place and the designed heat transfer surface of the plate package optimal for heat transfer is being used.
  • the service-free design of the heat exchanger makes it possible that advantageously the housing shell is welded to the end plates. In this way, a fully welded gas-tight compact heat exchanger can be provided in which leaks and leaks can be completely ruled out.
  • the heat exchanger consists essentially of a plate pack 1 with closure plates 19, 19a, the package clamping plates 3, 3a, the clamping bolt 4 - 4x, the side plates 6, 6a or the Generalizingblechen 6b, 6c and 6d, 6e, the combs 5 - 5c, the metallic seals 11 and the housing shell 12 with the two end plates 13, 13a and at least two fixed to the housing shell 12 mantle 14, 14a and at least two fixed to the end plates 13, 13a plate-side connecting piece 23, 23a.
  • the housing 21 is in the embodiment shown a vollversch spater pressure vessel consisting of the housing shell 12 and the two end plates 13; 13a with passage openings 25; 25a is formed, which are gas-tight welded to the housing shell 12 at the periphery.
  • a vollversch spater pressure vessel consisting of the housing shell 12 and the two end plates 13; 13a with passage openings 25; 25a is formed, which are gas-tight welded to the housing shell 12 at the periphery.
  • the passage opening 25 of the end plate 13 of the plate-side connecting piece 23 and at the passage opening 25 a of the end plate 13 a of the plate-side connecting piece 23 a is provided, each of the end plates 13; 13a and the package clamping plate 3, 3a penetrate and circumferentially with the end plate 13; 13a are connected.
  • shell-side passage openings 15; 15a provided, to which the jacket pipe 14; 14a are welded gas-tight for the jacket medium.
  • the plate pack 1 consists of a number of joined round profiled heat transfer plates 2 - 2x, which were determined thermally for the intended use and from the closure plates 19, 19a, which close the plate pack 1 at the ends.
  • the heat transfer plates 2 - 2x are at the periphery of the passages to heat transfer plate pairs 16; 16a gas-tight welded and the respective adjacent heat transfer plate pairs 16; 16 are together with the closing closure plates 19; 19a at the outer periphery welded together gas-tight.
  • the closure plates 19; 19a are formed with passage openings, which together with the passage openings of the heat transfer plates 2 - 2x the passageways 24; Form 24a through the plate pack 1.
  • the ends of the plate-side connecting pieces 23, 23a welded gas-tight, the package clamping plate 3; 3a and the end plate 13; 13 a of the housing 21 penetrate.
  • the plate pack 1 is on both sides by the package clamping plates 3; 3a with the passage openings 20; 20a limited, which are clamped by means of clamping bolts 4 - 4x.
  • the clamping bolts 4 - 4 extend adjacent to the periphery of the plate pack 1 and are on both sides with package clamping plates 3; 3a under predetermined bias of the plate package with the package clamping plates 3; 3a welded.
  • the shell-side opening angle ⁇ ; ⁇ 1 before the welding of the clamping bolt 4, 4b and 4a, 4c in a heat exchanger economically and individually adaptable to the designed power and the fluidic conditions of the jacket medium used. Consequently, the condition is thus created that the correspondingly available lateral surface of the plate pack 1 evenly is acted upon by the jacket medium, so that each heat exchanger for its application can be designed so that the designed heat transfer surface of the plate pack 1 is used optimally thermally.
  • the running at the periphery of the plate pack 1 clamping bolt 4d, 4e are 90 ° to the center of the opening angle ⁇ ; ⁇ 1 offset and the clamping bolts 4f - 4x are in the range of the opening angle ⁇ , ⁇ 1 and are with the package clamping plates 3; 3a welded to further stabilize the plate pack 1.
  • the clamping bolts 4f; 4x are rectangular in this particular case and at the same time serve to set the straight end 18 of the partial side panel 6c; 6f on the periphery of the disk pack 1.
  • the metallic seals 8 are compared with the opening angles ⁇ ; ⁇ 1 of the shell-side Anström Schemes by comb plates 5, 5a and 5b, 5c position stabilized positioned, which engage in the gaps 22 of the adjacent heat transfer plate pairs 16, 16a and extend over the length of the plate pack 1.
  • These comb plates 5; 5a; 5b; 5c are on the opposite side Side of the opening angle ⁇ ; ⁇ 1 parallel to the clamping bolt 4; 4a; 4b; 4c and 4c are on the clamping bolt; 4a; 4b; 4c welded.
  • the combs of the comb plates 5; 5a; 5b; 5 c formed with a contour corresponding to the shape of the columns 22.
  • the comb plates 5 - 5c are designed in a width which is supported on the inner wall of the housing 21 after installation of the heat exchanger.
  • the pressure-stable position of the plate package 1 in the housing 21 can be additionally improved.
  • the at the clamping bolt 4; 4a; 4b; 4c adjacent ends of the side panels 6; 6a and the partial side plates 6b; 6c; 6d; 6e are formed with congruent U-shaped angled portions 7, 7a and 7b, 7c, which are supported sealingly after assembly on the inner wall of the housing shell 12.
  • the partial side plates 6c and 6e are each formed with a straight-running end 18 of the clamping bolt 4f; 4x and partly from a partial side panel 6d; 6b, which is provided with a Z-shaped end 17, covered.
  • the Z-shaped end 17 of the partial side panels 6d; 6b is spaced apart from the plate pack 1 so that it is sealingly supported after assembly on the inner wall of the housing shell 12 and thus forms a further support point of the plate pack 1 against the inner wall of the housing shell 12, which further improves the positional stability and pressure stability of the plate pack 1 ,
  • the partial side plates 6d, 6e and 6b, 6c namely that of one of the two cooperating partial side plates 6d; 6e and 6b, respectively; 6c has a straight end 18, that of the other part of the side panel 6d; 6c and 6b, respectively; 6c, the partial side plates 6d, 6e or 6b, 6c are individually adaptable to the region to be covered, which is determined by the selected opening angle ⁇ , ⁇ 1 of the shell-side inflow region.
  • the described embodiment of the heat exchanger is designed Centerpposit.
  • a metallic plate pass 9 and coat side a metallic jacket separation 10 is used in the passage 24 a of the plate pack 1.
  • the metallic jacket partition 10 is slotted on the side facing the plate pack 1 side and placed on the junction of two heat transfer plate pairs 16, 16a and by the inserted metallic seals 6 in the columns 22 of the adjacent heat transfer plate pairs 16, 16 a sealed at the circumference of the plate pack 1 and fixed jacket side sealed against the inner wall of the housing shell 12 with a metallic seal 11.
  • the inventively proposed and completely metallic sealed heat exchanger is almost service-free and thus suitable for the compact design in a fully welded design in the high pressure and high temperature range. But it can also be designed by the specific embodiment very economically from prefabricated standard modules to each purpose individually for optimum use of the designed heat transfer surface.

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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)
EP05001668.2A 2004-01-30 2005-01-27 Wärmeübertrager aus runden profilierten Wärmeübertragunsplatten Expired - Lifetime EP1559981B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL05001668T PL1559981T3 (pl) 2004-01-30 2005-01-27 Wymiennik ciepła z okrągłych profilowanych płytek przewodzących ciepło

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004004895 2004-01-30
DE102004004895A DE102004004895B3 (de) 2004-01-30 2004-01-30 Wärmeübertrager aus runden profilierten Wärmeübertragungsplatten

Publications (3)

Publication Number Publication Date
EP1559981A2 EP1559981A2 (de) 2005-08-03
EP1559981A3 EP1559981A3 (de) 2012-05-30
EP1559981B1 true EP1559981B1 (de) 2013-07-03

Family

ID=34585412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05001668.2A Expired - Lifetime EP1559981B1 (de) 2004-01-30 2005-01-27 Wärmeübertrager aus runden profilierten Wärmeübertragunsplatten

Country Status (6)

Country Link
EP (1) EP1559981B1 (da)
DE (1) DE102004004895B3 (da)
DK (1) DK1559981T3 (da)
ES (1) ES2429137T3 (da)
PL (1) PL1559981T3 (da)
PT (1) PT1559981E (da)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9080815B2 (en) 2008-06-18 2015-07-14 Gesmex Gmbh Conversion set for a tube bundle heat exchanger
US20110024082A1 (en) * 2009-05-09 2011-02-03 Tranter, Inc. Heat exchanger with accessible core
DE102009023929A1 (de) 2009-06-04 2010-12-09 Stürzebecher, Wolfgang, Dr. Absorptionskälteaggregat
EP2944912B1 (en) 2014-05-13 2016-12-14 Alfa Laval Corporate AB Plate heat exchanger
KR20160147475A (ko) * 2015-06-15 2016-12-23 현대자동차주식회사 캔형 열교환기
CN108645255A (zh) * 2018-07-11 2018-10-12 广东捷玛节能科技股份有限公司 一种可拆式气气板式热交换器
DK180416B1 (en) * 2019-11-04 2021-04-22 Danfoss As Plate-and-shell heat exchanger and a channel blocking plate for a plate-and-shell heat exchanger
CN114570692B (zh) * 2022-02-12 2023-06-16 江苏高创风电设备有限公司 一种液压元件清洗设备

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB203160A (en) * 1922-08-15 1923-09-06 Burmah Oil Co Ltd Improved apparatus for cooling oil or other liquids
US1669062A (en) * 1924-10-28 1928-05-08 Menzel Ag Heat-exchange apparatus
FR2719369B1 (fr) * 1994-04-29 1996-07-19 Framatome Sa Echangeur thermique à plaques.
SE502638C2 (sv) * 1994-05-18 1995-11-27 Tetra Laval Holdings & Finance Plattvärmeväxlare med permanent sammanfogade moduler
SE9504586D0 (sv) * 1995-12-21 1995-12-21 Tetra Laval Holdings & Finance Plattvärmeväxlare
FI114738B (fi) * 2000-08-23 2004-12-15 Vahterus Oy Levyrakenteinen lämmönvaihdin

Also Published As

Publication number Publication date
EP1559981A2 (de) 2005-08-03
DK1559981T3 (da) 2013-10-14
EP1559981A3 (de) 2012-05-30
DE102004004895B3 (de) 2005-06-16
PT1559981E (pt) 2013-10-09
ES2429137T3 (es) 2013-11-13
PL1559981T3 (pl) 2013-12-31

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