Plate Heat Exchanger
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).
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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.
SUMMARY OF THE INVENTIONAs 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.
The exemplary embodiment of a plate heat exchanger schematically illustrated in
In each case two of the individual plates 1 illustrated in
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 14a lying in the plane of the longitudinal 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' 1 transverse edges 14b 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.
With regard to the image plane according to
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 the transverse edge 14a. 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. Due to the fact that the inlet region E in the region of the inflow cross-section Z1 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. Due to the particularly short and steep configuration of the guide blades 2, adherence of dirt particles on the guide 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 stamped embossments 33. Here, 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. As shown in
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
14a Transverse edge
14b Transverse edge
15 Edge channel
2 Projection
21 Inflow leg
22 Outflow leg
31 Individual knob
32 Individual knob
33 Stamped embossment
Claims
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 (14a, 14b) 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.
Type: Application
Filed: Sep 15, 2012
Publication Date: Oct 24, 2013
Applicant: GEA ECOFLEX GMBH (Duisburg)
Inventors: Gerd Abker (Marl), Alfred Ernst (Mettmann), Bernd Müller (Ratingen), Klaus Mönig (Bottrop)
Application Number: 13/620,790
International Classification: F28D 9/00 (20060101);