EP2307842B1 - Wärmetauscher - Google Patents

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Publication number
EP2307842B1
EP2307842B1 EP09762768.1A EP09762768A EP2307842B1 EP 2307842 B1 EP2307842 B1 EP 2307842B1 EP 09762768 A EP09762768 A EP 09762768A EP 2307842 B1 EP2307842 B1 EP 2307842B1
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EP
European Patent Office
Prior art keywords
distribution
heat exchanger
refrigerant
passage
plates
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EP09762768.1A
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English (en)
French (fr)
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EP2307842A1 (de
EP2307842A4 (de
Inventor
Alvaro Zorzin
Leif Hallgren
Angelo Muzzolon
Marcello Pavan
Emanuele Biancon
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Alfa Laval Corporate AB
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Alfa Laval Corporate AB
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Publication of EP2307842A1 publication Critical patent/EP2307842A1/de
Publication of EP2307842A4 publication Critical patent/EP2307842A4/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/086—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning having one or more openings therein forming tubular heat-exchange passages
    • 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
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the present invention relates to a plate heat exchanger having three separate fluid circuits.
  • a plate heat exchanger will have two independent refrigerant circuits and one liquid circuit.
  • Plate heat exchangers having three separate fluid circuits, one circuit for the liquid and two circuits for the refrigerant, show some advantages with respect to heat exchangers having two fluid circuits.
  • Such a heat exchanger allows for a well balanced cooling effect with less risk of freezing when used as an evaporator. It will also operate under partial load conditions in an efficient way which will reduce energy consumption. The installation will be easier and faster, which will reduce installation cost. Further, it will allow for a simpler and thus less expensive control system.
  • a plate heat exchanger used as an evaporator in a system of this kind often has heat exchanging plates that are welded or brazed together, but also sealing gaskets may be used for sealing between the heat transferring plates.
  • EP 0765461 B shows a plate heat exchanger with flow passages for three different fluids between the plates.
  • the delivery of the three fluids to the core of plates is done in such a way that passages for the fluid number one are present on both sides of every passage for each one of the two remaining fluids.
  • the passages are created using two different kinds of plates. Good sealing between adjacent plates at the openings creating the inlet and outlet channels for the three fluids is created by designing the areas around the ports, thereby defining a system with annular planar plateaus.
  • EP 1062472 B shows another example of a three fluid circuit heat exchanger. This application mainly concerns the connection of the port holes in an airtight manner.
  • EP 0965025 B describes a plate heat exchanger for three heat exchanging fluids.
  • the port holes of the heat exchanger are pair wise aimed for the flowing through of the respective heat exchanging fluids and the port holes are symmetrically positioned on both sides of a heat transferring part in such a way that a straight line drawn between the centres of the port holes divides the heat transferring part into two alike parts.
  • US3532161 discloses a heat exchanger according to the preamble of claim 1.
  • An object of the invention is therefore to provide an improved heat exchanger having an improved flow distribution in each flow circuit.
  • a further object of the invention is to provide a heat exchanger having an improved heat transfer coefficient.
  • the object of the invention is achieved in that the central port hole of the first distribution area is positioned at a vertical distance from the short end of the plate such that a fluid passage is obtainable between the central port hole and the short end of the plate when two plates are stacked to form a fluid channel between the plates.
  • a heat exchanger plate is obtained which allows for an improved flow distribution in the first distribution passage for the refrigerant circuits.
  • the advantage of this is that a larger part of the heat exchanger plate, i.e. the area around the passive inlet port, can also be used as an effective heat transfer surface.
  • Another advantage is that the flow distribution of the fluid in the first or lower distribution passage is improved, which in turn improves the flow distribution in the heat transfer passage.
  • Another advantage is that the flow in the liquid circuit and into the liquid outlet port is also improved. The efficiency of the heat exchanger will thus be improved.
  • the central port hole of the second distribution area is positioned at a vertical distance from the short end of the plate such that a fluid passage is obtainable between the central port hole and the short end of the plate when two plates are stacked to form a fluid channel between the plates.
  • a larger part of the heat exchanger plate i.e. the area around the passive outlet port, can also be used as an effective heat transfer surface.
  • Another advantage is that the flow distribution of the liquid from the inlet port is improved, which in turn improves the liquid flow distribution in the heat transfer passage. The efficiency of the heat exchanger will thus be further improved.
  • At least one corner of the plate is provided with a flat, ring-shaped bypass section adapted to form a refrigerant bypass passage around a port when two plates are stacked to form a refrigerant fluid channel between the plates. This will improve the fluid distribution in the refrigerant channels of the heat exchanger.
  • At least one water bypass section is provided at a corner of the plate such that a water passage is obtainable between two adjacent bypass sections when two plates are stacked to form a water channel between the plates. This will improve the fluid distribution in the water channel of the heat exchanger.
  • a lower distribution groove is provided between the first distribution area and the heat exchange area, the lower distribution groove comprises at least one restriction area, and an upper distribution groove is provided between the heat exchange area and the upper distribution area.
  • the first distribution area exhibits a chevron shape having a first layout
  • the second distribution area exhibits a chevron shape having a second layout
  • the heat exchange area exhibits a chevron shape having a third layout
  • the chevron shape of the first layout is directed in a first angular direction
  • the chevron shape of the second layout is directed in the opposite angular direction.
  • a heat exchanger assembly comprising four heat exchanger plates
  • the object of the invention is achieved in that the first plate, the second plate, the third plate and the fourth plate are different.
  • a first refrigerant channel is provided between the first plate and the second plate
  • a water channel is provided between the second plate and the third plate
  • a second refrigerant channel is provided between the third plate and the fourth plate
  • each fluid channel comprises a first distribution passage provided between two adjacent first distribution areas, a heat exchange passage provided between two adjacent heat exchange areas and a second distribution passage provided between two adjacent second distribution areas
  • a horizontal passage is provided in the first distribution passage between the central water port and the short end of the assembly.
  • the horizontal passage will improve the flow distribution in the first distribution passage which in turn will improve the flow distribution in the heat transfer passage.
  • This will allow a larger part of the heat exchanger plate, i.e. the area around the passive inlet port, to function as an effective heat transfer surface.
  • Another advantage is that the fluid flow in the liquid circuit is improved since the complete liquid outlet port is open. The efficiency of the heat exchanger will thus be improved.
  • a horizontal passage is provided in the second distribution passages between the central water port and the neighbouring short end of the assembly.
  • a larger part of the heat exchanger plate i.e. the area around the passive outlet port, can also be used as an effective heat transfer surface.
  • Another advantage is that the flow distribution of the liquid from the inlet port is improved, which in turn improves the liquid flow distribution in the heat transfer passage. The efficiency of the heat exchanger will thus be further improved.
  • a water bypass passage is provided in a water distribution passage between a refrigerant port and a corner of the assembly. This is advantageous in that a water bypass is obtained, which will improve the water flow distribution in the heat exchanger considerably.
  • a refrigerant bypass passage is provided around a refrigerant port in a refrigerant distribution passage. This is advantageous in that the refrigerant flow distribution is improved considerably.
  • the active refrigerant inlet ports are provided with inlet nozzles, where the angle of the inlet nozzles is between 0 and 180 degrees relative a vertical axis and where the inlet nozzle points towards the central vertical axis of the assembly. In this way, the inlet nozzle will point towards the centre of the heat exchanger, which will improve the fluid distribution in the heat exchanger.
  • a lower distribution path is provided between a lower distribution passage and a heat exchange passage. This is advantageous in that the flow distribution in the lower distribution passage can be controlled in a more refined way, such that the flow into the heat exchange passage can become as even as possible.
  • the lower distribution path comprises at least one restriction means such that a flow restriction is obtained in the lower distribution path.
  • an upper distribution path is provided between the heat exchange passage and the upper distribution passage. This is advantageous in that the flow distribution into the upper distribution passage can be evened out further.
  • a three-circuit heat exchanger comprising a plurality of inventive heat exchanger assemblies and further comprising at least a front plate and a back plate, an improved heat exchanger is obtained.
  • water is used as an example of a fluid that is to be cooled or heated.
  • the fluid that is to be cooled or heated is adapted to be used in a single-phase, in a solely liquid state.
  • the layout of the heat exchanger is thus adapted to a single-phase liquid for the water circuit. It is of course possible to use other fluids as well, such as different mixtures of waters and other fluids, e.g. for the purpose of anti-freezing or corrosion protection.
  • a refrigerant is used as an example of a fluid that is to be evaporated or condensed.
  • This fluid will preferably be used in two phases, a liquid state and a vapour state, but it is possible to use the fluid only in a single state, either in a liquid state, a vapour state or a mixture.
  • the layout of the heat exchanger is thus adapted to a two-phase fluid for the other fluid circuits.
  • the invention relates to a plate heat exchanger having three separate channel types allowing for three different fluid flow circuits.
  • One of the channels is adapted to carry a single-phase liquid that is to be heated or cooled. In this application, water will be used as an example of such a liquid.
  • the other two channels are adapted to carry a two-phase refrigerant that is adapted to evaporate or condensate in the heat exchanger.
  • the channels may either be connected so that one refrigerant is common to both circuits or the channels may be separated so that a different refrigerant can be used in each circuit.
  • a two phase saturated fluid that is in a somewhat pressurized state when entering the heat exchanger and which will evaporate in the heat exchanger is used as an example of a refrigerant.
  • the plate heat exchanger is in accordance with the invention of the permanently joined type, i.e. the plates are brazed, glued, bonded, soldered or welded together to form a complete heat exchanger.
  • the plate heat exchanger comprises a plurality of heat exchanger assemblies, where each assembly comprises four different heat exchanger plates. It is however also possible to use different sealing types, e.g. gaskets between the plates, welded plates or semi-welded plate unit with gaskets between every second plate.
  • the heat exchanger plates are formed using two different pressing tools, thereby obtaining two different plate types, a first plate type having a chevron layout in one direction and a second plate type having a chevron layout in the opposite direction.
  • the layout comprises a corrugation pattern consisting of ridges and valleys which extend across the plates in a chevron layout with angle direction change points along longitudinal lines dividing the plate width into equal parts.
  • the corrugation pattern together with the chevron layout is laid out such as to provide many crossing points of the pattern when the plates are stacked together, thereby creating a strong and rigid heat exchanger having a efficient heat transfer.
  • Corrugated pattern and layouts of this kind are well known to the skilled person. It is also possible to use a corrugated pattern having the same angle over the complete surface, i.e. which does not have any direction change points.
  • Each plate type is in a second operation run through one or more further pressing/cutting operations, thereby creating four different plates.
  • the port hole regions of the plates are pressed and cut to the final shape and the nozzle indentation is formed.
  • the resulting plates comprising a first plate 101, a second plate 201, a third plate 301 and a fourth plate 401, are stacked so that they form a heat exchanger plate assembly.
  • the plates are stacked such that every other plate is of the same plate type if the size and layout of the port hole region and the nozzle are not considered.
  • the port hole regions will differ between the plates, as will be described below.
  • the layout of the first plate type can thus have a slightly smaller angle and the layout of the second plate type a slightly larger angle, so that the mean value of the angles corresponds to the desired angle value of the layout.
  • Each heat exchanger plate comprises a first or lower distribution area comprising three port holes, a central heat exchange area and a second or upper distribution area comprising three port holes.
  • Each plate has a longitudinal or vertical axis and a lateral or horizontal axis.
  • the port holes of the first distribution area are arranged symmetrically with respect to the longitudinal axis.
  • the port holes of the second distribution area are also arranged symmetrically with respect to the longitudinal axis.
  • the port holes of the first and second distribution areas may be arranged symmetrically with respect to each other.
  • the port holes of the first and second distribution areas are however not arranged symmetrically with respect to each other, since the port holes adapted for an evaporated phase of a refrigerant are larger in diameter than the port holes adapted for a flushed liquid vapour mixture of the refrigerant, and the port holes are positioned at approximately the same distance from the corners of the plates.
  • the port holes in the second distribution area are adapted for the refrigerant in the vapour state and the port holes in the first distribution area are adapted for the liquid refrigerant.
  • the heat exchanger is in one example intended to be used for rising film evaporation on the refrigerant channel side and cooling on the water side in a counter-current flow arrangement.
  • a heat exchanger used for rising film evaporation will be used to exemplify the invention.
  • the references in the description will thus refer to the geometries for the position of such a vertical, upright heat exchanger. It is also possible to use the heat exchanger in other positions if required, e.g. at different angles around the horizontal axis.
  • the refrigerant two-phase fluid may be a mixture of liquid and vapour when entering the heat exchanger and may be completely evaporated, and even superheated, when leaving the heat exchanger.
  • the heat exchanger may also be used with the water and the refrigerant flowing in the same directions, i.e. a co-current flow.
  • the heat exchanger described is adapted for a diagonal flow of the refrigerant, i.e. the refrigerant will enter the heat exchanger through a port at a lower corner of the heat exchanger and will leave the heat exchanger through a port in the opposite higher corner. It is of course also possible to adapt the heat exchanger for a parallel flow, where the refrigerant enters the heat exchanger through a port at a lower corner of the heat exchanger and leaves the heat exchanger through a port in the higher corner on the same side, by adapting the inlet or outlet ports accordingly.
  • the heat exchanger may also be used for falling film refrigerant condensation while heating the water side in a counter-current flow or co-current flow arrangement.
  • the two-phase refrigerant fluid may be in a superheated or saturated vapour state when entering the heat exchanger through the upper distribution passage and may be partly or completely condensed and even sub-cooled when leaving the heat exchanger through the lower refrigerant port.
  • the heat exchanger may also be used as a desuperheater or gas cooler in a single phase heat transfer, or an economizer for evaporation, and similar uses, depending on the requirements of the installation. Small modifications may, depending on the use, be required in the plate layout.
  • the first heat exchanger plate 101 shown in Fig. 2 , comprises a first or lower distribution area 102, a heat exchange area 103 and a second or upper distribution area 104.
  • the plate has a longitudinal or vertical axis 105 and a lateral or horizontal axis 106.
  • the lower distribution area 102 is provided with a first refrigerant inlet port hole 107, a water outlet port hole 112 and a second refrigerant inlet port hole 109.
  • the first inlet port hole 107 is provided with a nozzle indentation 114.
  • the heat exchange area 103 is thus referred to as a heat exchange area since the main purpose is that of heat transfer, even though there will be some fluid distribution also in the heat exchange area.
  • the lower and upper distribution areas have the dual purpose of both fluid distribution as well as heat transferral.
  • the layout of the first distribution area 102 exhibits a single chevron shape, i.e. a V shape, where the direction change point is central to the plate, dividing the first distribution area in two equal parts.
  • the layout angle of the V layout is preferably between 50 and 70 degrees with respect to the vertical axis of the heat exchanger.
  • the interior angle of the V shape is thus between 100 and 140 degrees. Other angles are plausible but it is advantageous that the interior angle of the V shape is obtuse.
  • the heat exchange area 103 is provided with a corrugated pattern exhibiting a chevron layout, i.e. a W shape, having three direction change points dividing the heat exchange area in four equal parts.
  • a chevron layout i.e. a W shape
  • the interior angle between the chevrons is of great importance for the friction factor of a channel.
  • one advantage of using a W shape instead of a V shape is that the mean friction factor for the heat transfer area will be higher than when using a V shape. The heat transfer coefficient will thus be higher than for a conventional V shape.
  • the use of the W shape gives a layout with three direction changes. It is also possible to use a chevron layout having two, four or even more direction changes. At the transition region of the chevrons, i.e. at the direction change points, the horizontal and also the vertical flow velocity component is reduced and may be close to zero. In the shown first plate, the layout resembles a W placed upside down.
  • the angle of the corrugated W shape is preferably between 50 and 70 degrees with respect to the vertical axis of the heat exchanger.
  • the interior angle of a chevron is thus between 100 and 140 degrees.
  • the interior angle of the chevrons of the heat exchange area may be the same as the chevrons of the first distribution area, or it may be somewhat smaller. Other angles are plausible but it is important that the interior angle of the chevrons is obtuse.
  • the friction factor of the heat exchange passage depends e.g. on the interior angle of the chevron shape together with the number of direction changes.
  • the upper distribution area 104 of the plate is provided with a first refrigerant outlet port hole 108, a water inlet port hole 111 and a second refrigerant outlet port hole 110.
  • the corrugated pattern of the upper distribution area exhibits a chevron layout resembling a single V placed upside down.
  • the interior angle of the V shape may be the same as for the lower distribution area.
  • the interior angle of the chevrons in the lower distribution area, the heat exchange area and the upper distribution area may be the same or the may differ.
  • the chevrons of the lower distribution area and the heat exchange area are provided with the same interior angle.
  • the chevron shape of the upper distribution area is in this embodiment provided with an angle that is smaller with respect to the vertical axis.
  • the chevrons of the lower distribution area is provided with a first angle
  • the chevrons of the heat exchange area are provided with a second, smaller angle
  • the chevrons of the upper distribution area is provided with an even smaller angle.
  • the angles are in the interval of between 50 and 70 degrees.
  • the advantage of having different interior angles of the different areas is that, when the refrigerant is evaporating, the volume flow will be higher in the upper part of the heat exchanger.
  • the different interior angles will thus give a lower flow resistance when the volume flow increases with the flow direction in the channel.
  • a smaller interior chevron angle in relation to the vertical axis will give a lower flow resistance in this flow direction.
  • the second heat exchanger plate 201 shown in Fig. 3 , comprises a lower distribution area 202, a heat exchange area 203 and an upper distribution area 204.
  • the plate has a vertical axis 205 and a horizontal axis 206.
  • the lower distribution area 202 is provided with a first refrigerant inlet port hole 207, a water outlet port hole 212 and a second refrigerant inlet port hole 209.
  • the first inlet port hole 207 is provided with a nozzle indentation 214.
  • the layout of the lower distribution area 202 exhibits a single chevron shape, i.e. a V shape, where the V shape resembles a V placed upside down.
  • the direction change point is central to the plate, dividing the first distribution area in two equal parts. Apart from the direction of the chevron shape, the angles of the layout are the same as for the first plate.
  • the heat exchange area 203 is provided with a corrugated pattern exhibiting a chevron layout, i.e. a W shape, having three direction change points dividing the heat exchange area in four equal parts.
  • a chevron layout i.e. a W shape
  • the layout resembles a W.
  • the angles of the layout are the same as for the first plate.
  • the upper distribution area 204 of the second plate is provided with a first refrigerant outlet port hole 208, a water inlet port hole 211 and a second refrigerant outlet port hole 210.
  • the corrugated cross pattern of the upper distribution area exhibits a chevron layout resembling a single V.
  • the interior angle of the V shape may be the same as for the lower distribution area. Apart from the direction of the chevron shape, the angles of the layout are the same as for the first plate.
  • the third heat exchanger plate 301 shown in Fig. 4 , comprises a lower distribution area 302, a heat exchange area 303 and an upper distribution area 304.
  • the plate has a vertical axis 305 and a horizontal axis 306.
  • the lower distribution area 302 is provided with a first refrigerant inlet port hole 307, a water outlet port hole 312 and a second refrigerant inlet port hole 309.
  • the upper distribution area 304 of the plate is provided with a first refrigerant outlet port hole 308, a water inlet port hole 311 and a second refrigerant outlet port hole 310.
  • the third heat exchanger plate Apart from the port holes and the nozzle indentation, the third heat exchanger plate resembles the first heat exchanger plate.
  • the fourth heat exchanger plate 401 shown in Fig. 5 , comprises a lower distribution area 402, a heat exchange area 403 and an upper distribution area 404.
  • the plate has a vertical axis 405 and a horizontal axis 406.
  • the lower distribution area 402 is provided with a first refrigerant inlet port hole 407, a water outlet port hole 412 and a second refrigerant inlet port hole 409.
  • the upper distribution area 404 of the plate is provided with a first refrigerant outlet port hole 408, a water inlet port hole 411 and a second refrigerant outlet port hole 410.
  • the fourth heat exchanger plate Apart from the port holes and the nozzle indentation, the fourth heat exchanger plate resembles the second heat exchanger plate.
  • the phrase active inlet port means that the inlet port is open to let refrigerant flow through that inlet port into that refrigerant channel.
  • a passive inlet port means that the inlet port is sealed so that no refrigerant can flow into the refrigerant channel through the passive inlet port.
  • active outlet port which means that the outlet port is in contact with the refrigerant channel so that the refrigerant flows out of the active outlet port.
  • a passive outlet port is sealed so that no refrigerant can flow out from the refrigerant channel through the passive outlet port.
  • FIG. 1 an embodiment of the inventive heat exchanger plate assembly 1 comprising a first plate 101, a second plate 201, a third plate 301 and a fourth plate 401 is shown.
  • the different plates are shown in Figs. 2 - 5 .
  • the plates are stacked on each other in the number required for a specific heat exchanger.
  • a heat exchanger comprising a plurality of assemblies is formed.
  • the number of assemblies is selectable depending on the required specifications of a heat exchanger.
  • a complete heat exchanger will also include a specific front plate and back plate (not shown) having a larger thickness than the individual heat exchanger plates.
  • the front plate and back plate will comprise connections etc.
  • the liquid channel closest to the front and back plate will be a water channel.
  • a separate heat exchanger plate forming a water channel with the first plate may thus be comprised in the front plate, and a separate heat exchanger plate forming a water channel with the fourth plate may thus be comprised in the back plate.
  • the front and back plates will strengthen the heat exchanger, making it more stable and rigid.
  • the heat exchanger is of the brazed type. Between the first and the second plate, a first refrigerant channel 2 is formed. Between the second and the third plate, a water channel 3 is formed. Between the third and the fourth plate, a second refrigerant channel 4 is formed. Between the fourth plate and the first plate of a further assembly, a water channel is formed. In this way, the heat exchanger will have alternating first and second refrigerant channels, being surrounded by a water channel on each side.
  • Both a refrigerant channel and a water channel will comprise a lower distribution passage, a heat exchange passage and an upper distribution passage.
  • the vertical length of the lower distribution passage is preferably less than half of the width of the heat exchanger, while the vertical length of the upper distribution passage is preferably less than two thirds of the width of the heat exchanger.
  • a first refrigerant channel 2 is formed.
  • the refrigerant will enter the first refrigerant channel through a first refrigerant inlet port 21, being an active inlet port, created by the first refrigerant inlet port holes 107, 207.
  • the inlet port holes 107, 207 are provided with concentric sealing sections 113, 213 that will bear on each other.
  • the inlet into the first refrigerant channel is provided by an inlet nozzle 25 in the sealing sections.
  • the inlet nozzle is obtained by nozzle indentations 114, 214 in one or both of the sealing sections, pressed in the second press operation.
  • the size of the inlet nozzle i.e.
  • the length and the cross section, together with the angular position of the inlet nozzle are both important for the refrigerant distribution in the lower distribution passage 10 created between the lower distribution areas 102 and 202.
  • the size of the inlet nozzle depends partly on the inlet pressure of the refrigerant and is selected to achieve an even flow distribution over all refrigerant channels in a complete heat exchanger.
  • the angular position of the inlet nozzle is chosen such that the refrigerant can distribute evenly over the total width of the heat exchanger in each refrigerant channel.
  • the inlet nozzle may be directed in any chosen angle, depending e.g. on the corrugated pattern layout in the lower distribution passage and the bypass section around the inlet port.
  • the angle of the inlet nozzle is between 0 and 180 degrees relative a vertical axis and pointing towards the central vertical axis of the plate, and more preferably between 90 and 150 degrees.
  • the inlet port is opened. This may be advantageous when the heat exchanger is used such that the inlet port acts as a vapour outlet port, e.g. in a gas cooler. In order to avoid vapour from blocking the outlet, the sealing section and the nozzle are cut away in the production stage. Instead, an open port, resembling outlet port 22, is obtained. Such a port will allow vapour or a mixture of vapour and liquid to exit through the port.
  • the active inlet port is provided with an active inlet port bypass passage 18 around the inlet port, allowing the refrigerant to flow around both sides of the inlet port.
  • Each plate comprises a bypass section 115, 215 extending around the entire first inlet port hole.
  • the bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting bypass passage 18 will thus have the height of two times the pressing depth, which means that the friction pressure drop in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage 18 will thus distribute part of the refrigerant from the inlet nozzle to the distribution area around the active inlet port.
  • Part of the refrigerant from the nozzle will also continue in the direction from the nozzle into the corrugation pattern and further towards the second refrigerant inlet port 23, being a passive inlet port. Since the water outlet port holes 112, 212 are positioned at a vertical distance from the lower short end of the plate, a lower horizontal passage 13 is formed in the lower distribution channel between the water outlet port and the lower short end of the heat exchanger. The refrigerant can thus flow below the water outlet port and over to the region around the passive inlet port.
  • the refrigerant flow out of the inlet nozzle has in this example approximately the same angle as the corrugation pattern of the first plate, so that part of the refrigerant can pass mainly in a horizontal direction below the water outlet port with a relatively small friction factor and thus at a relatively high flow rate.
  • a passive inlet port bypass passage 19 around the passive inlet port will facilitate the distribution of the refrigerant to the area around the passive inlet port.
  • the bypass passage 19 around the passive inlet port 23 is created in the same way as at the active inlet port, by each plate comprising a bypass section 117, 217 extending around the entire second inlet port hole.
  • the bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting bypass passage will thus have the height of two times the pressing depth, which means that the friction in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage will thus distribute part of the refrigerant to the distribution area around the passive inlet port.
  • the second inlet port holes 109, 209 are provided with concentric sealing sections 116, 216 that will bear on each other and will thus seal off the passive inlet port.
  • the flat, circular section around the water outlet port holes 112, 212 bear on each other so that the water outlet port is sealed to the refrigerant channel.
  • the water outlet holes are positioned at a vertical distance from the lower short end of each plate.
  • a water outlet hole is larger in diameter than a refrigerant inlet port hole, and the centre of a water outlet hole is positioned closer to the horizontal axis of a plate than the centre of the refrigerant inlet port holes.
  • a lower horizontal passage 13 is created in the refrigerant channel between the water outlet port and the lower short end of the heat exchanger. Through this passage, the refrigerant can pass below the water outlet port to the region around the passive inlet port.
  • the first refrigerant channel is provided with lower distribution paths 15, 16 placed above the active and the passive inlet ports, between the lower distribution passage 10 and the heat exchange passage 11.
  • the lower distribution paths are created by mainly flat distribution grooves 118, 119, 218, 219 pressed in the plates between the V shape of the distribution area and the W shape of the heat exchange area, extending from the long side of a plate to the water outlet port hole.
  • the lower distribution paths will on one hand facilitate the distribution of the refrigerant uniformly into the heat exchange passage 11 and on the other hand act as a transitional region for the V shaped layout of the distribution area and the W shaped layout of the heat exchange area.
  • the height of the lower distribution paths and also the shape may be selected in order to optimise the flow distribution.
  • the height of a pressed groove may in one example be approximately half the pressing depth of a plate.
  • a lower distribution path may also comprise one or more contact points. Since corresponding distribution paths will be created in the water channel, the height of a lower distribution path in the refrigerant channel is preferably not more than a total of one pressing depth.
  • the lower distribution paths will have a low flow resistance in the horizontal direction of the channel, compared to the flow resistance through a flow tube with the same length and width in the corrugated pattern of the heat exchange passage.
  • the lower distribution paths 15, 16 may comprise one or more restriction areas in order to control the flow distribution over the width of the channel in the lower distribution passage.
  • the size and position of the restriction areas are chosen such that the flow through a distribution path 15 or 16 is as evenly distributed as possible.
  • the restrictions may be achieved by altering the pressing depth of the position of the restriction area in the plates, i.e. by altering the height of the restriction area, and/or by altering the width of the restriction area along the lower distribution path. In this way, different restrictions may be positioned at different positions in the lower distribution paths 15, 16. The restrictions will give a locally increased flow resistance that will provide a flow distribution over the width of the lower distribution paths.
  • the restrictions cover most of the distribution paths, thereby creating one or a few small openings between the distribution passage and the heat exchange passage.
  • the size and positions of the restrictions may be decided on by experiments or by calculations. The distribution of the refrigerant flowing into the heat exchange passage will thus be improved.
  • the refrigerant After entering the active inlet port 21 and being distributed in the lower distribution passage 10, the refrigerant will enter and pass the heat exchange passage 11 created between the heat exchange areas 103, 203.
  • the heat exchange passage with all the contact points between the corrugated patterns of the two plates, provides a large heat exchange area and a relatively high friction flow resistance, which ensures an efficient heat transfer between the refrigerant and the water channels.
  • the W shape increases the friction pressure drop somewhat in the heat exchange passage compared with a single V shape, which improves the total heat transfer of the heat exchanger.
  • the upper distribution path will allow the refrigerant flow to distribute and at the same time to even out the differences in pressure, that may arise in the heat exchange passage due to variations of the evaporation of the refrigerant, prior to entering the upper distribution passage created between the upper distribution areas 104, 204 of the plates.
  • the upper distribution path will have a low flow resistance in the horizontal direction of the heat exchanger, which will facilitate the distribution of the refrigerant before entering the upper distribution passage 12.
  • each distribution groove is approximately half the pressing depth of a plate, since a corresponding horizontal distribution path will be created in the water channel. This will give the upper distribution path a total height of one pressing depth.
  • the refrigerant being to a large degree in an evaporated state, enters the upper distribution passage created by the upper distribution areas 104, 204 of the plates.
  • the second refrigerant outlet port holes 110, 210 are provided with concentric sealing sections 122, 222 that will bear on each other and seal the second outlet port 24, being a passive outlet port.
  • a bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting bypass passage 20 will thus have the height of two times the pressing depth, which means that the flow resistance in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage will thus allow a considerable part of the refrigerant, which may be superheated, to pass mainly horizontally over to the active outlet port via the horizontal passage above the water inlet port.
  • the water inlet port holes are positioned at a vertical distance below the upper short end of each plate.
  • the centre of a water inlet hole is positioned closer to the horizontal axis of a plate than the centre of the refrigerant outlet port holes.
  • an upper horizontal passage 14 is provided in the refrigerant channel between the water inlet port and the upper short end of the heat exchanger. Through this horizontal passage, the refrigerant can flow above the water inlet port from the bypass passage 20 at the passive outlet port 24 to the active outlet port 22 formed between the first refrigerant outlet port holes 108, 208.
  • this horizontal passage prevents vapour to cumulate around the passive outlet port which would lead to an insulating area with vapour standing still in the area around the passive outlet port.
  • the passage will also enlarge the total effective heat transfer area of the heat exchanger by the region around the passive outlet port.
  • a water channel 3 is created.
  • the water will enter the water channel through the water inlet port 42 created by the water inlet port holes 211, 311.
  • the water will leave the water channel through the water outlet port 43 created by the water outlet port holes 212, 312. All the refrigerant ports will be sealed so that the water and refrigerant will not mix.
  • the bypass sections 215, 315 will bear on each other and will thus seal the first refrigerant inlet port.
  • the same applies for the bypass sections 217, 317 and the bypass sections 221, 321 which will also bear on each other so that the second refrigerant inlet port and the second refrigerant outlet port are sealed.
  • the first refrigerant outlet port is sealed by the flat sections 223, 323 around the first refrigerant outlet port holes 208, 308 bearing on each other.
  • the water inlet holes 211, 311 are positioned at a vertical distance from the upper short end of each plate edge of each plate.
  • the centre of a water inlet hole is positioned closer to the horizontal axis of a plate than the centre of the refrigerant outlet port holes.
  • an upper horizontal passage 34 is created in the water channel between the water inlet port and the upper short end of the heat exchanger. This enlarges the useful water inlet cross flow area which in turn improves the water distribution in the upper distribution passage and decreases the pressure drop of the water channel.
  • the water channel is provided with upper water bypass passages 40, 41 between the passive second and first refrigerant outlet ports and the upper corners of the heat exchanger.
  • the upper water bypass passages 40, 41 are created by water bypass sections 226, 227, 326, 327 outside each one of the second and first refrigerant outlet port holes. These bypass sections bear on each other when the plates are positioned to create a refrigerant channel, which means that the water bypass passages will have a height of two times the pressing depth. These water bypass passages will thus have a low friction pressure drop and will considerably facilitate water side distribution over the entire upper distribution passage.
  • the water passes horizontal flat distribution grooves 220, 320 pressed in each plate, creating an upper horizontal distribution path 37 in the water channel.
  • This distribution path allows for an additional distribution of the water so that the water pressure along the entire upper distribution path is substantially equal.
  • the upper distribution path also acts as the transitional region between the V shape of the upper distribution passage and the W shape of the heat exchange passage.
  • the height of each distribution groove is approximately half the pressing depth of a plate. This will give the upper distribution path a height of a total of one pressing depth.
  • the heat exchange passage With all the contact points between the corrugated patterns of the two plates, provides a large heat exchanger area and a relatively high friction factor, which ensures an efficient heat transfer between the water and the refrigerant channels.
  • the W shaped layout increases the friction factor somewhat in the heat exchange passage in relation to a single V layout, which will improve the heat transfer.
  • the water When the water has passed the heat exchange passage 31, it enters the lower distribution passage 30 through two lower distribution paths 35, 36 positioned between the heat exchange passage and the lower distribution passage.
  • These lower distribution paths are created by mainly flat distribution grooves 218, 219, 318, 319 pressed in the plates between the V shape of the distribution area and the W shape of the heat exchange area, extending from the long side of a plate to the water outlet port hole.
  • These distribution paths will both facilitate to distribute the water uniformly into the lower distribution passage and act as a transitional region for the W shaped layout of the heat exchange passage and the V shaped layout of the lower distribution passage.
  • the height of the lower distribution paths and also the shape may be selected in order to optimise the flow distribution.
  • the height of a pressed groove may in one example be approximately half the pressing depth of a plate.
  • a lower distribution path may also comprise one or more contact points.
  • the distribution paths will have a low flow resistance in the horizontal direction of the heat exchanger, compared to the flow resistance through the corrugated pattern in the lower distribution passage. This will facilitate an even flow distribution of the water into the lower distribution passage.
  • the lower distribution passage 30 is provided with lower water bypass passages 38, 39 between the passive first and second refrigerant inlet ports and the lower corners of the heat exchanger.
  • the lower water bypass passages are created by water bypass sections 224, 225, 324, 325 at each one of the first and second refrigerant inlet port holes. These bypass sections bear on each other when the plates are positioned to create a refrigerant passage, which means that the lower water bypass passage will have a height of two times the press depth. These lower water bypass passages will thus have a low friction pressure drop and will contribute considerably to the guiding of the water flow to the water outlet port.
  • the water outlet port holes are positioned at a vertical distance from the lower short end of each plate. In this way, a lower horizontal passage 33 is created in the water channel between the water outlet port and the lower short end of the heat exchanger. Through this horizontal passage, the water can flow into the water outlet port also from below the port, improving the efficiency of the heat exchanger.
  • the lower bypass passages together with the upward offset of the water outlet port improve the outlet flow distribution of water considerably and decreases the outlet pressure drop all around the port periphery by enlarging the useful water cross flow area.
  • the second refrigerant channel 4 is created between the third plate 301 and the fourth plate 401 when they are positioned next to each other and resembles the first refrigerant channel.
  • the difference between the first refrigerant channel and the second refrigerant channel are only the inlet and outlet ports and the inlet nozzle.
  • the refrigerant will enter the second refrigerant channel through a second refrigerant inlet port 63, being an active inlet port, created by the refrigerant inlet port holes 309, 409.
  • the inlet port holes 309, 409 are provided with concentric sealing sections 316, 416 that will bear on each other.
  • the inlet into the second refrigerant channel is provided by an inlet nozzle 65 through the sealing sections.
  • the inlet nozzle is obtained by nozzle indentation 314, 414 in one or both of the sealing sections.
  • the size of the inlet nozzle, i.e. the length and the cross section, together with the angular position of the inlet nozzle are both important for the refrigerant distribution in the lower distribution passage 50 created between the lower distribution areas 302 and 402.
  • the size of the inlet nozzle is selected partly depending on the pressure drop of the refrigerant circuit and is selected to obtain an even flow distribution over all refrigerant channels in the refrigerant circuit in a complete heat exchanger.
  • the angular position of the inlet nozzle is chosen such that the refrigerant can distribute evenly over the total width of the heat exchanger in each refrigerant channel.
  • the inlet nozzle may be directed in any chosen angle, depending e.g. on the corrugated pattern layout in the lower distribution passage and the bypass section around the inlet port.
  • the angle of the inlet nozzle is between 0 and 180 degrees relative a vertical axis and pointing towards the central vertical axis of the plate, and more preferably between 90 and 150 degrees.
  • the active inlet port is provided with an active inlet bypass passage 59 around the inlet port, allowing the refrigerant to flow around both sides of the inlet port.
  • Each plate comprises a bypass section 317, 417 extending around the entire inlet port hole.
  • the bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting active inlet bypass passage will thus have the height of two times the pressing depth, which means that the friction in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage will thus distribute part of the refrigerant from the inlet nozzle to the distribution area around the active inlet port.
  • Part of the refrigerant from the nozzle will also continue in the direction from the nozzle into the corrugation pattern in the direction towards the first refrigerant inlet port 61, being a passive inlet port. Since the water outlet port holes 312, 412 are positioned at a vertical distance from the lower short end of each plate, a lower horizontal passage 53 is formed in the lower distribution channel between the water outlet port and the lower short end of the heat exchanger. The refrigerant can thus flow below the water outlet port to the region around the passive inlet port.
  • the refrigerant flow out of the inlet nozzle has in this example approximately the same angle as the corrugation pattern of the third plate, so that part of the refrigerant can pass mainly in a horizontal direction below the water outlet port with a relatively small friction factor and thus a relatively high flow rate.
  • a bypass passage 58 around the passive inlet port will help distribute the refrigerant to the area around the passive inlet port.
  • the bypass passage 58 is created in the same way as at the active inlet port, by each plate comprising a bypass section 315, 415 extending around the entire first refrigerant inlet port hole.
  • a bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting bypass passage will thus have the height of two times the pressing depth, which means that the friction in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage will thus distribute part of the refrigerant to the distribution area around the passive inlet port.
  • the first inlet port holes 307, 407 are provided with concentric sealing sections 313, 413 that will bear on each other and will thus seal off the passive inlet port.
  • the flat, circular section around the water outlet port holes 312, 412 bear on each other so that the water outlet port is sealed to the refrigerant channel.
  • the water outlet port holes are positioned at a vertical distance from the lower short end of each plate.
  • a water outlet hole is larger in diameter than a refrigerant inlet port hole, and the centre of a water outlet hole is positioned closer to the horizontal axis of a plate than the centre of the refrigerant inlet port holes.
  • a lower horizontal passage 53 is created in the refrigerant channel between the water outlet port and the lower short end of the heat exchanger. Through this horizontal passage, the refrigerant can pass below the water outlet port to the region around the passive inlet port. This improves the distribution of refrigerant considerably over the plate width, which gives a more uniform flow through the heat exchange passage and also enlarges the total effective heat transfer area of the heat exchanger with the region around the passive inlet port.
  • the second refrigerant channel is provided with lower distribution paths 55, 56 placed above the passive and the active inlet ports, between the lower distribution passage 50 and the heat exchange passage 51.
  • the lower distribution paths are created by mainly flat distribution grooves 318, 319, 418, 419 in the plates between the V shape of the distribution area and the W shape of the heat exchange area, extending from the long side of a plate to the water outlet port hole.
  • the lower distribution paths will on the one hand facilitate the uniform distribution of the refrigerant into the heat exchange passage 51 and on the other hand act as a transitional region for the V shaped layout of the distribution area and the W shaped layout of the heat exchange area.
  • the height of the lower distribution paths and also the shape may be selected in order to optimise the flow distribution.
  • the height of a groove may in one example be approximately half the pressing depth of a plate.
  • the lower distribution path may also comprise one or more contact points. Since corresponding distribution paths will be created in the water channel, the height of a lower distribution path in the refrigerant channel is preferably not more than a total of one pressing depth.
  • the lower distribution paths will have a low flow resistance in the horizontal direction of the heat exchanger, compared to the flow resistance through a flow tube with the same length and width in the corrugated pattern of the heat exchange passage.
  • the lower distribution paths 55, 56 may also comprise one or more restriction areas in order to control the flow distribution over the channel width in the lower distribution passage. The restrictions may be fairly small, resembling one or more contact points, or they may be relatively large, such that only one or a few small passages are created between the distribution passage and the heat exchange passage.
  • the refrigerant After entering the active inlet port 63 and being distributed in the lower distribution passage 50, the refrigerant will enter and pass the heat exchange passage 51 in the same way as described for the first refrigerant channel.
  • each plate Between the heat exchange area and the upper distribution area of each plate is a horizontal flat distribution groove 320, 420 pressed in each plate, creating an upper distribution path 57 in the second refrigerant channel.
  • the upper distribution path will allow the differences in pressure that may arise in the heat exchange passage due to variations of the evaporation of the refrigerant to even out before the refrigerant enters the upper distribution passage 52 created between the upper distribution areas 304, 404 of the plates.
  • the refrigerant may at this stage be partly or fully evaporated, and may even be superheated.
  • the upper distribution path will have a low flow resistance in the horizontal direction of the heat exchanger, which will facilitate the distribution of the refrigerant before entering the upper distribution passage.
  • the height of each distribution path is approximately half the pressing depth of a plate, since a corresponding horizontal distribution path will be created in the water channel. This will give the distribution path a height of a total of one pressing depth.
  • the refrigerant being in this cross section to a large degree in vapour form, enters the upper distribution passage 52 created by the upper distribution areas 304, 404 of the plates.
  • the second refrigerant outlet port 64 being an active port, is created between the plates at the second refrigerant outlet port holes 310, 410.
  • Part of the refrigerant will enter the upper distribution passage on the left side of the vertical axis 305, and part of the refrigerant will enter the upper distribution passage on the right side of the vertical axis 305.
  • Part of the refrigerant will reach a passive outlet port bypass passage 60 created by bypass sections 323, 423 extending around the entire first refrigerant outlet port 62, being a passive outlet port.
  • the first refrigerant outlet port holes 308, 408 are provided with concentric sealing sections 328, 428 that will bear on each other and seal the first outlet port.
  • a bypass section has the same pressing depth as the corrugations of the plate.
  • the resulting bypass passage will thus have the height of two times the pressing depth, which means that the friction in the bypass passage will be much smaller than through the corrugation pattern.
  • the bypass passage will thus allow a considerable part of the refrigerant, which may be superheated, to pass over to the active outlet port via the cross corrugation pattern passage above the water inlet port.
  • the water inlet port holes are positioned at a vertical distance from the upper short end of each plate.
  • the centre of a water inlet hole is positioned closer to the horizontal axis of a plate than the centre of the refrigerant outlet port holes.
  • an upper horizontal passage 54 is provided in the refrigerant channel between the water inlet port and the upper short end of the heat exchanger.
  • the refrigerant can flow above the water inlet port from the bypass passage 60 at the passive outlet port 62 to the active outlet port 64 formed between the second refrigerant outlet port holes 310, 410. This improves the flow distribution of refrigerant considerably in the upper distribution passage and prevents heat congestion around the passive outlet port. Further, the total effective heat transfer area of the heat exchanger is enlarged by the region around the passive outlet port.
  • an improved three-circuit plate heat exchanger can be obtained, which shows a considerable improvement in the overall thermal performance of the heat exchanger. This is due to the improved flow distribution in the heat exchanger.
  • the invention is not to be regarded as being limited to the embodiments described above, a number of additional variants and modifications being possible within the scope of the subsequent claims.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Claims (19)

  1. Dauerhaft verbundene Wärmetauscherbaugruppe, umfassend Wärmetauscherplatten (101; 201; 301; 401) zur Verwendung in einer Dreikreis-Wärmetauscherbaugruppe (1) für mindestens ein Kältemittel, wobei die Platten einen ersten Verteilungsbereich (102; 202; 302; 402) mit drei Anschlusslöchern (107, 109, 112; 207, 209, 212; 307, 309, 312; 407, 409, 412), einen Wärmeaustauschbereich (103; 203; 303; 403) und einen zweiten Verteilungsbereich (104; 204; 304; 404) mit drei Anschlusslöchern (108, 110, 111; 208, 210, 211; 308, 310, 311; 408, 410, 411) umfassen, wobei die Platten ein geriffeltes Muster mit Rippen und Tälern umfassen und eine untere Verteilungsrille (118, 119; 218, 219; 318, 319; 418, 419) zwischen dem ersten Verteilungsbereich und dem Wärmeaustauschbereich bereitgestellt ist, sodass ein unterer Verteilungsweg zwischen zwei angrenzenden unteren Verteilungsrillen erlangbar ist, wenn zwei Platten gestapelt werden, um einen Fluidkanal zwischen den Platten zu bilden,
    dadurch gekennzeichnet, dass ein zentrales Anschlussloch (112; 212, 312; 412) des ersten Verteilungsbereichs in einem senkrechten Abstand vom kurzen Ende der Platten angeordnet ist, sodass die Mitte des zentralen Anschlusslochs (112; 212, 312; 412) näher an der waagerechten Achse einer Platte angeordnet ist als die Mitte eines Kühlmittelanschlusslochs (107, 109, 207, 209, 307, 309, 407, 409), sodass ein Fluiddurchgang zwischen dem zentralen Anschlussloch und dem kurzen Ende der Platten erlangbar ist, wenn zwei Platten gestapelt werden, um einen Fluidkanal dazwischen auszubilden, und dass ein zentrales Anschlussloch (111; 211; 311; 411) des zweiten Verteilungsbereichs in einem senkrechten Abstand vom kurzen Ende der Platten angeordnet ist, sodass ein Fluiddurchgang zwischen dem zentralen Anschlussloch und dem kurzen Ende der Platten erlangbar ist, wenn zwei Platten gestapelt werden, um einen Fluidkanal dazwischen auszubilden,
    worin die Wärmetauscherplatten (101; 201; 301; 401) durch Löten, Hartlöten oder Schweißen miteinander verbunden sind.
  2. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 1, dadurch gekennzeichnet, dass ein Anschlussloch (107, 109, 110; 207, 209, 210; 307, 308, 309; 407, 408, 409) an einer Ecke der Platten mit einem flachen, ringförmigen Umleitungsabschnitt (115, 117, 121; 215, 217, 221; 315, 317, 323; 415, 417, 423) versehen ist, der dafür eingerichtet ist, einen Kältemittel-Umleitungsdurchgang rings um einen Anschluss herum auszubilden, wenn zwei Platten gestapelt werden, um einen Kältemittel-Fluidkanal zwischen den Platten zu bilden.
  3. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein Wasser-Umleitungsabschnitt (124, 125, 126, 127; 224, 225, 226, 227; 324, 325, 326, 327; 424, 425, 426, 427) an einer Ecke der Platten bereitgestellt ist, sodass ein Wasserdurchgang zwischen zwei angrenzenden Umleitungsabschnitten erlangbar ist, wenn zwei Platten gestapelt werden, um einen Wasserkanal zwischen den Platten zu bilden.
  4. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der erste Verteilungsbereich (102; 202; 302; 402) eine Zickzackform mit einem ersten Layout aufweist, der zweite Verteilungsbereich (104; 204; 304; 404) eine Zickzackform mit einem zweiten Layout aufweist und wobei der Wärmeaustauschbereich (103; 203; 303; 403) eine Zickzackform mit einem dritten Layout aufweist, wobei die Zickzackform des ersten Layouts in eine erste Winkelrichtung gerichtet ist und die Zickzackform des zweiten Layouts in die entgegengesetzte Winkelrichtung gerichtet ist.
  5. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 4, dadurch gekennzeichnet, dass die Zickzackform des dritten Layouts in die gleiche Winkelrichtung wie die Zickzackform des ersten Layouts gerichtet ist.
  6. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 4 bis 5, dadurch gekennzeichnet, dass die Zickzackform des dritten Layouts mehr Richtungsänderungen aufweist als das erste und das zweite Layout.
  7. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass die erste und die zweite Zickzackform einem V ähneln und die dritte Zickzackform einem W ähnelt.
  8. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die untere Verteilungsrille (118, 119; 218, 219; 318, 319; 418, 419) mindestens einen Einengungsbereich umfasst, sodass eine Strömungseinengung im unteren Verteilungsweg erlangt wird.
  9. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass eine obere Verteilungsrille (120; 220; 320; 420) zwischen dem Wärmeaustauschbereich und dem zweiten Verteilungsbereich bereitgestellt ist, sodass ein oberer Verteilungsweg zwischen zwei angrenzenden oberen Verteilungsrillen erlangbar ist, wenn zwei Platten gestapelt werden, um einen Fluidkanal zwischen den Platten zu bilden.
  10. Dauerhaft verbundene Wärmetauscherbaugruppe, umfassend vier Platten nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die erste Platte (101), die zweite Platte (201), die dritte Platte (301) und die vierte Platte (401) sich voneinander unterscheiden.
  11. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 10, wobei ein erster Kältemittelkanal (2) zwischen den ersten Platten (101) und den zweiten Platten (201) bereitgestellt ist, ein Wasserkanal (3) zwischen den zweiten Platten (201) und den dritten Platten (301) bereitgestellt ist und ein zweiter Kältemittelkanal (4) zwischen den dritten Platten (301) und den vierten Platten (401) bereitgestellt ist, und wobei jeder Fluidkanal (2, 3, 4) einen ersten Verteilungsdurchgang (10; 30; 50), der zwischen zwei angrenzenden ersten Verteilungsbereichen (102, 202, 302, 402) bereitgestellt ist, einen Wärmeaustauschdurchgang (11; 31; 51), der zwischen zwei angrenzenden Wärmeaustauschbereichen (103, 203, 303, 403) bereitgestellt ist, und einen zweiten Verteilungsdurchgang (12; 32; 52), der zwischen zwei angrenzenden zweiten Verteilungsbereichen (104, 204, 304, 404) bereitgestellt ist, umfasst, dadurch gekennzeichnet, dass ein waagerechter Durchgang (13; 33; 53) in dem ersten Verteilungsdurchgang zwischen dem zentralen Wasseranschluss (43) und dem benachbarten kurzen Ende der Baugruppe bereitgestellt ist.
  12. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 10 oder 11, dadurch gekennzeichnet, dass ein waagerechter Durchlass (14; 34; 54) in den zweiten Verteilungsdurchgängen (12; 32; 52) zwischen dem zentralen Wasseranschluss (42) und dem benachbarten kurzen Ende der Baugruppe bereitgestellt ist.
  13. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 10 bis 12, dadurch gekennzeichnet, dass ein Wasser-Umleitungsdurchgang (38, 39, 40, 41) in einem Wasserverteilungsdurchgang (30, 32) zwischen einem Kältemittelanschluss (21, 22, 23, 24; 61, 62, 63, 64) und einer Ecke der Baugruppe bereitgestellt ist.
  14. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 10 bis 13, dadurch gekennzeichnet, dass ein Kältemittel-Umleitungsdurchgang (18, 19, 20; 58, 59, 60) rings um einen Kältemittelanschluss (21, 23, 24; 61, 62, 63) in einem Kältemittel-Verteilungsdurchgang (10, 12; 50, 52) bereitgestellt ist.
  15. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 10 bis 14, dadurch gekennzeichnet, dass der aktive Einlassanschluss (21) mit einer Einlassdüse (25) versehen ist und der aktive Einlassanschluss (63) mit einer Einlassdüse (65) versehen ist, wobei der Winkel der Einlassdüsen zwischen 0 und 180 Grad relativ zu einer senkrechten Achse liegt und die Einlassdüse auf die zentrale senkrechte Achse der Baugruppe zeigt.
  16. Dauerhaft verbundene Wärmetauscherbaugruppe nach Anspruch 15, dadurch gekennzeichnet, dass der Winkel der Einlassdüsen zwischen 90 und 150 Grad liegt.
  17. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 10 bis 16, dadurch gekennzeichnet, dass ein unterer Verteilungsweg (15, 16; 35, 36; 55, 56) zwischen einem unteren Verteilungsdurchgang (10, 30, 50) und einem Wärmeaustauschdurchgang (11, 31, 51) bereitgestellt ist.
  18. Dauerhaft verbundene Wärmetauscherbaugruppe nach einem der Ansprüche 10 bis 17, dadurch gekennzeichnet, dass ein oberer Verteilungsweg (17, 37, 57) zwischen einem Wärmeaustauschdurchgang (11, 31, 51) und einem oberen Verteilungsdurchgang (12, 32, 52) bereitgestellt ist.
  19. Dauerhaft verbundener Dreikreis-Wärmetauscher, eine Vielzahl von Wärmetauscherbaugruppen nach einem der Ansprüche 10 bis 18 umfassend und ferner eine Frontplatte und eine Rückplatte umfassend.
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SE0801394A SE532524C2 (sv) 2008-06-13 2008-06-13 Värmeväxlarplatta samt värmeväxlarmontage innefattandes fyra plattor
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EP2307842A1 (de) 2011-04-13
PT2307842T (pt) 2022-11-28
DK2307842T3 (da) 2023-01-23
EP2307842A4 (de) 2014-04-02
BRPI0913116A2 (pt) 2016-01-05
CN102084203A (zh) 2011-06-01
KR20110005913A (ko) 2011-01-19
CN102084203B (zh) 2013-07-24
RU2457416C1 (ru) 2012-07-27
JP5553828B2 (ja) 2014-07-16
SE532524C2 (sv) 2010-02-16
SE0801394L (sv) 2009-12-14
KR101263559B1 (ko) 2013-05-14
US20110083833A1 (en) 2011-04-14
PL2307842T3 (pl) 2022-12-27
WO2009151399A1 (en) 2009-12-17
JP2011523025A (ja) 2011-08-04

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