US20130277024A1 - Plate Heat Exchanger - Google Patents
Plate Heat Exchanger Download PDFInfo
- Publication number
- US20130277024A1 US20130277024A1 US13/620,790 US201213620790A US2013277024A1 US 20130277024 A1 US20130277024 A1 US 20130277024A1 US 201213620790 A US201213620790 A US 201213620790A US 2013277024 A1 US2013277024 A1 US 2013277024A1
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- United States
- Prior art keywords
- inflow
- plates
- heat exchanger
- individual
- cross
- 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.)
- Abandoned
Links
- 125000006850 spacer group Chemical group 0.000 claims description 5
- 239000003546 flue gas Substances 0.000 description 9
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- 230000003993 interaction Effects 0.000 description 5
- 239000002245 particle Substances 0.000 description 4
- 239000007787 solid Substances 0.000 description 4
- 238000009826 distribution Methods 0.000 description 3
- 230000035508 accumulation Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000011109 contamination Methods 0.000 description 2
- 238000000151 deposition Methods 0.000 description 2
- 230000008021 deposition Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 230000002195 synergetic effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 239000000356 contaminant Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
Images
Classifications
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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
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
-
- 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
- F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/02—Stamping using rigid devices or tools
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
-
- 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
- F28F3/044—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 pontual, e.g. dimples
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/104—Particular pattern of flow of the heat exchange media with parallel flow
Definitions
- the invention relates to a plate heat exchanger comprising flow channels through which a first and a second flow flows in concurrent or countercurrent flow, which flow channels are formed for the first medium between individual plates joined together to form in each case a pair of plates, and for the second medium between pairs of plates joined together to form a stack of plates, wherein the individual plates and the pairs of plates are connected to each other at longitudinal edges and support surfaces running parallel to the main flow direction, wherein each individual plate comprises inflow and outflow cross-sections arranged diagonally and corresponding in the longitudinal direction for the first medium, and inflow and outflow cross-sections adjacent thereto in the transverse direction for the second medium, wherein the outflow cross-sections for the first medium are in each case offset by half the height of the inflow and/or outflow cross-sections for the second medium, wherein the individual plates within an inlet region comprise guide blades formed by stamped embossments protruding into the flow channel, wherein the guide blades are formed in an arch-shaped manner with an inflow leg aligned substantially
- Plate heat exchangers of this kind are used on a large scale with plate dimensions of several meters.
- a field of application here is the use in incinerators, power plants, chemical plants, refineries and/or the like, in which the resulting combustion heat of the flue gas is used for heating the second medium.
- a plate heat exchanger of the aforementioned kind is disclosed in detail in German patent DE 41 42 177 C2.
- guide blades are provided which distribute the medium flowing in through the inflow cross-section over the full channel width of the flow channel.
- the guide blades are provided with elongated outflow legs which protrude beyond the longitudinal center of the individual plate.
- the guide blades are arranged closer to the inflow cross-section in the longitudinal center of the individual plates than in the direction of the longitudinal edge of the individual plate.
- a plate heat exchanger of the aforementioned kind in which the guide blades of the inflow cross-sections do not protrude beyond the longitudinal center of the individual plates, i.e., the guide blades are formed exclusively in the plate halves associated with the respective inflow cross-sections, wherein the inflow legs and the outflow legs have substantially identical lengths, and wherein the guide blades are arranged at substantially the same distance from the associated transverse edge of the respective individual plate, and wherein, at the same time, the profiling generating the turbulences protrudes in the inlet region of the inflow cross-sections up to the guide blades and is recessed in the region adjoining mirror-symmetrically the longitudinal center of the individual plates.
- the guide blades which, according to the invention, are shorter and arranged steeper relative to the main flow direction and closer to edge, adherence of dirt particles is minimized.
- high performance of the heat exchanger is ensured in that the turbulence-generating profiling of the individual plates protrudes in the inlet region of the inflow cross-section up to the guide blades and is recessed in the plate region located mirror-symmetrically opposite to the longitudinal center. Due to this profile recess in the plate half located next to the inflow cross-section, negative pressure is created with respect to the gas pressure inside the profiled inflow cross-section so that the inflowing flue gases are sucked into the profile-free region.
- the performance of the heat exchanger depends on how homogenously the heating medium is distributed over the width of the countercurrent flow plate.
- measures effecting a uniform distribution generally promote dirt accumulations.
- the invention thus provides a solution which equilibrates the two competing factors in such a manner that, on the one hand, adherence of dirt particles is reduced and, on the other, no performance loss occurs.
- the configuration according to the invention of the guide blades, on the one hand, and the configuration according to the invention of the profiling generating the turbulences, on the other, in combination result in the synergetic effect that equalization of the media flowing into the heat plate takes place over the entire plate width while minimizing at the same time the risk of contamination which, in the worst case, causes clogging of the guide blades.
- the invention deliberately departs from the previous configuration and proposes to downsize the guide blades, in particular with regard to the respective outflow leg.
- the number of guide blades has been significantly reduced.
- the result of the configuration according to the invention is increased efficiency over the prior art with regard to the distribution of the medium, and, at the same time, reduction of the guide-blade-related contact surfaces for dirt particles, foreign substances and/or the like is achieved.
- the plate heat exchanger according to the invention is less prone to contamination or even clogging, so that operational safety is increased and/or the maintenance intervals can be extended.
- a particularly positive effect in this connection has the fact that in contrast to the prior art, the outflow legs of the guide blades according to the invention are formed much steeper and much shorter.
- the guide blades are completely stamped through so that they rest without any gap against the adjacent individual plate.
- the guide blades serve completely as a support or a spacer so that vibrations within the pair of plates and within the plate stack are reduced and thus the structure of the heat exchanger overall becomes more stable.
- the guide blades, which are completely stamped through can rest against the guide blades of adjacent individual plates or against the opposing wall of the flow channels.
- the invention provides that the inflow legs and the outflow legs are arranged at an angle between 140° and 100°, preferably 135° and 112° relative to each other.
- the turbulence-generating profiling on the individual plates comprises stamped knobs.
- Said knobs can be produced in a very simple and cost-effective manner by stamping the individual plates.
- a uniform knob field is perfectly suited for increasing performance of the heat exchanger. Through the turbulent flow, heat transfer is increased and therefore efficiency is improved.
- knobs can be formed as spacers for adjacent individual plates. In this manner, even in the case of small distances between adjacent individual plates, the predefined plate spacing can be ensured over the entire channel length and channel width. Such spacers can also be formed in the region of the guide blades so as to keep the individual plates in the region of the inflow and outflow cross-sections at the predefined distance from each other. Of course, it is also possible that all knobs serve as spacers.
- the invention provides that the turbulence-generating profiling of the individual plate is formed perpendicular to the main flow direction over the entire bottom up to the contact surfaces. Through this profiling, which extends over the entire width of the individual plate up to the lateral edges thereof, a controlled flow pattern is obtained while avoiding bypasses at the same time. In contrast to the prior art, it is therefore avoided that the medium flowing over the individual plate moves into profile-free channels and contributes to the heat exchange only to a minor extent. Overall, the profiling which, in contrast to the prior art, is brought closer to the lateral edge, therefore effects an improvement of the heat flow rate of the heat exchanger.
- the individual plates comprise edge channels with a cross-section that is size-variable over the longitudinal extension of said edge channels.
- edge channels are formed in a labyrinthine manner and are formed in the region of the contact surfaces, i.e., in the edge region of the individual plates, where the heat medium otherwise would seek for a barrier-free and thus interaction-free flow path.
- the edge channels are formed to be substantially S-shaped, i.e., multiple times S-shaped. This results in a staggered blocking embossment on both sides of each edge channel, which embossment leads to increased interaction of the heat medium due to the resulting restrictions and expansions.
- the cross-section of the edge channels can vary up to 50% or more.
- the barrier-free cross-section for the medium is reduced at the restriction by more than half.
- a locally offset flow channel is created which further increases the interaction between medium and heat exchanger.
- the edge channel configuration according to the invention results in the synergetic effect that free flow paths for the medium are basically avoided.
- the media flowing into the plate heat exchanger therefore cannot divert via a bypass-like interaction-free flow-path.
- neither the bottom near the edge region of each individual plate nor the edge channel forming in the edge region between two individual plates represent according to the inventive configuration such a bypass because, according to the invention, the edge channels are formed in a labyrinthine manner and the turbulence-creating profiling extends up into the edge region of each individual plate.
- FIG. 1 shows a perspective view of a plate stack formed from a plurality of individual plates, wherein for a better overview, the guide blades and the profiling are not illustrated.
- FIG. 2 a shows a top view of an individual plate with guide blades and indicated profiling.
- FIG. 2 b shows a perspective view of a plate stack formed according to FIG. 2 a from a plurality of individual plates.
- FIG. 3 shows an enlarged detailed illustration of an S-shaped edge channel.
- FIG. 4 a shows a sectional view according to section “A” of the S-shaped edge channel.
- FIG. 4 b shows a sectional view according to section “B” of the S-shaped edge channel.
- FIG. 4 c shows a sectional view according to section “C” of the S-shaped edge channel.
- FIG. 1 shows perspectively a plate stack S from a plurality of individual plates 1 which are in each case connected to each other so as to form a pair P of plates.
- Each individual plate 1 comprises a bottom 11 which lies in a different plane than the longitudinal edges 12 .
- each individual plate 1 is formed with a contact surface 13 which is offset in height with respect to the longitudinal edges 12 .
- the offset between the contact surface 13 and the associated longitudinal edge 12 is twice as large as the offset between the longitudinal edges 12 and the bottom 11 .
- the bottom 11 is positioned at the middle of the height between the plane of the longitudinal edges 12 and the plane of the contact surfaces 13 .
- the edges running transverse to the longitudinal edges 12 of the individual plate 1 lie approximately half in the plane of the longitudinal edges 12 or in the plane of the contact surfaces 13 , respectively.
- the transverse edges 14 a and 14 b are created which are offset relative to each other in height, i.e., perpendicular to the surface of the bottom 11 , by the same amount as the planes in which the longitudinal edges 12 lie, on the one hand, and the contact surfaces 13 , on the other.
- FIG. 1 clearly shows that here, the transverse edges 14 a and 14 b oppose each other diagonally.
- FIG. 1 exemplary illustrates five complete pairs P of plates, wherein on top of the uppermost pair of plates, an additional individual plate 1 is arranged which is also connected to the uppermost individual plate 1 shown spaced apart so as to form a pair P of plates.
- the pairs P of plates When the pairs P of plates are connected in the region of the contact surfaces 13 so as to form a plate stack S, this results in channels arranged on top of each other for the two media involved in the heat exchange. While the one medium flows in the flow channels which are formed in each case by the pairs P of plates, the other medium flows in the flow channels which are formed by joining the pairs P of plates together so as to form the plate stack S.
- the individual plates' 1 transverse edges 14 a lying in the plane of the longitudinal edges 12 form the inflow cross-section Z 1 or, respectively, the outflow cross-section A 1 of the flow channels for the medium flowing between the pairs P of plates.
- FIG. 1 which shows a countercurrent heat exchanger, illustrates that due to the diagonal arrangement of the inlet and outlet openings, the inflow cross-sections Z 1 and Z 2 , respectively, for the one medium are located next to outflow cross-sections A 2 and A 1 , respectively, for the other medium, namely offset in each case by half the height of a pair P of plates.
- FIG. 2 a shows an individual plate 1 according to the invention, the inflow cross-section Z 1 of which extends over half the width of the individual plate 1 , from the longitudinal center up to the longitudinal edge 12 .
- the individual plate has an inlet region E, the length of which in the main flow direction characterizes the path which the inflowing medium requires to spread over the full width of the individual plate 1 .
- four guide blades 2 are arranged to the right of the longitudinal center of the individual plate 1 , each of which comprises one inflow leg 21 and one outflow leg 22 .
- the inflow legs 21 and outflow legs 22 are approximately of the same length and enclose an angle of approximately 140° to 100° between them. None of the outflow legs 22 protrudes beyond the longitudinal center of the individual plate 1 .
- the inflow legs 21 are in each case attached in close vicinity to the transverse edge 14 a .
- the individual plate 1 has a turbulence-generating profiling 31 , 32 which extends over the entire width of the individual plate up to the contact surfaces 13 .
- Said profiling 31 , 32 consists of a high number of knobs 31 , 32 stamped into the individual plates 1 , which knobs extend in the region of the inflow cross-section Z 1 up to the guide blades 2 and are recessed in the region to the left of the longitudinal center.
- S-shaped edge channels 15 are formed in the region of the contact surfaces 13 , said channels having a cross-section that is size-variable over their longitudinal extension.
- FIG. 2 b shows a perspective view of a plate stack S formed from a plurality of individual plates 1 . The interaction of the individual plates 1 is clearly visible in this illustration.
- FIG. 3 shows such an edge channel 15 in an enlarged top view.
- FIGS. 4 a , 4 b and 4 c show sectional views of this edge channel 15 at different sections A, B and C according to FIG. 3 .
- the cross-section through which the medium flows is at its maximum at the position A, whereas the cross-section at the positions B and C is in each case less than 50% of the maximum cross-section, wherein the cross-section at the positions B and C is in each case narrowed on different sides of the edge channel 15 .
- the restrictions result from stamped embossments which, with regard to the image plane according to FIG. 3 , are shaped as a partial circle, so that in the longitudinal direction, the overall S-shaped course of the channel is obtained.
- the invention functions such that the heat medium, here the flue gas, flowing through the inflow cross-section Z 1 into the individual plate 1 , impinges onto the guide blade's 2 inflow legs 21 immediately adjacent to the transverse edge 14 a . From there, the flue gas is guided onto the outflow legs 22 which are arranged at an angle of approximately 140° to 100°, preferably 135° to 112° relative to the inflow legs 21 .
- the heat medium here the flue gas
- the inlet region E in the region of the inflow cross-section Z 1 has a profiling 31 , 32 arranged immediately subsequent to the guide blades 2 while there is no profiling 31 , 32 in the inlet plate's 1 region located mirror-symmetrically on the left next to the longitudinal center, a pressure distribution develops above the profiling 31 , 32 within the inlet region E, which pressure distribution sucks the inflowing flue gas from the guide blades 2 into the profile-free region. In this manner, the flue gas is uniformly distributed over the width of the plate and provides for a homogenous heat flow rate over the entire inlet plate 1 of the heat exchanger.
- the individual plate 1 can comprise, in addition to the above-illustrated measures, edge channels 15 which, for the purpose of forming a labyrinth, comprise stamped embossments 33 .
- edge channels 15 which, for the purpose of forming a labyrinth, comprise stamped embossments 33 .
- the medium reaching the edge region of the individual plate 1 flows through the edge channels 15 and arrives at the restrictions and expansions of the respective channel cross-sections which cause a backup effect and result in an increased interaction of the medium with the individual plate 1 .
- the flue gas gets into the S-shaped edge channels 15 where the whole channel cross-section is available in the section area A (view FIG. 4 a ).
- the flue gas has to flow through the first curve in which the cross-section is reduced by half.
Abstract
A plate heat exchanger has flow channels through which a first and a second flow passes in concurrent or countercurrent flow. The flow channels are formed for the first medium between individual plates (1) joined together to form in each case a pair (P) of plates, and for the second medium between pairs (P) of plates joined together to form a stack (S) of plates, wherein the individual plates (1) within an inlet region (E) have guide blades (2) which are formed by stamped embossments and protrude into the flow channel, wherein the guide blades (2) are formed in an arch-shaped manner with an inflow leg (21) aligned substantially parallel to the main flow direction and an outflow leg (22) aligned at an angle to the inflow leg (21).
Description
- The invention relates to a plate heat exchanger comprising flow channels through which a first and a second flow flows in concurrent or countercurrent flow, which flow channels are formed for the first medium between individual plates joined together to form in each case a pair of plates, and for the second medium between pairs of plates joined together to form a stack of plates, wherein the individual plates and the pairs of plates are connected to each other at longitudinal edges and support surfaces running parallel to the main flow direction, wherein each individual plate comprises inflow and outflow cross-sections arranged diagonally and corresponding in the longitudinal direction for the first medium, and inflow and outflow cross-sections adjacent thereto in the transverse direction for the second medium, wherein the outflow cross-sections for the first medium are in each case offset by half the height of the inflow and/or outflow cross-sections for the second medium, wherein the individual plates within an inlet region comprise guide blades formed by stamped embossments protruding into the flow channel, wherein the guide blades are formed in an arch-shaped manner with an inflow leg aligned substantially parallel to the main flow direction and an outflow leg aligned at an angle to the inflow leg, and wherein the individual plates are provided with a profiling that generates turbulences.
- Plate heat exchangers of this kind are used on a large scale with plate dimensions of several meters. A field of application here is the use in incinerators, power plants, chemical plants, refineries and/or the like, in which the resulting combustion heat of the flue gas is used for heating the second medium.
- A plate heat exchanger of the aforementioned kind is disclosed in detail in German patent DE 41 42 177 C2. Here, for increasing the efficiency of the heat exchanger or, alternatively, for reducing the dimensions of the required individual plates, guide blades are provided which distribute the medium flowing in through the inflow cross-section over the full channel width of the flow channel. In order to avoid dead zones in the inlet region, in particular in the plate region located mirror-symmetrically adjacent to the longitudinal center, the guide blades are provided with elongated outflow legs which protrude beyond the longitudinal center of the individual plate. In addition, for equalizing the flow within the flow channel, the guide blades are arranged closer to the inflow cross-section in the longitudinal center of the individual plates than in the direction of the longitudinal edge of the individual plate.
- Although this arrangement has proved itself in practice, there are still problems due to depositions of solids within the inflowing medium. This relates in particular to the aforementioned use in incinerators because the flue gases resulting from the combustion contain a large proportion of contaminants. However, this problem is not limited to the use of the heat exchangers in incinerators, but it occurs wherever the medium is mixed with problematic solids. The solids contained result in buildup on the guide blades so that the spaces between adjacent guide blades become narrower and clog the inflow cross-sections. In order to avoid this, in some practical applications, the plate heat exchanger has to be cleaned regularly, for example one to two times per year, causing significant downtimes. This results, on the one hand, in costs due to the complicating cleaning and, on the other, in losses due to the downtimes of the installation.
- It is therefore an object of the invention to provide a plate heat exchanger with which clogging of the inflow cross-sections due to depositions of solids on the guide blades is avoided without reducing the performance of the heat exchanger at the same time.
- As a technical solution for this object, a plate heat exchanger of the aforementioned kind is proposed, in which the guide blades of the inflow cross-sections do not protrude beyond the longitudinal center of the individual plates, i.e., the guide blades are formed exclusively in the plate halves associated with the respective inflow cross-sections, wherein the inflow legs and the outflow legs have substantially identical lengths, and wherein the guide blades are arranged at substantially the same distance from the associated transverse edge of the respective individual plate, and wherein, at the same time, the profiling generating the turbulences protrudes in the inlet region of the inflow cross-sections up to the guide blades and is recessed in the region adjoining mirror-symmetrically the longitudinal center of the individual plates.
- With the guide blades which, according to the invention, are shorter and arranged steeper relative to the main flow direction and closer to edge, adherence of dirt particles is minimized. At the same time, high performance of the heat exchanger is ensured in that the turbulence-generating profiling of the individual plates protrudes in the inlet region of the inflow cross-section up to the guide blades and is recessed in the plate region located mirror-symmetrically opposite to the longitudinal center. Due to this profile recess in the plate half located next to the inflow cross-section, negative pressure is created with respect to the gas pressure inside the profiled inflow cross-section so that the inflowing flue gases are sucked into the profile-free region.
- Therefore, through the specific configuration of the profiling it is considered that the performance of the heat exchanger depends on how homogenously the heating medium is distributed over the width of the countercurrent flow plate. However, measures effecting a uniform distribution generally promote dirt accumulations. The invention thus provides a solution which equilibrates the two competing factors in such a manner that, on the one hand, adherence of dirt particles is reduced and, on the other, no performance loss occurs.
- The configuration according to the invention of the guide blades, on the one hand, and the configuration according to the invention of the profiling generating the turbulences, on the other, in combination result in the synergetic effect that equalization of the media flowing into the heat plate takes place over the entire plate width while minimizing at the same time the risk of contamination which, in the worst case, causes clogging of the guide blades. In contrast to the prior art according to the aforementioned DE 41 42 177 C2, the invention deliberately departs from the previous configuration and proposes to downsize the guide blades, in particular with regard to the respective outflow leg. Moreover, by deliberately departing from the aforementioned prior art, the number of guide blades has been significantly reduced. The deterioration of the medium equalization, as a result of these measures, to be feared according to the explanations in DE 41 42 177 C2 surprisingly did not occur or was compensated in combination with the configuration of the turbulence-generating profiling. The result of the configuration according to the invention is increased efficiency over the prior art with regard to the distribution of the medium, and, at the same time, reduction of the guide-blade-related contact surfaces for dirt particles, foreign substances and/or the like is achieved. As a result, in contrast to the previously known plate heat exchangers, the plate heat exchanger according to the invention is less prone to contamination or even clogging, so that operational safety is increased and/or the maintenance intervals can be extended. A particularly positive effect in this connection has the fact that in contrast to the prior art, the outflow legs of the guide blades according to the invention are formed much steeper and much shorter.
- Advantageously, the guide blades are completely stamped through so that they rest without any gap against the adjacent individual plate. Through this configuration, the guide blades serve completely as a support or a spacer so that vibrations within the pair of plates and within the plate stack are reduced and thus the structure of the heat exchanger overall becomes more stable. Depending on the configuration, the guide blades, which are completely stamped through, can rest against the guide blades of adjacent individual plates or against the opposing wall of the flow channels.
- The invention provides that the inflow legs and the outflow legs are arranged at an angle between 140° and 100°, preferably 135° and 112° relative to each other. The shorter the guide blades, the steeper inflow legs and outflow legs can be arranged relative to each other. Through the combination with an inflow leg aligned substantially parallel to the main flow direction, angles of up to 90° are possible without the risk of clogging the inflow cross-sections with accumulations of foreign matters on the guide blades.
- It is recommended that the turbulence-generating profiling on the individual plates comprises stamped knobs. Said knobs can be produced in a very simple and cost-effective manner by stamping the individual plates. Moreover, a uniform knob field is perfectly suited for increasing performance of the heat exchanger. Through the turbulent flow, heat transfer is increased and therefore efficiency is improved.
- Moreover, some of the knobs can be formed as spacers for adjacent individual plates. In this manner, even in the case of small distances between adjacent individual plates, the predefined plate spacing can be ensured over the entire channel length and channel width. Such spacers can also be formed in the region of the guide blades so as to keep the individual plates in the region of the inflow and outflow cross-sections at the predefined distance from each other. Of course, it is also possible that all knobs serve as spacers.
- The invention provides that the turbulence-generating profiling of the individual plate is formed perpendicular to the main flow direction over the entire bottom up to the contact surfaces. Through this profiling, which extends over the entire width of the individual plate up to the lateral edges thereof, a controlled flow pattern is obtained while avoiding bypasses at the same time. In contrast to the prior art, it is therefore avoided that the medium flowing over the individual plate moves into profile-free channels and contributes to the heat exchange only to a minor extent. Overall, the profiling which, in contrast to the prior art, is brought closer to the lateral edge, therefore effects an improvement of the heat flow rate of the heat exchanger.
- Furthermore, it is provided that in the region of the contact surfaces, the individual plates comprise edge channels with a cross-section that is size-variable over the longitudinal extension of said edge channels. By downsizing the barrier-free bypasses, these edge channels result also in an improved flow pattern so that, in turn, the heat flow rate of the heat exchanger is increased. The edge channels are formed in a labyrinthine manner and are formed in the region of the contact surfaces, i.e., in the edge region of the individual plates, where the heat medium otherwise would seek for a barrier-free and thus interaction-free flow path. The variation of the cross-section over the longitudinal extension of the edge channels provides that the medium flowing therethrough cannot continue to flow straight ahead and in a barrier-free manner, but is subject to a backup effect at the restrictions of the cross-section. Thus, an interaction-free medium flow through the edge channels of the individual plate and accordingly also performance loss is drastically reduced. This results in an increase of performance of up to 5% in comparison to the prior art.
- Particularly advantageously, the edge channels are formed to be substantially S-shaped, i.e., multiple times S-shaped. This results in a staggered blocking embossment on both sides of each edge channel, which embossment leads to increased interaction of the heat medium due to the resulting restrictions and expansions.
- Advantageously, the cross-section of the edge channels can vary up to 50% or more. As a result, the barrier-free cross-section for the medium is reduced at the restriction by more than half. In addition, in combination with the S-shaped configuration, a locally offset flow channel is created which further increases the interaction between medium and heat exchanger.
- In combination with the configuration according to the invention of the turbulence-generating profiling extending into the respective edge region of each individual plate, the edge channel configuration according to the invention results in the synergetic effect that free flow paths for the medium are basically avoided. The media flowing into the plate heat exchanger therefore cannot divert via a bypass-like interaction-free flow-path. In contrast to the prior art, neither the bottom near the edge region of each individual plate nor the edge channel forming in the edge region between two individual plates represent according to the inventive configuration such a bypass because, according to the invention, the edge channels are formed in a labyrinthine manner and the turbulence-creating profiling extends up into the edge region of each individual plate. Thus, as a result, with an unchanged plate size, performance increase can be achieved, or, with the same performance, a downsized plate size can be achieved. There is no example for such a configuration in the prior art.
- Further features and advantages of the invention arise from the following description by means of the figures.
-
FIG. 1 shows a perspective view of a plate stack formed from a plurality of individual plates, wherein for a better overview, the guide blades and the profiling are not illustrated. -
FIG. 2 a shows a top view of an individual plate with guide blades and indicated profiling. -
FIG. 2 b shows a perspective view of a plate stack formed according toFIG. 2 a from a plurality of individual plates. -
FIG. 3 shows an enlarged detailed illustration of an S-shaped edge channel. -
FIG. 4 a shows a sectional view according to section “A” of the S-shaped edge channel. -
FIG. 4 b shows a sectional view according to section “B” of the S-shaped edge channel. -
FIG. 4 c shows a sectional view according to section “C” of the S-shaped edge channel. - The exemplary embodiment of a plate heat exchanger schematically illustrated in
FIG. 1 shows perspectively a plate stack S from a plurality of individual plates 1 which are in each case connected to each other so as to form a pair P of plates. Each individual plate 1 comprises a bottom 11 which lies in a different plane than the longitudinal edges 12. Subsequent and parallel to theselongitudinal edges 12, each individual plate 1 is formed with acontact surface 13 which is offset in height with respect to the longitudinal edges 12. The offset between thecontact surface 13 and the associatedlongitudinal edge 12 is twice as large as the offset between thelongitudinal edges 12 and the bottom 11. Accordingly, the bottom 11 is positioned at the middle of the height between the plane of thelongitudinal edges 12 and the plane of the contact surfaces 13. In the exemplary embodiment, the edges running transverse to thelongitudinal edges 12 of the individual plate 1 lie approximately half in the plane of thelongitudinal edges 12 or in the plane of the contact surfaces 13, respectively. In this manner, thetransverse edges longitudinal edges 12 lie, on the one hand, and the contact surfaces 13, on the other.FIG. 1 clearly shows that here, thetransverse edges - In each case two of the individual plates 1 illustrated in
FIG. 1 as the uppermost part are connected according to the bottom illustration inFIG. 1 so as to form pairs P of plates.FIG. 1 exemplary illustrates five complete pairs P of plates, wherein on top of the uppermost pair of plates, an additional individual plate 1 is arranged which is also connected to the uppermost individual plate 1 shown spaced apart so as to form a pair P of plates. - When the pairs P of plates are connected in the region of the contact surfaces 13 so as to form a plate stack S, this results in channels arranged on top of each other for the two media involved in the heat exchange. While the one medium flows in the flow channels which are formed in each case by the pairs P of plates, the other medium flows in the flow channels which are formed by joining the pairs P of plates together so as to form the plate stack S. Here, the individual plates' 1
transverse edges 14 a lying in the plane of thelongitudinal edges 12 form the inflow cross-section Z1 or, respectively, the outflow cross-section A1 of the flow channels for the medium flowing between the pairs P of plates. The individual plates' 1transverse edges 14 b extending in the plane of the contact surfaces 13 form the inflow cross-sections Z2 or, respectively, the outflow cross-sections A2 for the other medium which flows between the individual plates 1 of each pair P of plates in the same direction or in the direction counter to the first medium.FIG. 1 , which shows a countercurrent heat exchanger, illustrates that due to the diagonal arrangement of the inlet and outlet openings, the inflow cross-sections Z1 and Z2, respectively, for the one medium are located next to outflow cross-sections A2 and A1, respectively, for the other medium, namely offset in each case by half the height of a pair P of plates. -
FIG. 2 a shows an individual plate 1 according to the invention, the inflow cross-section Z1 of which extends over half the width of the individual plate 1, from the longitudinal center up to thelongitudinal edge 12. The individual plate has an inlet region E, the length of which in the main flow direction characterizes the path which the inflowing medium requires to spread over the full width of the individual plate 1. In the image plane, fourguide blades 2 are arranged to the right of the longitudinal center of the individual plate 1, each of which comprises oneinflow leg 21 and oneoutflow leg 22. Theinflow legs 21 andoutflow legs 22 are approximately of the same length and enclose an angle of approximately 140° to 100° between them. None of theoutflow legs 22 protrudes beyond the longitudinal center of the individual plate 1. Theinflow legs 21 are in each case attached in close vicinity to thetransverse edge 14 a. The individual plate 1 has a turbulence-generatingprofiling Said profiling knobs guide blades 2 and are recessed in the region to the left of the longitudinal center. - With regard to the image plane according to
FIG. 2 , S-shapededge channels 15 are formed in the region of the contact surfaces 13, said channels having a cross-section that is size-variable over their longitudinal extension. -
FIG. 2 b shows a perspective view of a plate stack S formed from a plurality of individual plates 1. The interaction of the individual plates 1 is clearly visible in this illustration. -
FIG. 3 shows such anedge channel 15 in an enlarged top view.FIGS. 4 a, 4 b and 4 c show sectional views of thisedge channel 15 at different sections A, B and C according toFIG. 3 . It can be seen that the cross-section through which the medium flows is at its maximum at the position A, whereas the cross-section at the positions B and C is in each case less than 50% of the maximum cross-section, wherein the cross-section at the positions B and C is in each case narrowed on different sides of theedge channel 15. Here the restrictions result from stamped embossments which, with regard to the image plane according toFIG. 3 , are shaped as a partial circle, so that in the longitudinal direction, the overall S-shaped course of the channel is obtained. - The invention functions such that the heat medium, here the flue gas, flowing through the inflow cross-section Z1 into the individual plate 1, impinges onto the guide blade's 2
inflow legs 21 immediately adjacent to thetransverse edge 14 a. From there, the flue gas is guided onto theoutflow legs 22 which are arranged at an angle of approximately 140° to 100°, preferably 135° to 112° relative to theinflow legs 21. Due to the fact that the inlet region E in the region of the inflow cross-section Z1 has aprofiling guide blades 2 while there is noprofiling profiling guide blades 2 into the profile-free region. In this manner, the flue gas is uniformly distributed over the width of the plate and provides for a homogenous heat flow rate over the entire inlet plate 1 of the heat exchanger. Due to the particularly short and steep configuration of theguide blades 2, adherence of dirt particles on theguide blades 2 is reduced so that clogging of the inflow cross-section Z1 is prevented. Therefore, all in all, a low-maintenance plate heat exchanger is created which is not subject to a performance loss. - According to an embodiment variant, the individual plate 1 can comprise, in addition to the above-illustrated measures,
edge channels 15 which, for the purpose of forming a labyrinth, comprise stampedembossments 33. Here, the medium reaching the edge region of the individual plate 1 flows through theedge channels 15 and arrives at the restrictions and expansions of the respective channel cross-sections which cause a backup effect and result in an increased interaction of the medium with the individual plate 1. As shown inFIG. 3 , the flue gas gets into the S-shapededge channels 15 where the whole channel cross-section is available in the section area A (viewFIG. 4 a). In the region of section B (viewFIG. 4 b), the flue gas has to flow through the first curve in which the cross-section is reduced by half. In the course of this, the aforementioned backup effect is generated. Downstream of the curve, the cross-section expands again temporarily and reduces again in the region of section C (FIG. 4 c) to half the cross-section; however, this time following the S-shape of theedge channel 15 in the region of the opposing channel side wall. Therefore, all in all, performance losses which, according to the prior art, occur due to bypasses in the edge region of the individual plate 1, are considerably reduced through higher interaction of the heat medium with the individual plates 1, which, in turn, results in increased performance of the heat exchangers. This effect can be enhanced in that the turbulence-generatingprofiling - A Outlet region
- A1 Outflow cross-section
- A2 Outflow cross-section
- E Inlet region
- P Pair of plates
- S Plate stack
- Z1 Inflow cross-section
- Z2 Inflow cross-section
- 1 Individual plate
- 11 Bottom
- 12 Longitudinal edge
- 13 Contact surface
- 14 a Transverse edge
- 14 b Transverse edge
- 15 Edge channel
- 2 Projection
- 21 Inflow leg
- 22 Outflow leg
- 31 Individual knob
- 32 Individual knob
- 33 Stamped embossment
Claims (10)
1. A plate heat exchanger comprising flow channels through which a first and a second flow flows in concurrent or countercurrent flow, which flow channels are formed for the first medium between individual plates (1) joined together to form in each case a pair (P) of plates, and for the second medium between pairs (P) of plates joined together to form a stack (S) of plates, wherein the individual plates (1) and the pairs (P) of plates are connected to each other at longitudinal edges (12) and support surfaces (13) running parallel to the main flow direction, wherein each individual plate (1) comprises inflow and outflow cross-sections (Z1, Z2, A1, A2) arranged diagonally and corresponding in the longitudinal direction for the first medium, and inflow and outflow cross-sections (Z1, Z2, A1, A2) adjacent thereto in the transverse direction for the second medium, wherein the inflow and outflow cross-sections (A1, A2, Z1, Z2) for the first medium are in each case offset by half the height of the inflow and outflow cross-sections (Z1, Z2, A1, A2) for the second medium, wherein the individual plates (1) within an inlet region (E) comprise guide blades (2) formed by stamped embossments protruding into the flow channel, wherein the guide blades (2) are formed in an arch-shaped manner with an inflow leg (21) aligned substantially parallel to the main flow direction and an outflow leg (22) aligned at an angle to the inflow leg (21), and wherein the individual plates (1) are provided with a profiling (31, 32) that generates turbulences, wherein
the guide blades (2) of the inflow cross-sections (Z1, Z2) do not protrude beyond the longitudinal center of the individual plates (1), wherein the inflow legs (21) and the outflow legs (22) have substantially identical lengths, and wherein the guide blades (2) are arranged at substantially the same distance from the associated transverse edge (14 a, 14 b) of the respective individual plate (1), and
the profiling (31, 32) generating the turbulences protrudes in the inlet region (E) of the inflow cross-sections (Z1, Z2) up to the guide blades (2) and is recessed in the region adjoining mirror-symmetrically the longitudinal center of the individual plates (1).
2. The plate heat exchanger according to claim 1 , wherein the guide blades (2) are completely stamped through so that the guide blades (2) rest without any gap against the adjacent individual plate (1).
3. The plate heat exchanger according to claim 1 , wherein the inflow legs (21) and the outflow legs (22) are arranged at an angle between 140° and 100° relative to each other.
4. The plate heat exchanger according to claim 3 , wherein the inflow legs (21) and the outflow legs (22) are arranged at an angle between 135° and 112° relative to each other.
5. The plate heat exchanger according to claim 1 , wherein the profiling (31, 32) generating the turbulences has stamped knobs (31, 32).
6. The plate heat exchanger according to claim 5 , wherein some of the knobs (31, 32) are formed as spacers for adjacent individual plates (1).
7. The plate heat exchanger according to claim 1 , wherein the turbulence-generating profiling (31, 32) of the individual plate (1) is formed perpendicular to the main flow direction over the entire bottom (11) up to the contact surfaces (13).
8. The plate heat exchanger according to claim 1 , wherein in the region of the contact surfaces (13), the individual plates (1) comprise edge channels (15) with a cross-section that is size-variable over the longitudinal extension of said edge channels.
9. The plate heat exchanger according to claim 8 , wherein the edge channels (15) are formed to be substantially S-shaped or multiple times S-shaped.
10. The plate heat exchanger according to claim 8 , wherein the cross-section of the edge channels (15) can vary up to 50% or more.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP12165204.4A EP2657635B1 (en) | 2012-04-23 | 2012-04-23 | Plate heat exchanger |
EP12165204.4 | 2012-04-23 |
Publications (1)
Publication Number | Publication Date |
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US20130277024A1 true US20130277024A1 (en) | 2013-10-24 |
Family
ID=46026684
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/620,790 Abandoned US20130277024A1 (en) | 2012-04-23 | 2012-09-15 | Plate Heat Exchanger |
Country Status (3)
Country | Link |
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US (1) | US20130277024A1 (en) |
EP (1) | EP2657635B1 (en) |
KR (1) | KR102009304B1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108692597B (en) * | 2018-07-23 | 2023-10-03 | 江苏唯益换热器有限公司 | Plate heat exchanger capable of preventing internal leakage |
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US20060124287A1 (en) * | 2002-10-31 | 2006-06-15 | Reinders Johannes Antonius M | Heat exchanger and method of manufacture thereof |
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DE4100940C1 (en) * | 1991-01-15 | 1991-11-21 | Balcke-Duerr Ag, 4030 Ratingen, De | |
DE19832164C2 (en) * | 1998-07-17 | 2002-12-05 | Balcke Duerr Gmbh | Plate heat exchanger |
KR20030067877A (en) * | 2002-02-08 | 2003-08-19 | 벤트-악시아 그룹 리미티드 | Heat exchanger |
DE102007029753A1 (en) * | 2007-06-27 | 2009-01-08 | Gea Ecoflex Gmbh | Plate heat exchanger has channels flowed through in direct current or counter current of mediums, and sum of light gap of two mediums corresponds to distance between two disk pairs |
-
2012
- 2012-04-23 EP EP12165204.4A patent/EP2657635B1/en active Active
- 2012-09-15 US US13/620,790 patent/US20130277024A1/en not_active Abandoned
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2013
- 2013-04-23 KR KR1020130051327A patent/KR102009304B1/en active IP Right Grant
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Also Published As
Publication number | Publication date |
---|---|
EP2657635A1 (en) | 2013-10-30 |
EP2657635B1 (en) | 2015-06-10 |
RU2012145975A (en) | 2014-05-10 |
KR20130119390A (en) | 2013-10-31 |
KR102009304B1 (en) | 2019-08-09 |
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