WO2020211903A1 - Échangeur de chaleur à plaques et à nervures - Google Patents

Échangeur de chaleur à plaques et à nervures Download PDF

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Publication number
WO2020211903A1
WO2020211903A1 PCT/DE2020/100286 DE2020100286W WO2020211903A1 WO 2020211903 A1 WO2020211903 A1 WO 2020211903A1 DE 2020100286 W DE2020100286 W DE 2020100286W WO 2020211903 A1 WO2020211903 A1 WO 2020211903A1
Authority
WO
WIPO (PCT)
Prior art keywords
ribs
plate
heat exchanger
rib
flow
Prior art date
Application number
PCT/DE2020/100286
Other languages
German (de)
English (en)
Inventor
Hans Quack
Original Assignee
Hans Quack
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 Hans Quack filed Critical Hans Quack
Publication of WO2020211903A1 publication Critical patent/WO2020211903A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • 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
    • F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • 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
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/18—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes sintered

Definitions

  • the invention relates to a plate-fin heat exchanger which can be used in particular for cryotechnical applications or applications in aerospace.
  • a plate-fin heat exchanger of the generic type has at least two flow channels for the heat-transferring fluids, which are materially separated from one another by a partition wall as a plate.
  • the heat transfer from one fluid to the other fluid takes place through the partition wall, with ribs being provided in the flow channels which enlarge the heat transferring surface area beyond the surface of the partition wall.
  • ribs which serve to increase the surface area of the heat-transferring surface and which, due to the material, have good thermal conductivity.
  • heat exchangers are also known which use profile tubes instead of plates to separate the fluid flows, with one fluid flowing in the tubes and the second fluid flowing around the tubes.
  • a profile tube for heat exchangers emerges, a profile tube with a teardrop-shaped outer contour being proposed for the matrix of a tubular heat exchanger.
  • a first fluid flows through the profile tube and the second fluid flows around the matrix of the correspondingly profiled profile tubes.
  • profile tubes according to GB 468,980 are known which also provide profile tubes with a teardrop-shaped contour in a matrix-like arrangement for a heat-transferring fluid to flow around.
  • the heat exchangers according to the prior art generally have the disadvantage that the individual components cannot be miniaturized as desired in order to reduce the size of the heat exchangers.
  • the object of the invention is to provide a plate-fin heat exchanger which has good heat transfer properties while at the same time being small in size and which can also be produced with little manufacturing effort in a pressure-stable design, for example for use in cryotechnical systems.
  • the pressure-tight and material-tight separation of the fluid flows in the heat exchanger continues to place particularly high demands on the manufacturing technology and the design of the heat exchanger.
  • a plate-fin heat exchanger which is constructed from a top and a bottom plate as horizontal boundary plates and side walls and an arrangement of several ribs arranged perpendicular to the direction of flow.
  • the ribs extend vertically and rod-shaped between the horizontal delimitation plates.
  • At least one partition wall is formed as a plate of the plate heat exchanger between the horizontal delimitation plates, through which the ribs penetrate.
  • the partition wall as a horizontal plane between the horizontal delimitation plates thus forms at least two flow channels through which fluid flows can flow and which are materially separated by the partition wall. If more than one partition is provided, additional flow channels are formed corresponding to the number of partition walls, which can be combined to form different flows.
  • the ribs have a rib depth and a rib width in the flow direction.
  • ribs are arranged in a row of ribs transversely to the flow direction and several rows of ribs are arranged one behind the other at a row spacing in the flow direction.
  • the ribs of adjacent or successive rows of ribs are arranged offset from one another in such a way that the cross sections of the ribs overlap in the flow direction.
  • a gap with a gap width through which fluid can flow is formed between adjacent ribs.
  • the ribs are preferably designed as a triangle in cross section and have a pointed inflow edge and a pointed outflow edge.
  • a triangle is understood geometrically as a cross section which has two opposite corners with acute angles, which are connected to one another to form a surface without forming a further corner which is effective in terms of fluid mechanics.
  • the partition between the flow channels is preferably made geometrically several horizontal surface elements, also called individual surfaces, built up, the transitions of the individual surfaces in the rib being designed to be inclined relative to the horizontal by a manufacturing angle alpha.
  • the rib cross-section is designed in a diamond shape, the corners of the rhombus of the rib cross-section advantageously being rounded with the larger angle, thereby forming the cross-section of a delta.
  • the ratio of the rib depth as the longitudinal diagonal of the rhombus to the rib width as the transverse diagonal of the rhombus of the rib cross-section is advantageously between 1.5 and 3 and preferably 2.
  • the longitudinal diagonal is about twice as long as the transverse diagonal.
  • a rib capital is advantageously formed at the transition of the ribs into the upper horizontal delimitation plate.
  • the rib capital comparable to a column capital, is also referred to as the rib head and is the area of transition of the cross section of the rib into the upper horizontal delimitation plate.
  • the surface elements of the partition, the individual surfaces, are preferably designed as basic diamonds.
  • the rib diamonds are designed to be smaller than the basic diamonds by a reduction factor beta.
  • the individual surfaces are formed on the upper separating surface in the transition from the basic diamond to the ribbed diamond at a manufacturing angle for generative manufacturing processes with a maximum inclination of 45 °.
  • the inclination is understood to mean the angle to the vertical.
  • the reduction factor beta from the rib diamond to the basic diamond is advantageously in a range between 0.6 and 0.9.
  • the heat exchanger is preferably made with a plurality of essentially horizontal ones Partitions. Several flow areas are thus designed as floods in which the heat-transferring fluids can be guided in cocurrent, countercurrent or cross-flow.
  • the heat exchanger is designed for fluid flows of different volume flows, for example fluid flows at different pressure levels.
  • the ribs are preferably provided with a vertical gap in the direction of flow in order to provide an additional flow cross section with an additional heat transfer surface compared to the area of the low pressure flow.
  • the horizontal gap is preferably formed in the rib depth, the longitudinal diagonal of the rib diamond of the rib.
  • the rib advantageously has a different reduction factor beta from the rib diamond to the base diamond in the area of the high pressure flow than in the area of the low pressure flow.
  • the rib preferably has a larger reduction factor in connection with a gap in the area of the high pressure flow.
  • the reduction factor beta is designed to be variable in the direction of flow from the rib diamond to the base diamond when the volume flow changes along the heat exchanger.
  • the ribs are preferably made of solid material, a material with the best possible thermal conductivity being selected as the solid material. Metals such as aluminum or copper and corresponding alloys thereof are therefore particularly suitable.
  • the outer walls of the heat exchanger are preferably made of an outer and an inner layer, wherein the outer layer has a lower thermal conductivity than the inner layer.
  • the inner layer of the outer walls and the ribs are preferably formed from the same material which is a good conductor of heat.
  • secondary ribs are advantageously formed on the ribs, the secondary ribs being designed to be inclined relative to the horizontal by a manufacturing angle alpha.
  • the object of the invention is further achieved by a method for producing a plate-fin heat exchanger in which the outer walls, the partition and the fins are produced as one piece by means of laser sintering or laser melting as a generative production method.
  • This provides excellent heat conduction from the rib of higher temperature transversely to the direction of flow through the partition wall into the rib of lower temperature, with heat being additionally transferred through the partition wall.
  • only the horizontal inner layers of the outer walls are produced together with the ribs and the partition wall by means of laser sintering or laser melting as a generative manufacturing process.
  • the conception of the invention is that a highly efficient plate-fin heat exchanger can be produced by making the plates and fins in one piece and from a material that conducts heat well, such as metal, since only heat conduction within one material between the plate and within the fin and there is no heat transfer between different materials or across a gap.
  • the plates which functionally represent the partitions for material separation between the flowing fluids, and the rod-shaped ribs penetrating the plates are through the Use of generative manufacturing processes in one piece, i.e. as one piece and in one operation. Manufacturing processes are, for example, laser sintering or laser melting.
  • the rod-shaped ribs extend on both sides out of the partition wall into the flow paths, or flow areas, of the heat-transferring fluids.
  • the dividing wall of the flow areas is composed of individual geometric surface elements, the surface elements of the dividing wall preferably forming the basis for the geometry of the ribs. The division into surface elements is advantageous as an intermediate stage in the construction; this division then no longer plays a role in manufacture.
  • the ribs are thus made on both sides of the partition and the partition is constructed from a large number of individual surfaces with ribs resulting therefrom.
  • the ribs are preferably aligned vertically along the flow direction of the fluids and several ribs are designed as a row of ribs transversely to the flow direction. Several rows of ribs are arranged offset to one another along the direction of flow, so that a matrix of ribs around which flow flows is formed.
  • the matrix is designed in a particularly preferred manner in such a way that the cross sections of the ribs overlap, viewed in the direction of flow, and channels through which the fluids flow are thus formed between the adjacent ribs.
  • the channels are designed in such a way that the arrangement achieves guidance of the fluid flow which prevents the flow from separating on the rear side of the ribs or the pointed corner of the triangle facing away from the flow.
  • Laminar flow without flow separation is particularly advantageous due to the forced guidance of the fluids in the channels combined with the optimized flow Heat conduction with the ribs passing through the partition walls.
  • the heat transfer from one fluid flow to another is also referred to as dual flow transfer, with heat exchangers according to the conception of the invention also being designed in the same way as three or multiple flow heat exchangers.
  • the advantages of the invention are in particular that heat can be transferred between different fluids in a highly efficient manner via continuous, heat-conducting ribs, the fluids being reliably separated from one another in terms of material by plates or partition walls.
  • Generative manufacturing processes enable the creation of geometrically complex structures of flow-optimized ribs with partition walls with optimized costs and time expenditure.
  • Fig. 1 Plate-fin heat exchanger
  • Fig. 2 Cross section of a plate-fin heat exchanger
  • Fig. 3 Cross-section of individual surface and rib as a basic diamond and rib diamond in the low-pressure flow area
  • Fig. 4 Cross-section of the individual surface and rib as a base diamond and rib diamond in the floch pressure flow area
  • Fig. 5 Rib with rib capital in the low-pressure flow area
  • Fig. 6 Wall area and a rib in the low-pressure flow area
  • Fig. 7 Rib with rib capital in the floch pressure flow area
  • Fig. 8 Wall area and a rib in the floch pressure flow area
  • Fig. 9 Rib columns with partition walls
  • Fig. 10 Section of plate-fin heat exchanger with primary fins
  • a plate-fin heat exchanger 1 is shown, which essentially consists of three areas.
  • a cuboid heat-transferring area is bounded laterally by a connection and distribution area 11, which have fluid connections and at the same time distribute the fluids to the flow areas.
  • the heat-transferring area is cuboid and is made up of horizontal delimitation plates 2 above and below and the lateral delimitation plates as side walls 3. In the illustration according to FIG. 1, only the upper horizontal delimitation plate 2 and one side wall 3 are shown.
  • the heat-transferring fluids are fed into the plate-fin heat exchanger 1 via the fluid connection and the distributor of the first connection and distribution area 11 and are discharged via the second connection and distribution area 11.
  • the heat transfer takes place during the longitudinal flow of the fluids in the flow direction 9, for example using the countercurrent principle.
  • the entire heat exchanger 1 is produced in a single operation using an additive manufacturing process, so that no assembly of otherwise customary individual components of the heat exchanger is required.
  • the heat exchanger is particularly advantageously manufactured from aluminum or copper alloys by means of laser melting or laser sintering in order to achieve high thermal conductivity.
  • the plate-fin heat exchanger 1 is shown in cross section.
  • the connection and distribution area 11 merges into the heat-transferring area in the sectional plane.
  • the sectional plane shows the horizontally lying partition walls 8 which are arranged between the horizontal delimitation plates 2 above and below.
  • the flow channels 6, also referred to as flow areas, in which the fluids are guided, are formed between adjacent partition walls 8.
  • ribs 7 are arranged in rows across the direction of flow. The ribs 7 extend vertically and rod-shaped continuously from the lower horizontal delimitation plate 2 to the upper horizontal delimitation plate 2 through the Partitions 8 therethrough.
  • the ribs 7 penetrate the dividing walls 8 geometrically in a vertical direction and thus alternately run through flow channels 6 of the heat-transferring fluids, the fluids being, for example, once under pressure and high temperatures on the one hand and under low pressure and lower temperatures on the other. Heat is transferred from the high pressure fluid to the low pressure fluid between the adjacent flow areas with fluids with different pressures and temperatures.
  • the flow channels 6 for the low-pressure fluid are designed with a larger flow cross-section due to a larger distance between the partition walls 8 delimiting the flow channel 6 in comparison to the flow channels 6 for the fluid under high pressure.
  • flow channels 6 for high pressure and low pressure are alternately shown, through which the flow passes in countercurrent, the top and bottom channels each forming half a flow channel for low pressure in cross section.
  • the task of the plate-fin heat exchanger 1 given by the process is the cooling of a high pressure flow and the warming up of a low pressure flow.
  • the volume flow of the high pressure flow is, for example, ten times lower than that of the low pressure flow. Therefore the high pressure channels have lower channel heights.
  • the plate-fin heat exchanger 1 consists of individual parallel flow channels 6 arranged horizontally one above the other, with high-pressure and low-pressure channels preferably being arranged alternately.
  • the low-pressure flow has two inlets and two outlets, the high-pressure flow has an inlet and an outlet and is arranged between the connections for the low-pressure flow.
  • FIG. 3 shows a detail of a horizontal section in the direction of flow 9 in a flow channel for the low-pressure flow.
  • Two ribs 7 are shown with solid lines with their rib cross-section 13.
  • the geometry of the individual surfaces 12 from which the partition 8 is constructed is shown with a dashed line.
  • the Individual surfaces 12 and the rib cross-sections 13 are shown as rhombuses in the embodiment shown.
  • the base diamond 15 of the individual surface 12 merges into the ribbed diamond 16, which has a pointed leading edge 4 and a pointed trailing edge 5.
  • the longitudinal diagonal of the diamond is in relation to the transverse diagonal of the diamond of, for example, two to one.
  • the rib depth a corresponds to the longitudinal diagonal of the rib cross section 13 of the rib diamond 16.
  • the rib width b corresponds to the transverse diagonal of the rib diamond 16 minus the length of the rounded edges.
  • a gap 10 with a gap width e is formed between the ribs 7 of adjacent rows in the flow direction 9.
  • the row spacing of adjacent rows c denotes the spacing of the area centers of the diamonds.
  • FIG. 4 analogously to the illustration in FIG. 3, the configuration of ribs 7 for the high pressure flow is shown.
  • longitudinal gaps are designed to increase the surface area of the ribs in the high-pressure channels.
  • the high pressure flow has a significantly smaller volume flow than the low pressure flow. Therefore the rib height of the channels can be chosen lower. With the same rib design, the heat transfer area would decrease more than the heat transfer coefficient would improve. Therefore, the heat transfer area needs to be increased. For this purpose, a straight channel is laid as a gap 10 through the center of the rib 7.
  • the cross-section of the individual surfaces 12 is in relation to the rib cross-section 13 in the illustrated embodiment as a base diamond 15 and rib diamond 16.
  • This ratio as the quotient of the dimensions of rib diamond 16 to base diamond 15 is referred to as the reduction factor beta.
  • FIGS. 5a and 5b a part of a rib 7 with a rib capital 14, also referred to as the rib head, shown.
  • the ribs 7 are arranged in the area of the fluid flowing under low pressure.
  • the transition between the rib 7 and the partition 8, or the individual surfaces 12 of the partition 8, is referred to as the rib capital 14.
  • the rib cross-section 13 is shown in section in FIG. 5a and the individual surface 12 in FIG. 5b.
  • the individual surfaces 12, in turn, are part of the partition wall 8 into which the rib 7 merges or which is penetrated by the rib 7. Only one rib 7 extending from one side of the partition 8 is shown in FIGS.
  • FIGS. 6a and 6b the edge or the side rib in the low-pressure channel with the side wall 3 and the partition 8 is shown in perspective in section.
  • the representation of the ribs 7 in FIGS. 5a, 5b, 6a and 6b correspond to ribs from the area of the fluid flowing under low pressure.
  • the rib capitals 14 are shown as a transition to the partition wall 8 analogously to the illustrations in FIGS. 5a and 5b.
  • FIGS. 7a and 7b pressure ribs with a gap 10 and in FIGS. 8a and 8b edge ribs at the transition into the side wall 3 are shown.
  • the ribs 7 each merge into the rib capital 14 which merges into the partition 8.
  • the ribs 7 are shown as rib columns which extend vertically from the horizontal delimitation plates 2 in the manner of a column and penetrate several partition walls 8. Between the partition walls 8, channels are formed as flow channels 6, in which the heat-transferring fluid flows alternately under high pressure and low pressure.
  • the flow channels 6 with a greater distance between the partition walls 8 are for the higher volume flow at low pressure and the flow channels 6 with a smaller distance between the partition walls 8 are for the lower volume flow at high pressure.
  • the flow channels 6 along the upper and lower horizontal delimitation plates 2 are dimensioned in half Low pressure ducts.
  • FIG. 10 shows a section from a plate-fin heat exchanger 1, an upper horizontal delimitation plate 2 and a side wall 3 being shown.
  • the ribs 7 are shown in different planes once as a front row of ribs 17 in a row in section and in between as a rear row of ribs 18 in the side view.
  • the surface of the ribs 7 in FIG. 10 is enlarged by secondary ribs 19a, 19b, 19c and 19d.
  • partition walls 8 are provided between which the flow channels 6 are formed.
  • rib capitals 14 are formed which connect the ribs 7 to the horizontal delimitation plate 2.
  • All horizontal or essentially horizontal surfaces are designed on their underside at a manufacturing angle (alpha) ⁇ of preferably 45 ° inclination with respect to the vertical for manufacturing reasons. This applies, for example, to the partition walls 8, the secondary ribs 19 and the rib capitals 14.
  • the boundary plates 2 and the side walls 3 are divided into two parts. These preferably consist of an inner layer 20 made of the same highly thermally conductive material as the ribs 7 and an outer layer 21 made from poorly thermally conductive material, the latter outer layer 21 being the Reduced longitudinal heat conduction and insulated the plate-fin heat exchanger 1 to the outside.

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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)

Abstract

L'invention concerne un échangeur de chaleur (1) à plaques et à nervures comprenant une plaque de recouvrement et une plaque de fond en tant que plaques de délimitation horizontales (2) et des parois latérales (3) ainsi qu'un ensemble de plusieurs nervures (7) disposées de manière perpendiculaire par rapport à la direction d'écoulement (9), qui s'étendent de manière perpendiculaire et en forme de barre entre les plaques de délimitation horizontales (2). Au moins une paroi de séparation (8) est réalisée entre les plaques de délimitation horizontales (2) en tant que plaque, qui est traversée par les nervures (7) et qui réalise au moins deux canaux d'écoulement (6) pouvant être traversés par des flux de fluide, qui sont séparés matériellement par la paroi de séparation (8). Les nervures (7) présentent dans la direction d'écoulement (9) une profondeur (a) de nervure et une largeur (b) de nervure. Plusieurs nervures (7) sont disposées en une rangée de nervures de manière transversale par rapport à la direction d'écoulement (9), et plusieurs rangées de nervures sont disposées dans la direction d'écoulement (9) à une distance de rangées adjacentes (c) les unes derrière les autres, et les nervures (7) de rangées de nervures adjacentes sont disposées de manière décalée les unes par rapport aux autres de telle manière que les sections transversales des nervures (7) se chevauchent dans la direction d'écoulement (9) et une fente (10) pouvant être traversée par du fluide, présentant une largeur de fente (e) est réalisée entre des nervures (7) adjacentes.
PCT/DE2020/100286 2019-04-18 2020-04-08 Échangeur de chaleur à plaques et à nervures WO2020211903A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019110262.6 2019-04-18
DE102019110262.6A DE102019110262A1 (de) 2019-04-18 2019-04-18 Platten-Rippen-Wärmeübertrager

Publications (1)

Publication Number Publication Date
WO2020211903A1 true WO2020211903A1 (fr) 2020-10-22

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Application Number Title Priority Date Filing Date
PCT/DE2020/100286 WO2020211903A1 (fr) 2019-04-18 2020-04-08 Échangeur de chaleur à plaques et à nervures

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DE (1) DE102019110262A1 (fr)
WO (1) WO2020211903A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB468980A (en) 1936-03-16 1937-07-16 Harold Livsey Improvements in or connected with tubular feed water heaters and like heat exchangers
DE4234006A1 (de) 1992-10-09 1994-04-14 Mtu Muenchen Gmbh Profilrohr für Wärmetauscher
US20080066888A1 (en) * 2006-09-08 2008-03-20 Danaher Motion Stockholm Ab Heat sink
US20130020063A1 (en) * 2011-07-22 2013-01-24 8 Rivers Capital, Llc Heat exchanger comprising one or more plate assemblies with a plurality of interconnected channels and related method
US20160059437A1 (en) * 2014-08-29 2016-03-03 General Electric Company Article and process for producing an article
CN105547019A (zh) * 2015-12-15 2016-05-04 西安交通大学 一种非均匀分布肋片的高温高压板式换热器
US20180051943A1 (en) * 2016-08-22 2018-02-22 The Boeing Company Methods and apparatus to generate oscillating fluid flows in heat exchangers

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Publication number Priority date Publication date Assignee Title
GB783521A (en) * 1954-04-29 1957-09-25 Power Jets Res & Dev Ltd Heat-transfer wall structures
GB1233038A (fr) * 1968-04-03 1971-05-26
CH641893A5 (en) * 1977-06-09 1984-03-15 Ae Plc Heat exchanger element, method for producing it, and a heat exchanger
WO2005033607A1 (fr) * 2003-10-02 2005-04-14 Hiflux Limited Echangeur thermique et utilisation dudit echangeur
JP6262422B2 (ja) * 2012-10-02 2018-01-17 昭和電工株式会社 冷却装置および半導体装置
DE102013205244A1 (de) * 2013-03-25 2014-09-25 Mahle International Gmbh Verwendung eines additiven Herstellungsverfahrens zur Herstellung eines Bauteils für ein Kraftfahrzeug
DE102015203472A1 (de) * 2015-02-26 2016-09-01 Mahle International Gmbh Wärmetauscher, insbesondere für ein Kraftfahrzeug

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB468980A (en) 1936-03-16 1937-07-16 Harold Livsey Improvements in or connected with tubular feed water heaters and like heat exchangers
DE4234006A1 (de) 1992-10-09 1994-04-14 Mtu Muenchen Gmbh Profilrohr für Wärmetauscher
US20080066888A1 (en) * 2006-09-08 2008-03-20 Danaher Motion Stockholm Ab Heat sink
US20130020063A1 (en) * 2011-07-22 2013-01-24 8 Rivers Capital, Llc Heat exchanger comprising one or more plate assemblies with a plurality of interconnected channels and related method
US20160059437A1 (en) * 2014-08-29 2016-03-03 General Electric Company Article and process for producing an article
CN105547019A (zh) * 2015-12-15 2016-05-04 西安交通大学 一种非均匀分布肋片的高温高压板式换热器
US20180051943A1 (en) * 2016-08-22 2018-02-22 The Boeing Company Methods and apparatus to generate oscillating fluid flows in heat exchangers

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