WO2012000767A2 - Wärmeübertragerplatte, damit versehener plattenwärmeübertrager und verfahren zum herstellen eines plattenwärmeübertragers - Google Patents
Wärmeübertragerplatte, damit versehener plattenwärmeübertrager und verfahren zum herstellen eines plattenwärmeübertragers Download PDFInfo
- Publication number
- WO2012000767A2 WO2012000767A2 PCT/EP2011/059638 EP2011059638W WO2012000767A2 WO 2012000767 A2 WO2012000767 A2 WO 2012000767A2 EP 2011059638 W EP2011059638 W EP 2011059638W WO 2012000767 A2 WO2012000767 A2 WO 2012000767A2
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- WIPO (PCT)
- Prior art keywords
- channel
- heat exchanger
- plate
- flow
- flow channel
- Prior art date
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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
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
- B23P15/00—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass
- B23P15/26—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass heat exchangers or the like
-
- 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
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/04—Constructions of heat-exchange apparatus characterised by the selection of particular materials of ceramic; of concrete; of natural stone
-
- 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
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- 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
- F28F3/10—Arrangements for sealing the margins
-
- 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
- F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/4935—Heat exchanger or boiler making
Definitions
- Heat exchanger plate thus provided plate heat exchanger and method for producing a plate heat exchanger
- the present invention relates to a heat exchanger plate, a plate heat exchanger provided therewith and a method for producing a plate heat exchanger.
- the present invention also relates to a plate heat exchanger with ceramic plates.
- so-called plate heat exchangers or plate heat exchangers are often used in which the heat transfer area between the two media is formed a stapeiförmigen arrangement of so-called heat exchanger plates or heat exchanger plates which lie in the manner of a package to each other or one above the other, with directly adjacent heat exchanger plates form a flow space between them, directly adjacent flow spaces are separated from each other fluidly and each associated with one of the two media.
- heat exchanger plates or heat exchanger plates which lie in the manner of a package to each other or one above the other, with directly adjacent heat exchanger plates form a flow space between them, directly adjacent flow spaces are separated from each other fluidly and each associated with one of the two media.
- heat transfer takes place via the respective flow chambers limiting and separating heat transfer plates, which thus serve as boundary walls of the flow spaces and are sealed against each other by providing appropriate seals.
- Known heat exchanger plates are formed, for example, metallic, so that their arrangement can be welded or soldered from a plurality of heat exchanger plates, so that the solder seam or weld simultaneously acts as a seal.
- the invention is based on the object to provide a heat exchanger plate for a plate heat exchanger, a plate heat exchanger itself and a method for producing a heat exchanger plate, in which with a particularly high reliability and mechanical stability in a particularly effective manner heat transfer can be realized.
- the object of the invention is based on a heat exchanger plate for a plate heat exchanger according to the invention with the features of independent claim 1, in a plate heat exchanger according to the invention with the features of independent claim 1 7 and in a method for producing a heat exchanger plate for a plate heat exchanger according to the invention with the features of independent claim 18 solved.
- Advantageous developments are the subject matter of the dependent claims.
- One aspect of the present invention is therefore to provide a ceramic material and in particular a SiC material or a silicon carbide material as a material for the heat exchanger plate for a plate heat exchanger instead of a metal material which is normally provided.
- Another aspect of the present invention is to ensure the mechanical stability of the heat exchanger plate in such a choice of materials that some or all of the intended flow channels of the flow channel arrangement partially or completely channel webs that form completely or partially channel channels delimiting channel walls.
- channel lands stabilize the flow channels of the flow channel assembly and thus the plate substrate as a whole in a mechanical manner, particularly when in use and installation in a plate heat exchanger they interact with other heat transfer plates and substantially support a given heat transfer plate on a directly adjacent heat transfer plate allow planar manner, so that imprinted by the flowing media impressions can not lead to plate breaks in the underlying ceramic material.
- the plate substrate and thus the heat transfer plate can have any desired shapes and dimensions, so that in particular an overall height and a total width of the plate substrate and thus of the heat transfer plate according to the invention are not limited.
- a minimum channel depth can be predetermined, e.g. also in the range of about 0.2 mm in so-called micro-heat exchangers or micro-heat exchangers.
- a deflection of the heat transfer medium or fluids can be realized, e.g. also in the sense of a plate heat exchanger with multiple passage and / or with multiple deflection of the heat transfer fluid or fluids.
- the plate substrate may be formed with or from a sintered silicon carbide material or SSiC material. This choice of material has the particular advantage of further mechanical stabilization and increased chemical inertness.
- It may be a minimum layer thickness Dmin and / or a mean layer thickness Dm of the disc substrate in the range of about 2 mm to about 4 mm, in particular about 3 mm or less, preferably about 2 mm. Due to the formed channel webs, it is possible to reduce the layer thicknesses of the heat transfer plates accordingly, without causing mechanical destabilization. Without the mechanical stabilization by providing the corresponding webs of the flow channels much higher layer thicknesses for stabilization of the heat exchanger plates would be necessary if they were made of ceramic materials. This would result in a weight and volume increase, so that with the same heat transfer larger equipment needed and higher costs would be the result.
- the layer thickness Ds of the plate substrate may be greater than the minimum layer thickness Dmin of the plate substrate in the region of a channel web and / or as the average layer thickness Dm of the disk substrate, such that the relationship
- a local width Bb of the bottom of the channel groove of the flow channel and the local width Bsb of a base of the channel web of the flow channel at the level of the bottom of the channel channel of the flow channel - each measured perpendicular to the local course direction of the channel - can have a ratio Bb: Bsb of approximately 1: 4, so that's about the relationship
- the local width Bb of the bottom of the channel channels of the flow channel and the local width Bsp of a plateau of a channel web of a flow channel on the side facing away from the bottom of the channel channel of the flow channel - each measured perpendicular to the local course direction of the flow channel - a ratio Bb: Bsp in the range of have about 1 0: 3, so about the relationship
- the local width Bsb of the base of the channel web of the flow channel at the level of the bottom of the channel channel of the flow channel and the local width Bsp of the plateau of the channel web of the flow channel on the side remote from the bottom of the channel channel of the flow channel - each measured perpendicular to the local direction of the flow channel have a ratio Bsb: Bsp in the range of about 1: 1 to about 4: 2, preferably about 4: 3, so that about the relationship
- the channel walls of a flow channel with the normal to the bottom of the channel groove of the flow channel include an angle ⁇ which is in the range of more than 0 ° and less than 30 °, preferably about 1 5 °, so that about the relationship
- the local width Bb of the bottom of the channel channel of the flow channel - measured perpendicular to the local direction of the flow channel - and the depth t of the channel channel of the flow channel - measured perpendicular to the bottom of the channel channel of the flow channel - a ratio Bb: t in the range of about 10: 1 0th to about 10: 4, preferably about 10: 4, so that about the relationship
- the sheet substrate may be provided with top and bottom penetrating supply and discharge ports for supplying a first heat transfer fluid F1 to and from the top of the disk substrate, the flow channel assembly configured to transport the first heat transfer fluid F1 from the supply port to the discharge port ,
- Flow channels of the flow channel arrangement can have completely or in sections a multiple undulated course.
- the undulation direction U can run in a surface or plane defined by the plate substrate and / or perpendicular to the flow direction locally and / or in the middle defined by the respective flow channel.
- the shape of the undulation of a respective flow channel may be one of a group of shapes including sawtooth shapes, alternating step shapes, waveforms, sine shapes, and combinations thereof.
- a second flow channel arrangement for a second heat transfer fluid F2 having a plurality of corresponding flow channels.
- the plate substrate may be provided with top and bottom penetrating second supply and discharge ports for supplying the second heat transfer fluid F2 to and from the back or bottom of the disc substrate, and the second flow channel assembly for transporting the second heat transfer fluid F2 from the second Feed opening is formed to the second discharge opening.
- the heat exchanger plate according to the invention may be rotationally symmetrical with respect to the front or top side and the back or bottom side by 180 ° with respect to an axis of symmetry S. extending in the plate substrate.
- the plate substrate may have a substantially rectangular shape.
- supply and / or discharge openings can be formed in the area at opposite first, preferably shorter, sides of the rectangular shape, in particular in regions of the corners.
- first and / or second heat transfer fluids F1, F2 and / or main directions of flow of flow channels can be essentially along the extension directions of opposite second - preferably longer - sides of the rectangular shape may be formed.
- a plate heat exchanger as such having a plurality of heat transfer plates according to the invention, the heat transfer plates being constructed and arranged so that the back or bottom of the plate substrate is a respective preceding heat transfer plate.
- a method of manufacturing a heat transfer plate for a plate heat exchanger comprising the steps of providing or forming a plate substrate with or made of a ceramic, SiC material or a silicon carbide material having a front or top surface and a return or terseite, forming a flow channel arrangement having a plurality of flow channels on the front or top of the disk substrate, wherein a part or all of the flow channels of the flow channel arrangement are formed completely or in sections with channel channels defining channel walls forming channel webs.
- the plate substrate may be formed with or from a sintered silicon carbide material or SSiC material.
- Flow channels of the flow channel arrangement can be formed completely or in sections with a multiple undulated course.
- the undulation direction U can be formed to extend in a surface or plane defined by the plate substrate and / or perpendicular to the flow direction locally or in the middle defined flow direction.
- the shape of the undulation may be a shape of the group of shapes including sawtooth shapes, alternating step shapes, waveforms, sine shapes, and combinations thereof.
- Fig. 1A is a schematic plan view of the front side of an embodiment of the heat exchanger plate according to the invention.
- FIG. 1 B shows a schematic plan view of the back side of FIG. 1 illustrated embodiment of the heat exchanger plate according to the invention.
- FIGS. 1 and 2 another embodiment of the heat exchanger plate according to the invention, in which the Hauptfl warekanäle have a different geometry.
- Embodiments of inventive heat transfer plates which are similar to those of FIGS. 1 A and 2A are constructed, but wherein the channel webs of the feed channels have a different geometry.
- the present invention also relates to a plate heat exchanger 100 or plate heat exchanger 100 with a plurality of heat exchanger plates 1 according to the invention.
- ceramic materials for the design of the heat exchanger plates 1 according to the invention are provided.
- channel webs 20s which inherently stabilize the structure of the heat exchanger plate 1 made of a ceramic material and in particular of a SiC or SSiC material, and in particular also by supporting an arrangement of a plurality of inventive heat exchanger plates 1 in a plate heat exchanger 1 00 serve each other.
- Fig. 1 shows a schematic plan view of a first embodiment of the heat exchanger plate 1 or heat exchanger plate 1 according to the invention.
- This consists essentially of a plate substrate 1 0, which is also referred to simply as the substrate 1 0 for the heat exchanger plate 1 and with or at least one ceramic material 1 0 ', preferably a SiC material or Siliziumcarbidmaterial 1 0' and more preferably with or is formed of at least one sintered silicon carbide 1 0 'or SSiC material 1 0'.
- the substrate 1 0 for the heat exchanger plate 1 has a plate structure with a front or top 1 0o and a back or bottom 1 0u; however, these may be particularly equal, especially with respect to a particular application, and they may also be structured in a similar or even identical manner.
- a feed opening 2 for a first fluid F1 a discharge opening 3 for the first fluid F1
- a feed opening 2 'for a second fluid F2 a discharge opening 3 for the second fluid F2.
- All openings 2, 2 ', 3, 3' are formed at the edge or corner regions of the disk substrate 1 0.
- the feed opening 2 for the first fluid F1 is shown in the view of FIG. 1 A formed in the upper, left corner.
- the discharge opening 3 for the first fluid F1 is formed in the lower left corner. However, it may also be the discharge opening 3 for the first fluid F1 of the feed opening 2 for the first fluid F1 are formed diagonally opposite one another, ie in the in FIG. 1 A given view in the lower right corner.
- the supply opening 2 'for the second fluid F2 is formed in the region of the upper, right-hand corner, while the discharge opening 3' for the second fluid F2 is formed in the region of the lower, right-hand corner.
- the discharge opening 3 'for the second fluid may also be formed diagonally opposite the feed opening 2' for the second fluid, that is to say in the embodiment shown in FIG. 1 A view in the lower left corner.
- the respective supply openings and discharge openings for a respective fluid are in relation to the longitudinal orientation of the disk substrate 1 0 each opposite. In the in Fig. Moreover, they are both arranged on the left side or on the right side of the disk substrate 10 with respect to the short edge k, respectively.
- the feed opening 2 and the discharge opening 3 for the first fluid are surrounded or framed on the upper side 10a of the disk substrate 10 by a main seal 6 for the front side 10o and for the first fluid F1, so that outside the main seal 6 for the upper side 1 0o the supply port 2 'and the discharge opening 3' for the second fluid F2 lie.
- an arrangement 20 for flow channels 20k is provided next to the feed opening 2 and the discharge opening 3 for the first fluid F1, which is also referred to as channel arrangement 20 or flow channel arrangement 20.
- the plurality of flow channels 20k provided in this channel arrangement 20 extend on the surface or upper side 10o of the substrate 10, namely, the individual channels 20k in a plurality of reliefs on the upper side 10o of the plate substrate 10 within the main seal 6 for the upper side 10o form.
- the channels 20k extend substantially between the feed opening 2 and the discharge opening 3 for the first fluid F1.
- the entire channel assembly 20 is divided into a main channel assembly 21 or main heat transfer channel assembly 21, which is located in the middle between the supply port 2 and the discharge opening 3 for the first fluid and a little spaced therefrom and of main channels 21 k or main heat transfer channels 21 k is formed.
- a feed or distribution channel arrangement 22 Directly adjacent to the feed opening 2 and to the discharge opening 3 for the first fluid F1 and directly connected to and / or adjacent to the main channel arrangement 21 are a feed or distribution channel arrangement 22 with distribution channels 22k or distribution channels 22k or a bundling, merging or discharge channel arrangement 23 with a plurality of bundling, merging, or discharge channels 23k.
- Inn operation is supplied via the supply port 2, the first fluid F1 and practically introduced to the top 10 of the disk substrate 1 0 and distributed there. The distribution is taken over by the distribution channels 22k of the feed and distribution channel arrangement 22 adjoining the feed opening 2 for the first fluid F1.
- the distribution channels 22k of the supply and distribution channel arrangement 22 transfer the first fluid F1 into the main channels 21k or main heat transfer channels 21k of the main channel arrangement 21 or main heat transfer channel arrangement 21.
- the main channels 21 k and the main channel arrangement 21 are formed comparatively longer than the supply and distribution channel arrangement 22, so that there is a longer residence time of flowing in the channels 20 k first fluid F1 and thus sets a stronger heat transfer to the plate substrate 1 0.
- the main channels 21 k then lead into the so-called bundling channels 23 k, which can also be referred to as discharge channels 23 k or 23k merging channels and receive the first fluid F1 from the main channels 21 k and the discharge opening 3 for the first fluid F1 supply, through which then the first fluid F1 after flowing through the channels 20k of the entire channel assembly 20, starting from the feed opening 2 for the first fluid F1, the channel assembly 20 and thus the top 10o of the substrate 1 0 leaves the heat exchanger plate 1 according to the invention again.
- bundling channels 23 k which can also be referred to as discharge channels 23 k or 23k merging channels and receive the first fluid F1 from the main channels 21 k and the discharge opening 3 for the first fluid F1 supply, through which then the first fluid F1 after flowing through the channels 20k of the entire channel assembly 20, starting from the feed opening 2 for the first fluid F1, the channel assembly 20 and thus the top 10o of the substrate 1 0 leaves the heat exchanger plate 1 according to the invention again.
- the first fluid F1 when flowing from the feed opening 2 to the discharge opening 3, reaches the outside area outside the main seal 6 and thus the areas of the feed opening 2 'and the discharge opening 3' for the first second fl uid F2 not.
- the feed opening 2 'and the discharge opening 3' for the second fluid on first and two side seals 4-1 and 4-2, which the feed opening 2 'and the discharge opening 3' for the second fluid F2 for themselves once again by closing the feed opening 2 'and the lead opening 3 'for the second fluid F2 in the edge region surrounded from the outside.
- the feed opening 2 and the discharge opening 3 for the first fluid F1 and the feed opening 2 'and the discharge opening 3' for the second fluid F2 are fluidly separated from each other or isolated, so that the first and the second fluid F1 or Do not mix F2 on top 1 0o of the plate substrate 1 0.
- the main channel arrangement 21 or main heat transfer channel arrangement 21 with its main channels 21 k or main heat transfer channels 21 k forms the main heat transfer area or main heat exchange area 9 on the upper side 10o of the plate substrate 10 or of the first fluid F1 of the heat transfer plate 1 according to the invention.
- the discharge opening 3 for the first fluid F1 and the bundling and discharge channel arrangement with their bundling channels 23k, merging channels 23k or discharge channels 23k form the so-called bundling and discharge region 8 for the front side 10o of the plate substrate 10 of the heat transfer plate according to the invention 1 or the first fluid.
- the arrangement shown in plan view of FIG. 1 A is strictly axisymmetric with respect to the indicated symmetry axis x.
- the symmetry axis y which is also drawn, at least the feed opening 2 for the first fluid F1 and the discharge opening 3 'for the second fluid F2 on the one hand and the discharge opening 3 for the first fluid F1 and the supply opening 2' for the second fluid F2 are strictly axially symmetrical arranged.
- the outer shape of the substrate 10 is strictly axially symmetrical with respect to both axes x and y and has substantially the shape of one in the length drawn rectangles with rounded corners and an aspect ratio for the long edge I and the short edge k in the range of about 2: 1.
- the feed channels 22k or distribution channels 22k directly transition into the main channels 21k in a 1-to-1 arrangement or assignment, and these in turn in a 1-to-1 arrangement into the trunking channels 23k or discharge channels 23k.
- the channel cavities 20r or channel grooves 20r are shown white or light, whereas the channel lands 20s forming the channel walls 20w are shown in black or dark.
- the channels 20k in total are in the arrangement of FIG. 1 A thus formed by a respective feed channel 22k, a directly associated main channel 21k and a directly associated discharge channel 23k.
- the main channels 21 k here have the shape of a sawtooth or a zigzag line with triangular basic pattern. However, other embodiments are also conceivable.
- the mechanical stability of the sheet-like substrate 1 0, which is formed in a planar manner, is stabilized per se by the sequence of depression or groove 20r and web 20s per se.
- the Fig. 1B shows from the direction of view from the upper side 110o of the substrate 110 from the arrangement of FIG. 1 A from - quasi in review - the structure of the back 1 0u or bottom 10u of the same substrate 1 0. All structures are therefore shown dotted or dashed lines.
- the arrangement of the here provided main seal 6 'for the second fluid F2 for the back 1 0u and the first and second side seals 4-1' and 4-2 'for the supply port 2 and for the discharge opening 3 for the first fluid F1 in relation on the back 10u is strictly axis or mirror symmetry to the axis of symmetry x and appears in comparison to the in Fig. 1 A shown corresponding arrangement with respect to the main seal 6 for the first fluid F1 and the secondary seals 4-1 and 4-2 for the second fluid with respect to the front 1 0o to the symmetry axis y strictly axis or mirror symmetry.
- the main seal 6 surrounds the supply port 2' and the second fluid discharge port 3 ', fluidically outwardly separates the supply port 2 and the first fluid discharge port 3 with the corresponding first and second side seals 4-1' and 4-2 'and has in its interior the channel arrangement 20' or flow channel arrangement 20 'for the second fluid F2 on the back 1 0u of the plate substrate 1 0 of the heat exchanger plate 1 according to the invention.
- FIG. 1B for the rear side 10u or lower side 10u of the disk substrate 10 essentially the one for the front side 10o of the disk substrate 10, which is shown in FIG. 1 A is shown.
- a supply portion 7 'or distribution portion 7', a bundling portion 8 'or discharge portion 8' and a main heat transfer portion 9 'or main heat exchange portion 9' are formed for the back 10u or second fluid F2 by cooperation of the supply port 2 'for the second fluid F2 and the supply channel arrangement 22 'or distribution channel arrangement 22' with the supply channels 22k 'or distribution channels 22k' for the second fluid F2, through the main channel arrangement 21 'or main heat transfer channel arrangement 21' with the main channels 21k 'or main heat transfer channels 21k' for the second fluid F2 or by cooperation of the discharge opening 3 'for the second fluid F2 with the bundling channel arrangement 23',
- Reca supply portion 7 'or distribution portion 7', a bundling portion 8 'or discharge portion 8' and a main heat transfer portion 9 'or main heat exchange portion 9' are formed for the back 10u or second fluid F2 by cooperation of the supply port 2 'for the second fluid F2 and the supply channel arrangement 22 'or distribution channel arrangement
- FIGS. 2A and 2B arrangements correspond to those of FIGS. 1 A and 1 B, except that in Figs. 1 A and 1 B the main channels 21 k for the first fluid F1 and 21 k 'for the second fluid F2 and the respective webs 20s, 20s' have a sawtooth shape or a zigzag shape, whereas in the embodiment according to FIGS. 2A and 2B is a waveform, in particular in the manner of a sinusoidal course.
- the undulation itself leads in each case to a longer dwell time of the fluid F1, F2 flowing or flowing in the channel 20k, 20k 'and thus to a more intimate heat exchange with the material 10' of the substrate 10.
- FIGS. 3 and 4 show plan views of upper sides 10o of substrates 10 of two other embodiments for the heat exchanger plate 1 according to the invention.
- the main channels 21k, 21k 'of the channels 20k, 20k' essentially correspond in their structure to the channels of the arrangements of FIGS. 1A, B on the one hand and FIGS. 2A, B on the other hand, ie. they have a sawtooth, a waveform.
- FIG. 3 and 4 In contrast to the arrangements of FIG. 1A to 2B show the arrangements of FIG. 3 and 4 supply channels 22k, 22k 'and discharge channels 23k, 23k', which are no longer in 1-to-1 correspondence with the main channels 21k, 21k '. Rather, here are the channel webs 20s, 20s' - in particular 22s, 22s', 23s, 23s' - formed greatly widened, so that a total of the number of feed channels 22k, 22k 'and the discharge channels 23k, 23k' is less than the number of main channels 21 k, 21 k '.
- FIGS. 5 and 6 show partial sectional views through a substrate 10 of two embodiments of the heat exchanger plate 1 according to the invention, namely, when the arrangements of FIGS. 1 A to 4 - viewed in the direction Y
- the respective channel groove 20r, 20r 'and the respective channel web 20s, 20s' of the respective channel 20k, 20k' have approximately a rectangular or square shape and are substantially equal to one another.
- the webs or channel webs 20s, 20s ' having a height which forms the depth t of the channel channel 20r, 20r', which corresponds to the width Bb of the bottom 20b, 20b 'the channel groove 20r of the flow channel 20k, 20k' but also the width Bsb of the channel web 20s, 20s 'at the level of the bottom 20b, 20b' and also the local width Bsp of the plateau 20sp, 20sp 'of the web 20s, 20s' corresponds.
- the channel walls 20W, 20W' are formed vertically.
- the base of the channel web 20s, 20s' and the plateaus 20sp, 20sp 'of the channel webs 20s, 20s' such chosen that the channel webs 20s, 20s' to the channel bottom 20b, 20b 'side facing away from a tapered course results, wherein the inclination angle ⁇ of the respective channel wall 20w, 20w' is different from 0 °, it is therefore: Bsb> Ex.
- the arrows indicate the flow conditions with respect to the outward and return flow, that is to say from inflow and outflow.
- the respective seals 6, 4-1, 4-2 and the various channel arrangements 20, 20 ' are not indicated in this illustration.
- FIGS. 8A to 8D show, in sectional side and plan views, the schematic arrangement shown in the arrangement 100 'of FIG. 7 present flow conditions with respect to the first and second fluids F1 and F2.
- first and second secondary seals 4-1, 4-2, 4-1 ', 4-2' for the first and second fluids F1, F2 are shown.
- FIG. 8A to 8D are not to scale here because the main seals 6, 6 'and the side seals 4-1, 4-2, 4-1', 4-2 'are designed too strong in strength; However, this serves to clarify the geometric and flow conditions.
- Fig. 10A and 10B describe another embodiment of the heat exchanger plate 1 according to the invention with or consisting of a ceramic substrate 10.
- the heat exchanger plate 1 also has a substantially rectangular configuration, but with an edge ratio of the long and short edges I and k of about 4: 1. Otherwise, in connection with FIGS. 2A, 2B and 4 and 6 described before. That is, the actual main heat transfer channels 21k, 21k 'are approximately undulating, with no 1-to-1 correspondence or allocation between the supply and discharge channels 22k, 22k', 23k, 23k 'on the one hand and the main heat transfer channels 21 k, 21 k 'is present and that the webs 20s, 20s' - in particular 22s, 22s ', 23s, 23s' - the underlying flow channels 20k, 20k 'in cross-section have a trapezoidal shape, with the respective channel bottom 20b, 20b' facing away from tapering Course.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Ceramic Engineering (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
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Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2803972A CA2803972C (en) | 2010-06-30 | 2011-06-09 | Heat exchanger plate, plate heat exchanger provided therewith, and method for manufacturing a plate heat exchanger |
KR1020137002396A KR20130056279A (ko) | 2010-06-30 | 2011-06-09 | 열 교환기 플레이트, 이를 구비하는 플레이트 열 교환기 및 플레이트 열 교환기를 제조하는 방법 |
JP2013517147A JP2013534608A (ja) | 2010-06-30 | 2011-06-09 | 熱伝達板、これを備えた平板式熱伝達器および平板式熱伝達器の製造方法 |
BR112012033628A BR112012033628A2 (pt) | 2010-06-30 | 2011-06-09 | placa trocadora de calor, trocador de calor de placa dotado da mesma e método para fabricar um trocador de calor de placa |
CN2011800327770A CN103026164A (zh) | 2010-06-30 | 2011-06-09 | 热交换器板、具有热交换器板的板式热交换器以及用于制造板式热交换器的方法 |
EP11728796.1A EP2588827A2 (de) | 2010-06-30 | 2011-06-09 | Wärmeübertragerplatte, damit versehener plattenwärmeübertrager und verfahren zum herstellen eines plattenwärmeübertragers |
US13/731,299 US20130327513A1 (en) | 2010-06-30 | 2012-12-31 | Heat exchanger plate, plate heat exchanger provided therewith and method for manufacturing a heat exchanger plate |
Applications Claiming Priority (2)
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DE102010030781A DE102010030781A1 (de) | 2010-06-30 | 2010-06-30 | Wärmeübertragerplatte, damit versehener Plattenwärmeübertrager und Verfahren zum Herstellen eines Plattenwärmeübertragers |
DE102010030781.5 | 2010-06-30 |
Related Child Applications (1)
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US13/731,299 Continuation US20130327513A1 (en) | 2010-06-30 | 2012-12-31 | Heat exchanger plate, plate heat exchanger provided therewith and method for manufacturing a heat exchanger plate |
Publications (2)
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WO2012000767A2 true WO2012000767A2 (de) | 2012-01-05 |
WO2012000767A3 WO2012000767A3 (de) | 2012-04-19 |
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PCT/EP2011/059638 WO2012000767A2 (de) | 2010-06-30 | 2011-06-09 | Wärmeübertragerplatte, damit versehener plattenwärmeübertrager und verfahren zum herstellen eines plattenwärmeübertragers |
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US (1) | US20130327513A1 (de) |
EP (1) | EP2588827A2 (de) |
JP (1) | JP2013534608A (de) |
KR (1) | KR20130056279A (de) |
CN (1) | CN103026164A (de) |
BR (1) | BR112012033628A2 (de) |
CA (1) | CA2803972C (de) |
DE (1) | DE102010030781A1 (de) |
WO (1) | WO2012000767A2 (de) |
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WO2012166750A1 (en) * | 2011-06-01 | 2012-12-06 | Alstom Technology Ltd | Heating element undulation patterns |
US10094626B2 (en) | 2015-10-07 | 2018-10-09 | Arvos Ljungstrom Llc | Alternating notch configuration for spacing heat transfer sheets |
US10175006B2 (en) | 2013-11-25 | 2019-01-08 | Arvos Ljungstrom Llc | Heat transfer elements for a closed channel rotary regenerative air preheater |
US10197337B2 (en) | 2009-05-08 | 2019-02-05 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
US10378829B2 (en) | 2012-08-23 | 2019-08-13 | Arvos Ljungstrom Llc | Heat transfer assembly for rotary regenerative preheater |
US10914527B2 (en) | 2006-01-23 | 2021-02-09 | Arvos Gmbh | Tube bundle heat exchanger |
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JP6363485B2 (ja) * | 2014-12-03 | 2018-07-25 | 京セラ株式会社 | セラミック流路体およびこれを備える熱交換器 |
CA2978795A1 (en) * | 2015-03-16 | 2016-09-22 | Dana Canada Corporation | Heat exchangers with plates having surface patterns for enhancing flatness and methods for manufacturing same |
JP2016221461A (ja) * | 2015-06-01 | 2016-12-28 | 東京理化器械株式会社 | 理化学実験用コンデンサー |
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CN106001662B (zh) * | 2016-06-28 | 2017-12-05 | 洛阳红奇机械科技有限公司 | 一种大板热压机一体式水套加热板的制造工艺 |
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DE102016218370A1 (de) | 2016-09-23 | 2018-03-29 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Wärmeübertragervorrichtung und Verfahren zur Herstellung einer Wärmeübertragervorrichtung |
CN106802104B (zh) * | 2017-01-13 | 2024-03-26 | 江门市东联热工设备有限公司 | 换热器波纹板 |
AT520072B1 (de) * | 2017-07-28 | 2019-01-15 | Zkw Group Gmbh | Kühlkörper und Fahrzeugscheinwerfer |
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US11333448B2 (en) | 2018-09-18 | 2022-05-17 | Doosan Heavy Industries & Construction Co., Ltd. | Printed circuit heat exchanger and heat exchange device including the same |
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JP6881516B2 (ja) | 2019-07-29 | 2021-06-02 | 株式会社富士通ゼネラル | 隔壁式熱交換器 |
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- 2011-06-09 KR KR1020137002396A patent/KR20130056279A/ko active Search and Examination
- 2011-06-09 CN CN2011800327770A patent/CN103026164A/zh active Pending
- 2011-06-09 EP EP11728796.1A patent/EP2588827A2/de not_active Withdrawn
- 2011-06-09 CA CA2803972A patent/CA2803972C/en not_active Expired - Fee Related
- 2011-06-09 WO PCT/EP2011/059638 patent/WO2012000767A2/de active Application Filing
- 2011-06-09 JP JP2013517147A patent/JP2013534608A/ja active Pending
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2012
- 2012-12-31 US US13/731,299 patent/US20130327513A1/en not_active Abandoned
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Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10914527B2 (en) | 2006-01-23 | 2021-02-09 | Arvos Gmbh | Tube bundle heat exchanger |
US10197337B2 (en) | 2009-05-08 | 2019-02-05 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
US10982908B2 (en) | 2009-05-08 | 2021-04-20 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
WO2012166750A1 (en) * | 2011-06-01 | 2012-12-06 | Alstom Technology Ltd | Heating element undulation patterns |
CN103717992A (zh) * | 2011-06-01 | 2014-04-09 | 阿尔斯通技术有限公司 | 加热元件波状图案 |
US9644899B2 (en) | 2011-06-01 | 2017-05-09 | Arvos, Inc. | Heating element undulation patterns |
US10378829B2 (en) | 2012-08-23 | 2019-08-13 | Arvos Ljungstrom Llc | Heat transfer assembly for rotary regenerative preheater |
US11092387B2 (en) | 2012-08-23 | 2021-08-17 | Arvos Ljungstrom Llc | Heat transfer assembly for rotary regenerative preheater |
US10175006B2 (en) | 2013-11-25 | 2019-01-08 | Arvos Ljungstrom Llc | Heat transfer elements for a closed channel rotary regenerative air preheater |
US10094626B2 (en) | 2015-10-07 | 2018-10-09 | Arvos Ljungstrom Llc | Alternating notch configuration for spacing heat transfer sheets |
Also Published As
Publication number | Publication date |
---|---|
CN103026164A (zh) | 2013-04-03 |
CA2803972C (en) | 2015-05-12 |
WO2012000767A3 (de) | 2012-04-19 |
BR112012033628A2 (pt) | 2016-11-22 |
DE102010030781A1 (de) | 2012-01-05 |
KR20130056279A (ko) | 2013-05-29 |
US20130327513A1 (en) | 2013-12-12 |
JP2013534608A (ja) | 2013-09-05 |
CA2803972A1 (en) | 2012-01-05 |
EP2588827A2 (de) | 2013-05-08 |
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