EP4001818A1 - Platten-kapsel-wärmetauscher und wärmeübertragungsplatte für platten-kapsel-wärmetauscher - Google Patents

Platten-kapsel-wärmetauscher und wärmeübertragungsplatte für platten-kapsel-wärmetauscher Download PDF

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Publication number
EP4001818A1
EP4001818A1 EP21208296.0A EP21208296A EP4001818A1 EP 4001818 A1 EP4001818 A1 EP 4001818A1 EP 21208296 A EP21208296 A EP 21208296A EP 4001818 A1 EP4001818 A1 EP 4001818A1
Authority
EP
European Patent Office
Prior art keywords
plate
shell
heat exchanger
furrow
distribution area
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.)
Pending
Application number
EP21208296.0A
Other languages
English (en)
French (fr)
Inventor
Helge Nielsen
Ivan Knudsen
Jes Petersen
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.)
Danfoss AS
Original Assignee
Danfoss 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 Danfoss AS filed Critical Danfoss AS
Publication of EP4001818A1 publication Critical patent/EP4001818A1/de
Pending 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
    • F28D9/0031—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
    • 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
    • F28D9/0006—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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box

Definitions

  • the present invention relates to a plate-and-shell heat exchanger and a heat transfer plate for a plate-and-shell heat exchanger.
  • Plate-and-shell heat exchangers comprise a plurality of stacked structured plates positioned within a shell or casing.
  • the plates are connected in pairs such that a first fluid flow path for a first fluid is provided at least partially within the connected pairs of plates.
  • the pairs of connected plates are designed to fluidly connect a first inlet opening to a first outlet opening of the heat exchanger, thereby forming the first fluid flow path.
  • a second fluid flow path for a second fluid is provided outside of the connected pairs of plates and separated from the first fluid flow path by the plates.
  • the second fluid flow path fluidly connects a second inlet opening to a second outlet opening.
  • the second fluid enters the shell of the heat exchanger through the second inlet opening, flows along the complex second fluid flow path inside the shell and out through the second outlet opening.
  • the second fluid enters the shell of the heat exchanger it undergoes a complex change from a tubular or cylindrical flow through e.g. a pipe into a branched flow past the various components of the inside of the heat exchanger.
  • the first and second fluid flows may be obstructed in some regions and/or guided in a non-uniform way, such that the heat transfer rate between the two fluids inside the heat exchanger is reduced.
  • the pressures such as in the area of the openings and in the centre flow sections of the plates may be significant, and thus it is a goal to make a better pressure distribution over the plates.
  • the problem of the present invention's is how to enhance the heat exchanger efficiency.
  • the central transferring regions may be formed with a corrugated pattern and the first distribution area may be formed with a first distribution corrugated pattern.
  • neither the first distribution corrugations or the central heat transferring region corrugations cross the furrow to extend between the central heat transferring region and the first distribution area.
  • the furrow may be formed with a reinforcement pattern.
  • the reinforcement pattern may be formed as reinforcement corrugations with a series of parallel ridges and grooves extending in the direction a line P being perpendicular to the length direction L of the furrow.
  • the reinforcement corrugations may reach across the furrow connecting the respective first distribution area to the central heat transferring region.
  • the reinforcement corrugations may be narrower than the corrugations in the respective first distribution area and the central heat transferring region.
  • the furrow may be formed with a section where at least one reinforcement corrugation merges one or both ends of a top or bottom into a top or bottom of a corrugation in the respective first distribution area and the central heat transferring region.
  • the furrow may be formed with a section where at least one reinforcement corrugation merges one or both ends of a top or bottom connection to a bottom or top of a corrugation in the respective first distribution area and the central heat transferring region.
  • the furrow may be formed with a section where at least one reinforcement corrugation merges one or both ends of a top or bottom of into the side wall connecting a top and bottom of a corrugation in the respective first distribution area and the central heat transferring region.
  • the second opening may be formed in a second distribution area and where a furrow as in any of the previous claims is formed in connection to the second opening and second distribution area the same manner as the furrow in relation to the first opening of the previous claims.
  • the corrugations may be lower than the corrugations in the respective first and/or second distribution areas and the central heat transferring region.
  • the distribution furrow could extend across the whole of the plate from rim to rim.
  • the furrow may be formed of a first part and a second part, each extending from the rim of the of opening to the rim of the plate.
  • the opening in the area between the first furrow part and second furrow part may be in direct fluidic contact with the central heat transferring region.
  • FIG. 1a shows an exploded view of a plate-and-shell heat exchanger 100.
  • the heat exchanger 100 comprises a shell 20 and a plurality of sealed pairs of heat transfer plates 10 within the shell 20.
  • the shell 20 may be of a hollow cylindrical shape and the plates 10 may be of a corresponding shape and size such that they can be fit into the shell 20.
  • Other shapes of the shell 20 and plates 10 are also possible, however shapes are preferred, which allow for a substantially close positioning of the plates 10 within the shell 20.
  • the plates 10 in the pairs are in the heat transfer sections 32 contacting each other by intersecting patterns 30.
  • the first fluid flow enters and leaves the heat exchanger through first inlet and outlet openings 23, 23'.
  • the first cavities 11 are surrounded by two adjacent plates 10, which are connected to each other, as is shown more clearly in figure 1b and as will be described below in more detail.
  • Figure 1b shows the heat exchanger 100 in a sectional view and in an assembled state.
  • the plates 10 in the pairs may be connected e.g. by welding or brazing at their rims 14A, possible also at the connected intersecting patterns 30. Two and two this forms first cavities 11 for a sealed first fluid flow path 12 from a first inlet opening 23 to a first outlet opening 23'.
  • the plates 10 comprise plate openings 13, 13' for connecting fluidly adjacent plates 10 to each other and to the first inlet and outlet opening 23, 23'.
  • the two adjacent plates 10 of two connected pairs may be connected and sealed together by e.g. a welding or brazing along the edge of the plate openings 13, 13'.
  • a second fluid flow path 22 is formed at the outside surfaces of the plates 10 by the connected patterns 30 projecting outwardly relative to the first cavities 11 of the connected pairs of plates 10, thus at the opposite side of the plates 10.
  • the second fluid flow path 22 thus is formed outside of the sealed pairs of plates 10 and inside of the shell 20 and is connected to second inlet and outlet openings 24, 24'.
  • a second fluid flow enters and leaves the heat exchanger 100 through second inlet and outlet openings 24, 24'.
  • the shell 20 forms a second cavity 21 in which the plates 10 are arranged and in which a second fluid flow path 22 for a second fluid flow is provided.
  • the second fluid flow enters and leaves the heat exchanger 100 through second inlet and outlet openings 24, 24'.
  • the first flow path 12 and second fluid flow path 22 are separated and sealed from each other respectively by the plate pairs connected at the rims 14a and the pairs being connected by being connected at their rim 14b of the openings 13, 13'.
  • the heat exchange occurs between the two fluids flowing separated from each other by the plates 10.
  • Fluid for the first flow path 12 is sealed from the inside of the second cavity 21 inside the shell 20, and therefore the second flow paths 22, but each cavity 11 is fluidically contacted with the other cavities 11 of the connected plate 10 pairs in the stack by the openings 13. 13', and thereby also first inlets and outlets 23, 23'.
  • Fluid for the second flow path 22 is in fluid contact to the second cavity 21, and thereby the second inlets and outlets 24, 24', over the rims 14A of the plates 10, but is sealed from the cavities 11 as the two plates 10 in each pair is connected at their rims 14A and pairs are connected to neighbouring pairs at the (outer) rims 14B of the openings 13, 13'.
  • FIG 2a shows a detailed view of a heat transfer plate 10 of a prior art plate-and-shell heat exchanger 100.
  • the plate 10 sheet is possibly made of metal.
  • the pattern 30 at the heat transfer sections 32 is seen as being corrugated having a series of parallel ridges and grooves. It may be formed by pressing the corrugations into a flat sheet preform. The plates 10 then are connected such that every second plate is turned, or formed, with the corrugated patterns 30 of neighbouring plates crossing each other rather than extending in parallel. The crossing points then forms the contacts of the plates 10 in the heat transfer sections.
  • Figure 2b shows a detailed sectional view of a plurality of connected heat transfer plates 10.
  • Two adjacent plates 10 at their outer circumferences, in at the rims 14A of their outer edges.
  • sealed pairs of connected plates 10 are provided for allowing the first fluid to flow through the first fluid flow path 12 bounded by the connected pairs of plates 10.
  • the second fluid flow path 22 is guided between two adjacent pairs of connected plates 10 and separated from the first fluid flow path 12 by the plates 10. It comprises flat, narrow channels between closely positioned plates 10.
  • the second fluid flow rate in the vertical direction and between the pairs of connected plates 10 as shown in figure 2b is essential. This flow component corresponds in approximation to a radial or tangential component of the second fluid flow with respect to the shell 20.
  • Figure 3 is a schematic view of parts of the first and second fluid flow paths 12, 22 through the heat exchanger 100 along the heat transfer sections 32.
  • the arrows at the one plate 10 indicates the first fluid flow path 12 inside a pair of connected plates 10.
  • the fluid flow path 12 enters the pair of connected plates 10 through one of the two plate openings 13 and leaves the pair of connected plates 10 through the other of the two plate openings 13.
  • the second plate shows a part of the second fluid flow path 22 in a cross section of the heat exchanger 100. This time, not the inside of a pair of connected plates 10 is shown, but the space between two such connected pairs of plates 10.
  • the second fluid flow path 22 fills the second cavity 21.
  • the second cavity 21 is bounded by the inside of the shell 20, the outsides of the pairs of connected plates 10, one of which is shown in figure 3b and possibly further structures contained within the shell 20.
  • the second flow path 22 enters the shell 20 through the second inlet and outlet openings 24, 24', which may be positioned on opposite sides of the shell surface.
  • the fluids preferably should distribute sufficiently over the entire plates 10.
  • Figs. 4A and 4B illustrate an embodiment pair of plates 10A, 10B according to the present invention to be connected in a pair.
  • Each plate comprises a pair of openings 13, 13' arranged opposite each other relative to a central heat transferring regions 32 formed corrugated patterns 30 and possible positioned near the rim 14A.
  • the corrugated pattern 30 in the central transferring regions 32 may be chevron shaped, W-shaped, straight parallel corrugations etc.
  • the first opening 13 is arranged in a first distribution area 33, 34 having a first distribution corrugated pattern 30.
  • the second opening 13' may be arranged in a second distribution area (33', 34') having a second distribution corrugated pattern 30.
  • a distribution furrow 40 may be formed in the connection of the first distribution area 33, 34 to the central heat transferring region 32, and may extend parallel to a line P being perpendicular to the line L reaching from the first opening 13 to the second opening 13', possible through the opening 13, 13' centres.
  • the first distribution pattern 30 in the first distribution area 33, 34 may be formed with differently to the corrugated pattern 30 in the central transferring region.
  • the first plate 10A in a plate pair is formed a first part first distribution area 33 where the corrugations 30 extend from the rim portion 14A of the first part first distribution area 33 towards the central heat transferring region 32.
  • the first plate 10A further is formed with a second part first distribution area 34 where the corrugations 30 extend from the rim portion 14A of the first part first distribution area 34 towards the central heat transferring region 32.
  • the first part first distribution area 33 and second part first distribution area 34 are positioned at opposite sides of the opening 13 and may be mirroring each other over opening 13 corresponding to the line L.
  • first part first distribution area 33 and second part first distribution area 34 are formed with different corrugations 30, where different, or opposite, may indicate they are oriented differently, or opposite to each other.
  • first part first distribution area 33 corrugations 30 incline downwards seen in the direction from the left towards the right along the line P, this being a first direction of inclination
  • second part first distribution area 34 is inclining in a second direction being in an upwards inclination in the direction from the left towards the right along the line P
  • the first direction of inclination thus is opposite to the second direction of inclination.
  • the corrugations in the second part first distribution area 34 may have an angle relative to the line L in the range of 10 to 45 degrees, or in the range of 10 to 30 degrees.
  • the corrugations in the first part first distribution area 33 may have an angle relative to the line L in the range of 135 to 170 degrees, or in the range of 150 to170 degrees.
  • first plate 10A in a plate pair is formed a first part second distribution area 33' where the corrugations 30 may extend from the central heat transferring region 32 to the rim 14B of the opening 13'.
  • the corrugations 30 in first part first distribution area 33 may be inclined in the same orientation, or direction, as those in the second part first distribution area 33'. In the illustration they are inclined in the first direction of inclination.
  • they are parallel and in others they are inclined with slightly different angles of the first direction of inclination.
  • the first plate 10A further is formed with a second part second distribution area 34' where the corrugations 30 may extend from the central heat transferring region 32 to the rim 14B of the opening 13'.
  • the corrugations 30 in second part first distribution area 34 may be inclined relative to the line L with an inclination in the same orientation, or direction, as those in the second part second distribution area 34', such as illustrated with a second direction of inclination. In one embodiment they are parallel and in others they are inclined with slightly different angles.
  • the first part second distribution area 33' and second part second distribution area 34' are positioned at opposite sides of the opening 13' and may be mirroring each other over opening 13' corresponding to the line L.
  • first part second distribution area 33' and second part second distribution area 34' are formed with different corrugations 30, where different may indicate they are oriented different.
  • the corrugations 30 in the second part second distribution area 34' may have an angle relative to the line L in the range of 10 to 45 degrees, or in the range of 10 to 30 degrees.
  • the corrugations in the first part second distribution area 33' may have an angle relative to the line L in the range of 135 to 170 degrees, or in the range of 150 to170 degrees.
  • Fig. 4B shows the second plate 10B in the pair.
  • the second plate 10B may be like the plate 10A of fig. 4A , only turned 180 degrees, or it may be formed differently.
  • the first plate 10A in the pair is aligned with the second plate 10B such that:
  • This construction of the pair of plates 10A, 10B ensure their connection by intersecting corrugations 30 in the distribution areas 33, 34, 33', 34', and at the same time defines respectively the first flow path 12 and the second flow path 22 when a stack of pairs is formed.
  • the corrugations of one of the plates 10A, 10B are arranged such as to respectively assist fluid distributing from the inlet opening 13 to the full width of the plate 10A, 10B, and at the other end, assist fluid being directed into the outlet opening 13'. This also helps lowering the pressures in the first flow path 12.
  • the corrugations of one of the plates 10A, 10B are arranged such as to respectively assist fluid distributing to the full width of the plate 10A, 10B, and at the other end, assist fluid being directed out of the second flow paths 22. This also helps lowering the pressures in the second flow path 22.
  • the pressure distribution furrow 40 could extend across the whole of the plates 10A, 10B from a rim 14A to an opposite rim 14A, or as in the illustrated embodiment, it may be formed of a first part 41 and a second part 42, each extending from the rim 14B of opening 13, 13' to the rim 14A of the plate 10A, 10B, parallel to the line P.
  • the opening may be in direct fluidic contact with the central heat transferring region 32.
  • the pressure distribution furrow 40 assists in directing the fluid respectively directly from or to the opening 13, 13' to the full width of the plates 10A, 10B where this in addition reduces the pressures in the areas of the openings 13, 13'.
  • a sealing 44 is formed in the area between the from the central heat transferring region 32 and at least one of the openings 13, 13' thus forcing the fluids entering towards the sides of the plates 10A, 10B when entering the inlet of the respective openings 13, 13', and correspondingly being directed from the heat central transferring region 32 towards the outlet of the respective openings 13, 13'.
  • a sealing 44 is formed in connection to each opening 13, 13'.
  • the sealing(s) may be formed as projections in the plate 10A, 10B formed in the section between the opening 13, 13' and the central heat transferring region 32 and connected to a similar projection of the connected plate 10A, 10B forming the flow barrier.
  • the sealing 44 projection may be semi-circular covering the opening 13, 13' edge towards the central heat transferring region 32.
  • the sealing 44 is formed in the area 43 between the first furrow part 41 and second furrow part 42, possible connecting to them.
  • a sealing element is positioned in the position possible in some groove formed or fixed in position otherwise.
  • the furrow 40 is formed between the central heat transferring region 32 and respectively the first 33, 33' and second 34, 34' distribution areas.
  • the corrugations (30, 30a, 30b) therefore does not extend between the central heat transferring region 32 and respectively the first 33, 33' and second 34, 34' distribution areas.
  • corrugation tops 30a are illustrated as solid lines, whereas corrugation bottoms 30b are illustrated as dashed lines.
  • a reinforcement pattern 50 To increase strength of the furrow 40, it may be formed with a reinforcement pattern 50.
  • a reinforcement pattern 50 One such embodiment is seen in fig. 5 , where this pattern forms reinforcement corrugations with a series of parallel ridges and grooves extending in the direction of the line P along the length direction L of the furrow 40.
  • the reinforcement corrugations 50 reach across the furrow 40 connecting the respective first 33, 33' and second 34, 34' distribution area to the central heat transferring region 32.
  • the reinforcement corrugations 50 top or bottom merges into a top a corrugation 30 in the respective first 33, 33' and second 34, 34' distribution area. See fig. 6 .
  • the reinforcement corrugations 50 top or bottom ends in connection to a bottom of a corrugation 30 in the respective first 33, 33' and second 34, 34' distribution area.
  • the reinforcement corrugations 50 top or bottom of merges into the side wall connecting a top and bottom of a corrugation 30 in the respective first 33, 33' and second 34, 34' distribution area.
  • the reinforcement furrow 40 may be formed with all kinds of sections 51, 52 and 53, or with only one kind of either section 51, 52, 53, or with the sections 51 and 52, or sections 51 and 53, or sections 52 and 53.
  • the reinforcement corrugations 50 may extend continuous along the length of the furrow 40 or may be positioned in sections having flat section (top or bottom) between the sections.
  • the reinforcement corrugations 50 may be significantly narrower than the corrugations 30 in the respective first 33, 33' and second 34, 34' distribution areas and the central heat transferring region 32.
  • narrower is meant the distance from top to top (respective bottom to bottom) is significantly smaller. This automatically enables the different sections 51, 52 and/or 53 along the furrow 40.
  • the reinforcement corrugations 50 may be lower than the corrugations 30 in the respective first 33, 33' and second 34, 34' distribution areas and the central heat transferring region 32. Thereby they are not contacting the corresponding reinforcement corrugations 50 in the neighbouring plates 10, 10A, 10B, thus enabling the flow and pressure distribution over the furrows 40.
  • the furrows 40 is part of the border of the respective first 33, 33' and second 34, 34' distribution areas, these thus being bordered respectively by a furrow 40, opening 13, 13' and a rim 14A section.
  • the furrows 40 merge into the projection 44.

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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)
EP21208296.0A 2020-11-16 2021-11-15 Platten-kapsel-wärmetauscher und wärmeübertragungsplatte für platten-kapsel-wärmetauscher Pending EP4001818A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DKPA202070756 2020-11-16

Publications (1)

Publication Number Publication Date
EP4001818A1 true EP4001818A1 (de) 2022-05-25

Family

ID=78649169

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21208296.0A Pending EP4001818A1 (de) 2020-11-16 2021-11-15 Platten-kapsel-wärmetauscher und wärmeübertragungsplatte für platten-kapsel-wärmetauscher

Country Status (2)

Country Link
EP (1) EP4001818A1 (de)
CN (1) CN114508955A (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4635714A (en) * 1981-10-21 1987-01-13 Reheat Ab Packing groove in plate member of plate heat exchanger
US20160025007A1 (en) * 2014-07-25 2016-01-28 Airbus Helicopters Plate heat exchanger of improved thermal efficiency for a turboshaft engine
US10234212B2 (en) * 2014-08-22 2019-03-19 Alfa Laval Corporate Ab Heat transfer plate and plate heat exchanger
FR3079605A1 (fr) * 2018-03-30 2019-10-04 Airbus Helicopters Echangeur thermique a plaques muni d'un bouclier de repartition de debit d'un fluide pour turbomoteur

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE505225C2 (sv) * 1993-02-19 1997-07-21 Alfa Laval Thermal Ab Plattvärmeväxlare och platta härför
FR2866699B1 (fr) * 2004-02-23 2008-06-27 Barriquand Echangeurs Echangeur thermique a plaques nervurees soudees
KR101891444B1 (ko) * 2017-09-29 2018-08-23 주식회사프로스트 니켈 도금에 의해 내식성이 강한 번들타입의 판형 열교환모듈 및 이의 제조방법

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4635714A (en) * 1981-10-21 1987-01-13 Reheat Ab Packing groove in plate member of plate heat exchanger
US20160025007A1 (en) * 2014-07-25 2016-01-28 Airbus Helicopters Plate heat exchanger of improved thermal efficiency for a turboshaft engine
US10234212B2 (en) * 2014-08-22 2019-03-19 Alfa Laval Corporate Ab Heat transfer plate and plate heat exchanger
FR3079605A1 (fr) * 2018-03-30 2019-10-04 Airbus Helicopters Echangeur thermique a plaques muni d'un bouclier de repartition de debit d'un fluide pour turbomoteur

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