EP4097413B1 - Hartgelöteter plattenwärmetauscher und dessen verwendung - Google Patents

Hartgelöteter plattenwärmetauscher und dessen verwendung

Info

Publication number
EP4097413B1
EP4097413B1 EP21705649.8A EP21705649A EP4097413B1 EP 4097413 B1 EP4097413 B1 EP 4097413B1 EP 21705649 A EP21705649 A EP 21705649A EP 4097413 B1 EP4097413 B1 EP 4097413B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
pattern
grooves
ridges
plates
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.)
Active
Application number
EP21705649.8A
Other languages
English (en)
French (fr)
Other versions
EP4097413A1 (de
Inventor
Sven Andersson
Tomas Dahlberg
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.)
Swep International AB
Original Assignee
Swep International 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
Application filed by Swep International AB filed Critical Swep International AB
Priority to EP25193080.6A priority Critical patent/EP4617602A3/de
Priority to SI202130355T priority patent/SI4097413T1/sl
Publication of EP4097413A1 publication Critical patent/EP4097413A1/de
Application granted granted Critical
Publication of EP4097413B1 publication Critical patent/EP4097413B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28D9/005—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 the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing
    • 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

Definitions

  • the present invention relates to a brazed plate heat exchanger comprising a plurality of heat exchanger plates having a pattern of ridges and grooves providing contact points between at least some crossing ridges and grooves of neighbouring plates under formation of interplate flow channels for fluids to exchange heat.
  • the present invention is also related to the use of such a heat exchanger.
  • Heat exchangers are used for exchanging heat between fluid media. They generally comprise a start plate, an end plate and a number of heat exchanger plates stacked onto one another in a manner forming flow channels between the heat exchanger plates. Usually, port openings are provided to allow selective fluid flow in and out from the flow channels in a way well known to persons skilled in the art.
  • a common way of manufacturing a plate heat exchanger is to braze the heat exchanger plates together to form the plate heat exchanger.
  • Brazing a heat exchanger means that a number of heat exchanger plates are provided with a brazing material, after which the heat exchanger plates are stacked onto one another and placed in a furnace having a temperature sufficiently hot to at least partially melt the brazing material. After the temperature of the furnace has been lowered, the brazing material will solidify, whereupon the heat exchanger plates will be joined to one another to form a compact and strong heat exchanger.
  • the flow channels between the heat exchanger plates of a plate heat exchanger are created by providing the heat exchanger plates with a pressed pattern of ridges and grooves.
  • a number of heat exchanger plates are typically stacked on one another, wherein the plates can be identical to provide a symmetric plate heat exchanger or not identical to provide an asymmetric plate heat exchanger.
  • the ridges of a first heat exchanger plate contact the grooves of a neighboring heat exchanger plate and the plates are thus kept at a distance from each other through contact points.
  • flow channels are formed.
  • fluid media such as a first and second fluid media are lead so that heat transfer is obtained between such media.
  • a plurality of brazed plate heat exchangers with a pressed corrugated pattern having ridges and grooves in a herringbone pattern is known in the prior art. However, there is a need to improve such prior art heat exchangers.
  • EP3040670A1 discloses a heat exchanger having first and second plates, wherein the first plates comprise extruded ridges obliquely or parallel to a longitudinal direction of said plates, wherein the second plates comprise extruded ridges extending in the longitudinal direction along the whole length of said plates.
  • GB1561787 discloses a plate heat exchanger with flow spaces bounded by peripheral gaskets and arranged with gasketing to connect alternate flow spaces with ports for media, wherein a majority of the plates have an inclined corrugation and a minority of the plates have a longitudinal corrugation.
  • a brazed plate heat exchanger according to claim1.
  • the combination of different interplate flow channel volumes on opposite sides of the plates and at least two different plate patterns having different angles result in a BPHE with favourable properties for fluid distribution, wherein the fluid flow distribution and pressure drop can be balanced to achieve efficient heat exchange.
  • This makes it possible to achieve different properties in interplate flow channels on opposite sides of the same plate, wherein the flow and pressure drop on one side can be different from the opposite side.
  • the different flow channel volumes on opposite sides of the plates can be used for different types of medias, such as a liquid in one and a gas in the other.
  • a refrigerant start to evaporate it is transferred from a liquid state to a vapour state.
  • the liquid has a density that is much higher than the vapour density.
  • the performance (Temperature Approach, TA) of a heat exchanger is defined as the water outlet temperature (at the inlet of the heat exchanger channel) minus the evaporation temperature (Tdew) at the outlet of the heat exchanger channel.
  • Tdew evaporation temperature
  • the only way for the system to compensate for the too high refrigerant inlet temperature is by lowering the evaporation temperature until correct water outlet temperature can be reached.
  • a higher performance can be reached for the heat exchanger.
  • a lower overall refrigerant pressure drop in the channel will not only improve the heat exchanger performance it will also have a positive impact on the total system performance and, hence, the energy consumption.
  • At least one of the first and second heat exchanger plates can be an asymmetric heat exchanger plate.
  • the first heat exchanger plates are formed with another corrugation width than the second heat exchanger plates.
  • the first heat exchanger plate can be a symmetric heat exchanger plate, wherein the second heat exchanger plate can be an asymmetric heat exchanger plate.
  • first grooves of the second heat exchanger plates can be formed with a first depth
  • second grooves of the second heat exchanger plates can be formed with a second depth different from the first depth.
  • the depths of the first and second heat exchanger plates may differ from each other in a way that the interplate flow channels have different sizes seen in cross section, wherein the interplate flow channels have different volumes on opposite sides of the plates.
  • the interplate flow channels can have different cross section areas on opposite sides of the plates.
  • the first and second patterns can be herringbone patterns or patterns where the ridges and grooves extend in oblique straight lines over the heat exchanger plate.
  • the angles are in a plane of the heat exchanger plates, e.g. towards a side of the heat exchanger plates.
  • the angle is between a short side of a rectangular heat exchanger plate and the extension of the ridges and grooves.
  • the first and second angles such as first and second chevron angles, can be 0-90°, 25-70° or 30-45°.
  • the difference between the first and second angles can be 2-35°.
  • the first and second patterns can be in opposite directions, wherein the first and second angles are in opposite directions, such as towards opposite short sides of rectangular heat exchanger plates.
  • brazed plate heat exchanger Disclosed is also the use of a brazed plate heat exchanger according to the present invention for evaporation or condensation of media.
  • the heat exchanger 100 comprises a plurality of first heat exchanger plates 110 and a plurality of second heat exchanger plates 120 stacked in a stack to form the heat exchanger 100.
  • the first and second heat exchanger plates 110, 120 are arranged alternatingly, wherein every other plate is a first heat exchanger plate 110 and every other plate is a second heat exchanger plate 120.
  • the first and second heat exchanger plates are arranged in another configuration together with additional heat exchanger plates.
  • the heat exchanger 100 is an asymmetric plate heat exchanger.
  • the heat exchanger plates 110, 120 are made from sheet metal and are provided with a pressed pattern of ridges R1, R2a, R2b and grooves G1, G2a, G2b such that interplate flow channels for fluids to exchange heat are formed between the plates when the plates are stacked in a stack to form the heat exchanger 100 by providing contact points between at least some crossing ridges and grooves of neighbouring plates 110, 120 under formation of the interplate flow channels for fluids to exchange heat.
  • the pressed pattern of Figs. 1 and 2 is a herringbone pattern. However, the pressed pattern may also be in the form of obliquely extending straight lines. In any case, the pressed pattern of ridges and grooves is a corrugated pattern. The pressed pattern is adapted to keep the plates 110, 120 on a distance from one another, except from the contact points, to form the interplate flow channels.
  • each of the heat exchanger plates 110, 120 is surrounded by a skirt S, which extends generally perpendicular to a plane of the heat exchanger plate and is adapted to contact skirts of neighbouring plates in order to provide a seal along the circumference of the heat exchanger.
  • a skirt S which extends generally perpendicular to a plane of the heat exchanger plate and is adapted to contact skirts of neighbouring plates in order to provide a seal along the circumference of the heat exchanger.
  • Apart from the skirt S and ports 01-04 practically the remaining part of the heat exchanger plates 110, 120 forms a heat exchanging surface 130, 140.
  • the heat exchanger plates 110, 120 are arranged with port openings 01-04 for letting fluids to exchange heat into and out of the interplate flow channels.
  • the heat exchanger plates 110, 120 are arranged with a first port opening O1, a second port opening O2, a third port opening O3 and a fourth port opening O4. Areas surrounding the port openings O1 to O4 are provided at different heights such that selective communication between the port openings and the interplate flow channels is achieved.
  • the areas surrounding the port openings O1-O4 are arranged such that the first and second port openings O1 and O2 are in fluid communication with one another through some interplate flow channels, whereas the third and fourth port openings O3 and O4 are in fluid communication with one another by neighboring interplate flow channels.
  • the heat exchanger plates 110, 120 are rectangular with rounded corners, wherein the port openings 01-04 are arranged near the corners.
  • the heat exchanger plates 110, 120 are square, e.g. with rounded corners.
  • the heat exchanger plates 110, 120 are circular, oval or arranged with other suitable shape, wherein the port openings 01-04 are distributed in a suitable manner.
  • each of the heat exchanger plates 110, 120 is formed with four port openings O1-O4.
  • the number of port openings may be larger than four, i.e. six, eight or ten.
  • the number of port openings is at least six, wherein the heat exchanger is configured for providing heat exchange between at least three fluids.
  • the heat exchanger is a three circuit heat exchanger having at least six port openings and in addition being arranged with or without at least one integrated suction gas heat exchanger.
  • the number of port openings is at least six, wherein the heat exchanger includes one or more integrated suction gas heat exchangers.
  • the heat exchanger 100 comprises only the first and second heat exchanger plates 110, 120.
  • the heat exchanger 100 comprises a third and optionally also a fourth heat exchanger plate, wherein the third and optional fourth heat exchanger plates are arranged with different pressed patterns than the first and second heat exchanger plates 110, 120, and wherein the heat exchanger plates are arranged in a suitable order.
  • the heat exchanger 100 also comprises a start plate 150 and an end plate 160.
  • the start plate 150 is formed with openings corresponding to the port openings 01-04 for letting fluids into and out of the interplate flow channels formed by the first and second heat exchanger plates 110, 120.
  • the end plate 160 is a conventional end plate.
  • the first heat exchanger plates 110 are formed with a first pattern of ridges R1 and grooves G1.
  • the grooves G1 of the first heat exchanger plates are formed with identical depth D1.
  • all grooves G1 are formed with the same depth D1.
  • the depth D1 is 0.5-5 mm, such as 1-3 mm or 1.5-3 mm.
  • all ridges R1 are formed with the same height in a corresponding manner.
  • the corrugation depth of the first heat exchanger plates 110 is symmetrical and similar throughout the plate or at least substantially throughout the plate.
  • a section view of the second heat exchanger plate 120 is illustrated schematically according to one embodiment.
  • the second heat exchanger plates 120 are formed with a second pattern of first and second ridges R2a, R2b and first and second grooves G2a, G2b.
  • the first and second grooves G2a, G2b of the second heat exchanger plates 120 are formed with different depths, wherein the first grooves G2a are formed with a first depth D2a, and the second grooves G2b are formed with a second depth D2b, wherein the second depth D2b is different from the first depth D2a.
  • the first depth D2a is 0.5-5 mm, such as 0.5-3 mm, wherein the second depth D2b is 30-80% of the first depth D2a, such as 40-60% thereof.
  • the ridges R2a, R2b have different heights in a corresponding manner.
  • the first depth D2a is larger than the second depth D2b.
  • the first and second grooves G2a, G2b are arranged alternatingly.
  • the first and second grooves G2a, G2b, and optionally further grooves having other depths are arranged in any desired pattern.
  • the pattern of ridges and grooves of the second heat exchanger plates 120 is asymmetrical, i.e.
  • the second heat exchanger plates 120 would form an asymmetric heat exchanger when combined with first heat exchanger plates 110 such as shown below with reference to Fig. 5 .
  • the entire heat exchanging surface of the second heat exchanger plates 120 is formed with the second pattern of ridges and grooves having at least two different corrugation depths D2a, D2b of the grooves.
  • a plurality of the first and second heat exchanger plates 110, 120 have been stacked to schematically illustrate formation of interplate flow channels according to one embodiment.
  • every other plate is a first heat exchanger plate 110 and the remaining plates are second heat exchanger plates 120, wherein the first and second heat exchanger plates are arranged alternatingly to form an asymmetric heat exchanger 100, wherein the interplate flow channels are formed with different volumes.
  • the different volumes of the interplate flow channels are formed by an extended profile on the same press depth or corrugation depth.
  • the first and second heat exchanger plates are provided with different corrugation depths.
  • the first and/or second heat exchanger plates is/are asymmetric heat exchanger plates.
  • the first and/or second heat exchanger plates is/are symmetric heat exchanger plates.
  • the first pattern of ridges R1 and grooves G1 of the first heat exchanger plate 110 is illustrated schematically.
  • Said pattern is a pressed herringbone pattern, wherein the ridges R1 and grooves G1 are arranged with two inclined legs meeting in an apex, such as a centrally arranged apex, forming an arrow pattern.
  • said legs of the ridges R1 and grooves G1 are equally long.
  • the apices are distributed along an imaginary centre line, such as a longitudinal centre line of a rectangular heat exchanger plate.
  • the herringbone pattern is arranged so that ridges R and grooves G extend from one long side to the other of the first heat exchanger plate 110, e.g.
  • the pattern of the first heat exchanger plate 110 i.e. the first pattern of ridges R1 and grooves G1, exhibits a first chevron angle ⁇ 1.
  • the chevron angle is the angle between the ridge and an imaginary line across the plate, perpendicular to the long sides of a rectangular plate, which is illustrated schematically by means of the dashed line C.
  • the chevron angle is the angle between the leg of the ridge and a short side of the heat exchanger plate towards which the apex is pointing.
  • the long sides of the heat exchanger plates extend perpendicular to the short sides and hence the pattern of ridges and grooves is also arranged so that the ridges have an angle to the long sides.
  • the chevron angle is the same on both sides of the apex.
  • the entire or substantially entire first pattern of ridges and grooves is formed with the first chevron angle ⁇ 1 throughout the heat exchanging surface 130 of the plate.
  • the first chevron angle ⁇ 1 is between 5° and 85°, 25° and 70° or 40° and 65°.
  • the first pattern of ridges R1 and grooves G1 of the first heat exchanger plate 110 is illustrated schematically according to an alternative embodiment, wherein the pressed pattern is in the form of obliquely extending straight lines.
  • the pressed pattern of ridges and grooves is a corrugated pattern of obliquely extending straight lines.
  • the obliquely extending straight lines of the first heat exchanger plates 110 are arranged in the angle ⁇ 1.
  • the pattern is arranged so that ridges R1 and grooves G1 extend, e.g. in parallel, from one long side to the other of the first heat exchanger plate 110.
  • the second pattern of ridges R2a, R2b and grooves G2a, G2b of the second heat exchanger plate 120 is illustrated schematically.
  • Said second pattern is a pressed herringbone pattern as described above with reference to the first heat exchanger plate 110 but with a second chevron angle ⁇ 2 different from the first chevron angle ⁇ 1.
  • the second heat exchanger plate 120 is arranged with a herringbone pattern having a different angle than the first heat exchanger plate.
  • the second chevron angle ⁇ 2 is between 5° and 85°, 25° and 70° or 40° and 65°.
  • the entire or substantially entire pattern of ridges and grooves of the second heat exchanger plates 120 is formed with the second chevron angle ⁇ 2 throughout the heat exchanging surface 140 of the plate.
  • the second pattern of ridges R2a, R2b and grooves G2a, G2b is arranged in the opposite direction as the first pattern of ridges R1 and grooves G1.
  • the apices of the herringbone pattern of the second heat exchanger plate 120 point in the opposite direction as the apices of the herringbone pattern of the first heat exchanger plate 110.
  • the apices of the first pattern of ridges R1 and grooves G1 point toward one short side of the first heat exchanger plate 110, wherein the apices of the second pattern of ridges R2a, R2b and grooves G2a, G2b point toward the opposite short side of the second heat exchanger plate 120, so that the herringbone patterns alternatingly are arranged in opposite directions throughout the heat exchanger 100.
  • the first and second angles ⁇ 1, ⁇ 2 are in opposite directions.
  • the first angle ⁇ 1 is towards one short side of the heat exchanger plates and the second angle ⁇ 2 is towards the opposite short side.
  • the second pattern of ridges R2a, R2b and grooves G2a, G2b of the second heat exchanger plate 120 is illustrated schematically according to an alternative embodiment, wherein the pressed pattern is in the form of obliquely extending straight lines.
  • the pressed pattern of ridges and grooves is a corrugated pattern of obliquely extending straight lines.
  • the obliquely extending straight lines of the second heat exchanger plates 120 are arranged in the angle ⁇ 2.
  • the pattern is arranged so that ridges R and grooves G extend, e.g. in parallel, from one long side to the other of the second heat exchanger plate 120.
  • the second pattern of ridges R2a, R2b and grooves G2a, G2b is arranged in the opposite direction as the first pattern of ridges R1 and grooves G1.
  • the pattern of the second heat exchanger plate 120 is oblique in the opposite direction as the pattern of obliquely extending straight lines of the first heat exchanger plate 110, so that the patterns alternatingly are arranged in opposite directions throughout the heat exchanger 100.
  • the first angle ⁇ 1 is towards one short side of the heat exchanger plates and the second angle ⁇ 2 is towards the opposite short side.
  • the first and second heat exchanger plates 110, 120 are formed with different chevron angles ⁇ 1, ⁇ 2 and different pressed patterns resulting in different interplate volumes.
  • the first and second heat exchanger plates 110, 120 are provided with different corrugation depths.
  • the first and second heat exchanger plates 110, 120 are provided with different corrugation frequencies.
  • the first and second heat exchanger plates 110, 120 are provided with the same corrugation depth but different corrugation frequencies.
  • the first and second heat exchanger plates 110, 120 are provided with different corrugation depths and/or different corrugation frequencies.
  • one of the first and second heat exchanger plates 110, 120 is a symmetric heat exchanger plate, wherein the other is asymmetric.
  • both the first and second heat exchanger plates 110, 120 are asymmetric.
  • both the first and second heat exchanger plates 110, 120 are symmetric.
  • Figs. 8 and 9 contact points between the first and second plates 110, 120 are illustrated schematically using the example of Fig. 5 .
  • brazing joints 170 are formed in and/or around the contact points 170 between crossing ridges and grooves.
  • brazing joints 170 are formed in all contact points.
  • brazing joints 170 are formed in only some of the contact points.
  • the first heat exchanger plate 110 is arranged on the second heat exchanger plate 120, wherein contact points are formed in a first pattern.
  • all crossings between the ridges R1 of the first heat exchanger plate 110 and ridges or grooves of the second heat exchanger plate 120 result in a contact point.
  • Fig. 9 is a schematic view of the second heat exchanger plate 120 arranged on the first heat exchanger plate 110, wherein contact points are formed in a second pattern.
  • a contact point which may form a brazing joint 170
  • the second ridges R2b are arranged with a gap to the crossing ridges or grooves of the first heat exchanger plate 110.
  • no contact points are formed, and no brazing joint is formed, between the second ridges R2b of the second heat exchanger plate 120 and the first heat exchanger plate 110.
  • all contact points are showed with a brazing joint 170.
  • the brazing joints 170 between the first and second heat exchanger plates 110, 120 are elongated, such as oval, wherein the brazing joints 170 are arranged in a first orientation in the interplate flow channels having bigger volume and in a second orientation in the interplate flow channels having smaller volume to provide a favourable pressure drop in the desired interplate flow channels.
  • the brazing joints 170 are arranged in a first angle in relation to a longitudinal direction of the plates 110, 120 in the interplate flow channels having bigger volume and in a second angle in the remaining interplate flow channels.
  • the first angle is bigger than the second angle.
  • a cross section of a part of a heat exchanger comprising first and second heat exchanger plates 110, 120 is illustrated schematically.
  • the first heat exchanger plate 110 is a symmetric heat exchanger plate, wherein the second heat exchanger plate 120 is an asymmetric heat exchanger plate as described above.
  • the corrugation depth of the first heat exchanger plate 110 is constant, wherein the corrugation depth of the second heat exchanger plate 120 is varying.
  • the second heat exchanger plate 120 is formed with at least two different corrugation depths.
  • the first and second heat exchanger plates 110, 120 are formed with corrugated patterns different angles, such as chevron angles, as described above.
  • the chevron angle of the first heat exchanger plate 110 is 54 degrees, wherein the chevron angle of the second heat exchanger plate 120 is 61 degrees.
  • neighbouring interplate volumes are different, so that the interplate volume on one side of the first heat exchanger plates 110 is different from the interplate volume on the opposite side of the first heat exchanger plates 110.
  • this also apply for the second heat exchanger plates 120.
  • the interplate volume between the first and second heat exchanger plates is different from the interplate volume between the second and first heat exchanger plates.
  • a cross section area on one side of the first heat exchanger plates 110 is different from the cross section area on the opposite side of the first heat exchanger plates 110.
  • FIG. 11 a cross section of a part of a heat exchanger comprising first and second heat exchanger plates 110, 120 according to yet another embodiment is illustrated schematically.
  • the first heat exchanger plate 110 is a symmetric heat exchanger plate, wherein the second heat exchanger plate 120 is an asymmetric heat exchanger plate as described above.
  • the chevron angle of the first heat exchanger plate 110 is 45 degrees, wherein the chevron angle of the second heat exchanger plate 120 is 61 degrees.
  • a cross section of a part of a heat exchanger comprising first and second heat exchanger plates 110, 120 is illustrated schematically.
  • the first heat exchanger plate 110 is an asymmetric heat exchanger plate, wherein the second heat exchanger plate 120 is also an asymmetric heat exchanger plate.
  • the chevron angle of the first heat exchanger plate 110 is different from the chevron angle of the second heat exchanger plate 120 as described above.
  • the interplate flow channels have different volumes as described above.
  • the brazing joints are elongated, such as oval, and arranged in a first orientation in the interplate flow channels having bigger volume and in a different, second orientation in the interplate flow channels having smaller volume.
  • a cross section of a part of a stack of first and second heat exchanger plates 110, 120 is illustrated schematically.
  • the first and second heat exchanger plates 110, 120 are provided with different corrugation depths.
  • the first heat exchanger plate 110 is a symmetric heat exchanger plate, wherein the second heat exchanger plate 120 is an asymmetric heat exchanger plate.
  • both the first and second heat exchanger plates 110, 120 are symmetric or asymmetric.
  • the chevron angle of the first heat exchanger plate 110 is different from the chevron angle of the second heat exchanger plate 120 and the interplate flow channel volumes formed by the first and second heat exchanger plates 110, 120 when brazed together in brazing joints are different.
  • the heat exchanger according to the present invention is, e.g. used for condensation or evaporation, wherein at least one media at some point is in gaseous phase.
  • the heat exchanger is used for heat exchange, wherein condensation or evaporation takes place in the interplate flow channels of bigger volume.
  • a liquid media such as water or brine, is conducted through the interplate flow channels having smaller volume.
  • the first pattern of ridges R1 and grooves G1 of the first heat exchanger plate 110 is illustrated schematically.
  • the pressed pattern according to the embodiment of Fig. 14 is a herringbone pattern but may alternatively be a pattern of oblique lines and thus exhibits the first angle ⁇ 1 generally as described above with reference to Figs. 6a and 6b .
  • the first angle ⁇ 1 is in a central main heat exchanging section of the heat exchanger plate 110.
  • the first pressed pattern partially comprises the first angle ⁇ 1.
  • the central main heat exchanging section extends across the first heat exchanger plate 110 from one side to the opposite side.
  • the central main heat exchanging section is arranged between first and second heat exchanging sections at port openings of the heat exchanger plate, called end sections herein.
  • the first and second end sections are, for example, arranged at opposite ends of the first heat exchanger plate 110.
  • the first and second end sections extend across the first heat exchanger plate 110 from one side to the opposite side thereof and optionally also extends to a third side, such as a short side, of the heat exchanger plates.
  • the first end section includes port openings, such as the first port opening O1 and the third port opening O3.
  • the second end section includes port openings, such as the second and fourth port openings O2, O4.
  • the pressed pattern of ridges and grooves R1, G1 is arranged with an angle ⁇ 1' in at least one end section, such as the first and/or second end sections, which angle ⁇ 1' differs from the angle ⁇ 1 of the pressed pattern in the central main heat exchanging section.
  • the direction of the pressed pattern is the same in the central main section as in the end sections.
  • the angle is the same in both end sections.
  • the angle in the first end section is different from the angle in the second end section.
  • the second heat exchanging portion 140 is arranged with a pattern or an angle different from the first end section.
  • the first pattern is at least partially arranged with the first angle ⁇ 1.
  • the first angle ⁇ 1 is bigger than the different angle ⁇ 1'.
  • the first heat exchanger plate 110 is illustrated as an example but it is understood that the second pressed pattern of the second heat exchanger plate 120 is designed in a corresponding manner, wherein the second pattern of ridges R2a, R2b and grooves G2a, G2b is arranged with the angle ⁇ 2 in the central main heat exchanging section and one or more of the end sections are arranged with a different angle ⁇ 2' (not illustrated).
  • the second heat exchanger plates 120 at least some of the ridges R2a, R2b and grooves G2a, G2b extend in the angle ⁇ 2, wherein others extend in the differing angle ⁇ 2'.
  • the second pattern is at least partially arranged with the second angle ⁇ 2.
  • the second angle ⁇ 2 is, e.g. in the opposite direction as the first angle ⁇ 1.
  • the first pattern exhibit chevrons in the opposite direction as chevrons of the second pattern and hence chevron angles in opposite directions.
  • the first heat exchanger plate 110 comprises small port openings SO1, SO2 and a dividing surface DW to provide a separate heat exchanging section which can form an integrated suction gas heat exchanger of a heat exchanger comprising alternatingly arranged first and second plates 110, 120 with such a design.

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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)

Claims (13)

  1. Gelöteter Plattenwärmetauscher (100), welcher mehrere rechteckige erste und zweite Wärmetauscherplatten (110, 120) umfasst, wobei die ersten Wärmetauscherplatten (110) mit einem ersten Muster von Rippen und Nuten ausgebildet sind und die zweiten Wärmetauscherplatten (120) mit einem zweiten Muster von Rippen und Nuten ausgebildet sind, die Kontaktpunkte zwischen wenigstens einigen sich kreuzenden Rippen und Nuten benachbarter Platten bereitstellen, unter Bildung von Strömungskanälen zwischen den Platten für Fluide zum Wärmeaustausch, wobei die Strömungskanäle zwischen den Platten über Anschlussöffnungen in selektiver Fluidverbindung stehen, wobei das erste Muster von Rippen und Nuten von dem zweiten Muster von Rippen und Nuten verschieden ist, so dass ein Strömungskanalvolumen zwischen den Platten auf einer Seite der ersten Wärmetauscherplatten (110) von dem Strömungskanalvolumen zwischen den Platten auf der gegenüberliegenden Seite der ersten Wärmetauscherplatten (110) verschieden ist,
    wobei wenigstens einige der Rippen und Nuten des ersten Musters sich in einem ersten Winkel (31) zu einer kurzen Seite der Wärmetauscherplatten erstrecken und wenigstens einige der Rippen und Nuten des zweiten Musters sich in einem zweiten Winkel (β2) zu einer kurzen Seite der Wärmetauscherplatten erstrecken, wobei der zweite Winkel (β2) von dem ersten Winkel (31) verschieden ist,
    dadurch gekennzeichnet, dass
    das erste und das zweite Muster von Rippen und Nuten Wellenmuster von schräg verlaufenden Geraden sind oder das erste Muster ein erstes Fischgrätmuster ist und das zweite Muster ein zweites Fischgrätmuster ist,
    die Nuten (G1) der ersten Wärmetauscherplatten (110) mit identischer Wellungstiefe (D1) ausgebildet sind, wobei erste Nuten (G2a) der zweiten Wärmetauscherplatten (120) mit einer ersten Tiefe (D2a) und zweite Nuten (G2b) der zweiten Wärmetauscherplatten (120) mit einer zweiten Tiefe (D2b), die von der ersten Tiefe (D2a) verschieden ist, ausgebildet sind,
    und
    Lötverbindungen (170) an den und um die Kontaktpunkte zwischen sich kreuzenden Rippen und Nuten zwischen den ersten und zweiten Wärmetauscherplatten (110, 120) lang gestreckt und mit einer ersten Ausrichtung in den Strömungskanälen zwischen den Platten mit größerem Volumen und mit einer zweiten Ausrichtung in den Strömungskanälen zwischen den Platten mit kleinerem Volumen angeordnet sind.
  2. Gelöteter Plattenwärmetauscher nach Anspruch 1, wobei die Strömungskanäle zwischen den Platten auf einer Seite der ersten Wärmetauscherplatten (110) eine andere Querschnittsfläche als auf der gegenüberliegenden Seite aufweisen.
  3. Gelöteter Plattenwärmetauscher nach Anspruch 1 oder 2, wobei wenigstens ein zentraler Haupt-Wärmeaustauschabschnitt der ersten Wärmetauscherplatten (110) den ersten Winkel (β1) aufweist, wobei wenigstens ein zentraler Haupt-Wärmeaustauschabschnitt der zweiten Wärmetauscherplatten (120) den zweiten Winkel (β2) aufweist.
  4. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei eine Tiefe (D1) der Nuten (G1) der ersten Wärmetauscherplatte (110) im Bereich von 0,5-5 mm, vorzugsweise im Bereich von 0,6-2 mm liegt.
  5. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei eine erste Tiefe (D2a) der zweiten Wärmetauscherplatte (120) im Bereich von 0,5-5 mm, vorzugsweise im Bereich von 0,6-3 mm liegt und eine zweite Tiefe (D2b) der zweiten Wärmetauscherplatte (120) im Bereich von 30-80 % der ersten Tiefe (D2a) liegt.
  6. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei der erste Winkel (β1) des ersten Musters von Rippen und Nuten im Bereich von 25-70° liegt.
  7. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei der zweite Winkel (β2) des zweiten Musters von Rippen und Nuten im Bereich von 25-70° liegt.
  8. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei eine Differenz zwischen dem ersten Winkel (β1) des ersten Musters von Rippen und Nuten und dem zweiten Winkel (β2) des zweiten Musters von Rippen und Nuten im Bereich von 2-35° liegt.
  9. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei die ersten und zweiten Wärmetauscherplatten (110, 120) mit unterschiedlichen Wellungstiefen versehen sind.
  10. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei die Wärmetauscherplatten (110, 120) mit unterschiedlichen Wellungsbreiten versehen sind.
  11. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei das erste Muster ein erstes Fischgrätmuster oder ein erstes Muster von schräg verlaufenden Geraden ist und das zweite Muster ein zweites Fischgrätmuster oder ein zweites Muster von schräg verlaufenden Geraden ist, und wobei Rippen und Nuten des ersten und zweiten Musters sich von einer langen Seite der Wärmetauscherplatten zur anderen erstrecken, und wobei der erste Winkel zu einer kurzen Seite der Wärmetauscherplatten gerichtet ist und der zweite Winkel zu der gegenüberliegenden kurzen Seite gerichtet ist.
  12. Gelöteter Plattenwärmetauscher nach einem der vorhergehenden Ansprüche, wobei die ersten und zweiten Wärmetauscherplatten (110, 120) abwechselnd angeordnet sind, wobei im gesamten Wärmetauscher (100) jede zweite Platte eine erste Wärmetauscherplatte (110) ist und jede zweite Platte eine zweite Wärmetauscherplatte (120) ist.
  13. Verwendung eines gelöteten Plattenwärmetauschers nach einem der Ansprüche 1 bis 12 zur Verdampfung oder Kondensation von Medien, wobei Medien in den Strömungskanälen zwischen den Platten mit kleinerem Volumen verdampft oder kondensiert werden und wobei flüssige Medien zu den Strömungskanälen zwischen den Platten mit größerem Volumen geleitet werden.
EP21705649.8A 2020-01-30 2021-01-29 Hartgelöteter plattenwärmetauscher und dessen verwendung Active EP4097413B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP25193080.6A EP4617602A3 (de) 2020-01-30 2021-01-29 Gelöteter plattenwärmetauscher und verwendung davon
SI202130355T SI4097413T1 (sl) 2020-01-30 2021-01-29 Lotan ploščat toplotni izmenjevalnik in uporaba le-tega

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SE2050094A SE545690C2 (en) 2020-01-30 2020-01-30 A brazed plate heat exchanger and use thereof
PCT/SE2021/050067 WO2021154152A1 (en) 2020-01-30 2021-01-29 A brazed plate heat exchanger and use thereof

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JP (2) JP7736693B2 (de)
CN (1) CN114945789A (de)
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SE (1) SE545690C2 (de)
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CN116817640A (zh) * 2022-04-28 2023-09-29 浙江三花板换科技有限公司 板式换热器
PT4310428T (pt) * 2022-07-22 2025-03-03 Alfa Laval Corp Ab Permutador de calor de placas submetidas a soldadura forte
FR3165715A1 (fr) * 2024-08-20 2026-02-27 Valeo Systemes Thermiques Echangeur de chaleur
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EP4617602A3 (de) 2025-10-15
SE2050094A1 (en) 2021-07-31
EP4617602A2 (de) 2025-09-17
EP4097413A1 (de) 2022-12-07
US20230036224A1 (en) 2023-02-02
JP7736693B2 (ja) 2025-09-09
SE545690C2 (en) 2023-12-05
JP2023512425A (ja) 2023-03-27
PL4097413T3 (pl) 2025-12-22
CN114945789A (zh) 2022-08-26
JP2025170375A (ja) 2025-11-18
WO2021154152A1 (en) 2021-08-05
SI4097413T1 (sl) 2025-12-31

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