SE532524C2 - Heat exchanger plate and heat exchanger assembly include four plates - Google Patents

Description

Of each passage for the remaining two liquids. The passages are created using two different plate types. A good seal between adjacent plates at the openings that creates inlet and outlet channels for the three liquids is created by designing the areas around the openings, so that a system of annular, flat areas is. Niered.

EP 1062472 B shows another example of a three-circuit heat exchanger. This design is mainly about joining the opening holes in an airtight manner.

EP 0965025 B describes a plate heat exchanger for three heat exchanging liquids.

The opening holes of the heat exchanger are intended in pairs for the flow of respective heat exchanging liquid and the opening holes are symmetrically arranged on both sides of a heat transfer part in such a way that a straight line drawn through the center of the opening holes divides the heat transfer part into two equal parts.

These heat exchangers work really well in some applications. There is still room for improvement on existing heat exchangers.

DESCRIPTION OF THE INVENTION An object of the invention is thus to provide an improved heat exchanger with an improved fate distribution in each flow circuit. A further object of the invention is thus to provide a heat exchanger with an improved heat transfer coefficient.

The solution to the problem according to the invention is stated in the characterizing part of claim 1. Claims 2 - 11 contain preferred embodiments of the heat exchanger plate. Claims 12 to 21 contain preferred embodiments of a heat exchanger assembly. Claim 22 contains a preferred heat exchanger. 10 15 20 25 30 532 524 With a heat exchanger plate for use in a three-circuit heat exchanger assembly, the plate comprising a first distribution area with three opening holes, a heat transfer area and a second distribution area with three opening holes, the plate comprising a corrugated pattern with axes and valleys, the purpose of the opening is achieved by placing the middle opening hole in the first distribution area at a vertical distance from the short side of the plate so that a fate passage is obtained between the middle opening hole and the short side of the plate when two plates are stacked to form a flow channel in between.

With this first embodiment of the plate for a heat exchanger assembly, a heat exchanger plate is obtained which enables an improved fate distribution in the first distribution passage for the coolant circuits. The advantage of this is that a larger part of the heat exchanger plate, i.e. the area around the passive inlet opening can also be used as an effective heat transfer surface.

Another advantage is that the flow distribution of the liquid 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 fate in the liquid circuit and into the liquid outlet opening is also improved. The efficiency of the heat exchanger will thus be improved.

In an advantageous further development of the inventive plate, the middle opening hole in the second distribution area is placed with a vertical distance from the short side of the plate so that a flow passage is obtained between the middle opening hole and the short side of the plate when two plates are stacked to form a desert channel. . The advantage of this is that a larger part of the heat exchanger plate, i.e. the area around the passive outlet opening can also be used as an effective heat transfer surface. Another advantage is that the fate distribution of the liquid from the inlet opening is improved, which in turn improves the liquid fate distribution in the heat transfer passage. The efficiency of the heat exchanger will thus be further improved. 10 15 20 25 30 532 Thus, in an advantageous further development of the inventive plate, at least one corner of the plate is provided with a flat, annular bypass section adapted to form a coolant bypass passage around an opening when two plates are stacked to form a coolant channel between the plates.

This improves the fl distribution of fate in the coolant channels in the heat exchanger. In an advantageous further development of the inventive plate, at least one water bypass section is arranged at a corner of the plate so that a water passage is obtained between two adjacent bypass sections when two plates are stacked to form a water channel between the plates. This improves the des fate distribution in the water channel in the heat exchanger. In a further advantageous further development of the inventive plate, a lower distribution groove is arranged between the first distribution area and the heat transfer area, where the lower distribution groove comprises at least one limiting area, and an upper distribution groove is arranged between the heat transfer area and the upper distribution area. These further developments bring about an improved flow distribution in the heat exchanger. In an advantageous further development of the inventive plate, the first distribution area has a cartilaginous pattern with a first design, the second distribution area has a cartilaginous pattern with a second design and the heat transfer area has a cartilaginous pattern with a third design, where the first cartilage pattern where the second design of the herringbone pattern is directed in an opposite angular direction. This provides an improved heat transfer in the heat exchanger. In a heat exchanger assembly comprising four heat exchanger plates according to the invention, the purpose of the heat is achieved in that the first plate, the second plate, the third plate, the third plate and the fourth plate differ from each other. In an advantageous further development of the inventive assembly, where a first coolant channel is arranged between the first plate and the second plate, a water channel is arranged between the second plate and the third plate and a second coolant channel is arranged between the third plate and the fourth plate. , and wherein each fl fate channel comprises a first distribution passage arranged between two adjacent first distribution areas, where a heat transfer passage is arranged between two adjacent heat transfer areas and where a second distribution passage is arranged between two adjacent second distribution areas, where a horizontal in the first distribution passage between the middle water opening and the short side of the assembly. This is advantageous in that the horizontal passage will improve fl fate distribution in the first distribution passage, which in turn improves fl fate distribution in the heat transfer passage. This allows a larger portion of the heat transfer plate, i.e. the area around the passive inlet opening, to function as an effective heat transfer surface. Another advantage is that the liquid flow in the liquid circuit is improved since the entire liquid outlet opening is open. The efficiency of the heat exchanger is thus improved. In an advantageous further development of the inventive assembly, a horizontal passage is arranged in the second distribution passage between the middle water opening and the adjacent short side of the assembly. The advantage of this is that a larger part of the heat transfer plate, i.e. the area around the passive outlet opening, can also be used as an effective heat transfer surface. Another advantage is that the flow distribution of the liquid from the inlet opening is improved, which in turn improves the liquid distribution distribution in the heat transfer passage. The efficiency of the heat exchanger is thus further improved. 10 15 20 25 30 532 524 In an advantageous further development of the assembly according to the invention, a water bypass is arranged in a water distribution passage between a coolant opening and a corner of the assembly. This is advantageous by obtaining a water bypass, which significantly improves the water distribution in the heat exchanger.

In an advantageous further development of the inventive assembly, a coolant bypass is arranged around a coolant opening in a coolant distribution passage. This is advantageous in that the fate distribution of coolant is significantly improved.

In an advantageous further development of the inventive assembly, the active coolant inlet opening is provided with an inlet nozzle, where the angle of the inlet nozzle is between 0 and 180 degrees relative to a vertical axis and where the inlet nozzle is directed towards the central vertical axis of the assembly. In this way, the inlet nozzle points towards the center of the heat exchanger, which improves the fate distribution in the heat exchanger. In an advantageous further development of the inventive assembly, a lower distribution channel is arranged between a lower distribution passage and a heat transfer passage. This is advantageous in that the fate distribution in the lower distribution passage can be controlled in a more detailed manner, so that the fate into the heat transfer passage can be made as even as possible.

In an advantageous further development of the inventive assembly, the lower distribution channel comprises at least one limiting means so that a flow limitation is obtained in the lower distribution passage. This is advantageous in that the fate distribution in the lower distribution passage can be controlled in a more detailed manner. so that the in fate into the heat transfer passage becomes as even as possible. 10 15 20 25 30 532 5211 In an advantageous further development of the inventive assembly, an upper distribution channel is arranged between the heat transfer passage and the upper distribution passage. This is advantageous in that the flow distribution into the upper distribution passage can be further evened out. In a three-circuit heat exchanger, comprising a number of heat exchanger-compatible heat exchangers and further comprising at least one front plate and a back plate, an improved heat exchanger is obtained.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be described in more detail in the following, with reference to the embodiments shown in the accompanying drawings, in which: Fig. 1 shows a heat exchanger plate assembly according to the invention, Fig. 2 shows a first heat exchanger plate for use in a heat exchanger plate assembly according to the invention, Fig. 3 shows a second heat exchanger plate for use in a heat exchanger plate assembly according to the invention, Fig. 4 shows a third heat exchanger plate for use in a heat exchanger plate assembly according to the invention, and Fig. 5 shows a fourth heating plate use in a heat exchanger plate assembly according to the invention.

METHODS OF PRACTICE OF THE INVENTION The embodiments of the invention with further developments which are described in the following are to be considered as examples only and do not in any way constitute a limitation of the scope of protection provided by the claims. In the examples below, water is used as an example of a liquid to be cooled or heated. The liquid to be cooled or heated is adapted for use in a single phase, in a purely fl superficial state. The design of the heat exchanger is thus adapted to a single-phase liquid for the water circuit.

Of course, it is also possible to use other liquids, such as different mixtures of water and other liquids, e.g. for the purpose of preventing freezing or corrosion. A coolant is used as an example of a liquid to be evaporated or condensed. This liquid is advantageously used in two phases, a liquid phase and a vapor phase, but it is possible to use the liquid only in a single phase, either in a liquid state, a vapor state or a mixture.

The design of the heat exchanger is thus adapted for a two-phase liquid in the other liquid circuits.

The invention relates to plate protection exchangers with three separate channels which enable three different liquid circuit circuits. One of the channels is adapted to conduct a single-phase liquid to be heated or cooled. In this application, water is used as an example of such a liquid. The other two ducts are adapted to conduct a two-phase coolant that is adapted to evaporate or condense in the heat exchanger. The channels can either be connected so that one coolant is common to both circuits or the channels can be separated so that different coolants can be used in each circuit. In this application, a two-phase saturated liquid is used, which is in a slightly pressurized state when it fl pours into the heat exchanger and which will evaporate in the heat exchanger, as an example of a coolant.

Furthermore, in the example described, the plate heat exchanger is of the permanently joined type, i.e. the plates are brazed, glued, bonded, soldered or welded together to form a complete heat exchanger. 10 15 20 25 30 532 5241? The plate heat exchanger comprises a number of heat exchanger assemblies, each assembly comprising four different heat exchanger plates. It is also possible to use different types of seal, e.g. gaskets between the plates, welded plates or semi-welded plate units with gaskets between every other plate.

The heat exchanger plates are formed by using two equal pressing tools so that two different plate types are obtained, a first plate type having a bony pattern in one direction and a second plate type having a herringbone pattern in the opposite direction. The design comprises a corrugated pattern consisting of ridges and valleys which extend across the plates in a crescent pattern with angular change points along longitudinal lines dividing the width of the plate into equal parts. The corrugated pattern together with the fi leg pattern is arranged to give the pattern many intersection points when the plates are stacked on top of each other, to create a strong and stable heat exchanger with an efficient heat transfer. Corrugated patterns and designs such as these are well known to those skilled in the art. It is also possible to use corrugated patterns with the same angle over the entire surface, i.e. which have no angular change points.

Each plate type is run in a second working step through one or more additional pressing / punching steps so that four different plates are obtained. In the further working steps, the areas at the opening holes of the plates are pressed and punched to their final shape and the recess of the nozzles is formed.

The formed plates, including a first plate 101, a second plate 201, a third plate 301 and a fourth plate 401 are stacked so as to form a heat exchanger plate assembly. The plates are stacked so that every other plate is of the same plate type if one disregards the size and shape of the areas at the opening holes and the nozzles. The areas at the opening holes differ between the plates, which will be described below. It is also possible to give the first and the second plate type different angles on the skeletal pattern.

The pattern of the first plate type can thus have a slightly smaller angle and the pattern of the second plate type can have a slightly larger angle, so that the average value of the angles corresponds to the desired angular value of the plates.

Each heat exchanger plate comprises a first or lower distribution area comprising three opening holes, a central heat transfer area and a second or upper distribution area comprising three opening holes. Each plate has a longitudinal axis or vertical axis and a transverse axis or horizontal axis.

The opening holes of the first distribution area are arranged symmetrically with respect to the longitudinal axis. The opening holes of the second distribution area are also symmetrically arranged with respect to the longitudinal axis. The opening holes of the first and the second distribution area can be arranged symmetrically with respect to each other. In an advantageous embodiment, the opening holes of the first and the second distribution area are not arranged symmetrically with respect to each other, since the opening holes adapted for a vaporized phase of the coolant have a larger diameter than the opening holes adapted for a destructive liquid-gas mixture of the coolant, and the opening holes are placed at approximately the same distance from the corners of the plates. In this embodiment, the opening holes in the second distribution area are adapted for the refrigerant in the gas phase and the opening holes in the first distribution area are adapted for the liquid coolant.

In an example, the friend changer is intended to be used for solid evaporator on the duct side of the coolant and cooling on the water side in a countercurrent fate arrangement. Below, a heat exchanger is used which is used for evaporation to illustrate the invention. The references in the description will therefore refer to the geometry of such a vertically standing heat exchanger. It is also possible to use the heat exchanger placed in other ways, e.g. placed at different angles around the horizontal axis. The coolant two-phase liquid can consist of a mixture of liquid and gas when entering the heat exchanger and can be completely evaporated, and even overheated, when exiting the heat exchanger. The heat exchanger can also be used with the water and the coolant flowing in the same direction, i.e. in a downstream fl fate. The described heat exchanger is adapted for a diagonal fate of the coolant, i.e. the coolant flows into the heat exchanger through an opening in a lower corner of the heat exchanger and leaves the heat exchanger through an opening in the opposite upper corner. It is of course also possible to adapt the heat exchanger to a parallel fate, where the coolant flows into the heat exchanger through an opening in a lower corner of the heat exchanger and leaves the heat exchanger through an opening in the upper corner on the same side, by adjusting the inlet and the outlet openings in a suitable manner.

The heat exchanger can also be used for falling film coolant condensation with heating of the water side in a countercurrent or cocurrent fl fate arrangement. The biphasic coolant may be in an overheated or saturated gas state as it flows into the heat exchanger through the upper distribution passage and may be partially or completely condensed and even subcooled as it leaves the heat exchanger through the lower coolant orifice. The heat exchanger can also be used as a cooler for superheated steam or gas cooler in a single-phase heat transfer, or as a preheater for evaporation and other similar areas of use, depending on the needs of the installation. Depending on the use, small changes may need to be made to the tile design.

The first heat exchanger plate 101, shown in Figure 2, includes a first or lower distribution area 102, a heat transfer area 103 and a second or upper distribution area 104. The plate has a longitudinal axis or vertical axis 105 and a transverse axis or horizontal axis 106. The lower distribution area 102 is provided with a first coolant inlet opening hole 107, a water outlet opening hole 112 and a second coolant inlet opening hole 109. The first coolant inlet opening hole 107 is provided with a nozzle recess 114.

It is to be understood that the entire surface of the heat exchanger plate where there is a liquid passage on the other side of the plate is a heat transfer area. The heat transfer area 103 is therefore referred to as a heat transfer area because its main purpose is heat transfer, although there will be some flow distribution also in the heat transfer area. The lower and upper distribution areas have the dual purpose of both fl fate distribution and heat transfer.

The design of the first distribution area 102 exhibits a simple tibial pattern, i.e. a V-pattern, where the angular change point is centrally located on the plate so that the first distribution area is divided into two equal parts. The design of the angle of the V-pattern is advantageously between 50 and 70 degrees with respect to the vertical axis of the heat exchanger.

The inner angle of the V-pattern is thus between 100 and 140 degrees. Other angles are conceivable but it is advantageous that the inner angle is obtuse. By giving the skeletal pattern a relatively small angle with respect to the horizontal axis, the friction factor in the horizontal direction of the lower distribution channel becomes relatively small, which will facilitate the distribution of coolant over the width of the plate.

The heat transfer area 103 is provided with a corrugated pattern which has a velcro pattern, i.e. a W-pattern, which has three angular change points which divide the heat transfer area into four equal parts.

The inner angle of the skeletal pattern is of great importance for the friction factor in a channel. With the same inner angle, an advantage of using a W-pattern instead of a V-pattern is that the average friction factor for the heat transfer area is higher than when a V-pattern is used. The heat transfer coefficient is thus higher than for a conventional V-pattern. The use of a W-pattern gives a design with three changes of direction. It is also possible to use a leg pattern with two, four and even more changes of direction. At the transition areas of the fresh bone pattern, i.e. at the direction change points, the horizontal and also the vertical fl velocity velocity component is reduced so that it can become close to zero. For the first plate shown, the pattern is reminiscent of an upside-down W, 10 15 20 25 30 532 SZQ 13 The angle of the corrugated W pattern is advantageously between 50 and 70 degrees with respect to the vertical axis of the heat exchanger. The inside angle of the skeletal pattern is thus between 100 and 140 degrees. The inner angle of the tibial pattern of the heat transfer area may be the same as that of the tibial pattern of the first distribution area, or it may be slightly smaller. Other angles are conceivable, but it is important that the inner angle of the tibial pattern is obtuse. The friction factor for the heat transfer passage depends b | .a. on the inner angle of the skeletal pattern together with the number of changes of direction.

The upper distribution area 104 of the plate is provided with a first coolant outlet opening hole 108, a water inlet opening hole 111 and a second coolant outlet opening hole 110. the pattern may be the same as for the lower distribution area. The inner angle of the skeletal pattern of the lower distribution area, in the heat transfer area and in the upper distribution area may be the same or may be different. In an advantageous embodiment, the cartilage pattern of the lower distribution area and of the heat transfer area is provided with the same inner angle. The herringbone pattern of the upper distribution area in this embodiment is provided with an angle which is smaller with respect to the vertical axis. In a further advantageous embodiment, the cartilage pattern of the lower distribution area is provided with a first angle, the cartilage pattern of the heat transfer area is provided with a second, smaller angle and the cartilage pattern of the upper distribution area is provided with an even smaller angle. Advantageously, the angles are in the range between 50 and 70 degrees. The advantage of having different inner angles for the different areas is that the volume fl fate, when the coolant evaporates, becomes higher in the upper part of the heat exchanger. The different inner angles thus give a lower flow resistance when the volume flow increases with the direction of fate in the channel. The same applies when fl fate is reversed and the heat exchanger is used to condense steam.

A smaller inner angle of the cartilage pattern with respect to the vertical axis gives a lower flow resistance in the direction of fate.

The second heat exchanger plate 201, shown in Figure 3, includes a lower distribution area 202, a heat transfer 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 coolant inlet opening hole 207, a water outlet opening hole 212 and a second coolant inlet opening hole 209. The first coolant inlet opening hole 207 is provided with a nozzle recess 214.

The design of the lower distribution area 202 shows a simple skeletal pattern, i.e. a V-pattern, where the V-pattern resembles an upside-down V. The angular change point is centrally located on the plate so that the first distribution area is divided into two equal parts. Apart from the direction of the fi tibial pattern, the angles of the pattern are the same as for the first plate.

The friend transfer area 203 is provided with a corrugated pattern which has a skeletal pattern, i.e. a W-pattern, which has three angular change points which divide the heat transfer area into four equal parts.

For the second plate shown, the pattern is reminiscent of a W. Fransett the direction of the skeletal pattern, so the angles of the pattern are the same as for the first plate.

The upper distribution area 204 of the second plate is provided with a first coolant outlet opening hole 208, a water inlet opening hole 211 and a second coolant outlet opening hole 210. The corrugated pattern for the upper distribution area has a herringbone pattern reminiscent of a simple same as for the lower distribution area. Apart from the direction of the fi shin pattern, the angles of the pattern are the same as for the first plate.

The third heat exchanger plate 301, shown in Figure 4, includes a lower distribution area 302, a heat transfer 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 coolant inlet opening hole 307, a water outlet opening hole 312 and a second coolant inlet opening hole 309. The upper distribution area 304 of the plate is provided with a first coolant outlet opening hole 308, a water inlet opening hole 311 and a second cooling outlet outlet 3. the third heat exchanger plate the first heat exchanger plate.

The fourth heat exchanger plate 401, shown in Figure 5, includes a lower distribution area 402, a heat transfer 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 coolant inlet opening hole 407, a water outlet opening hole 412 and a second coolant inlet opening hole 409. The upper distribution area 404 of the plate is provided with a first coolant outlet opening hole 408, a water inlet opening hole 411 and a second cooling outlet opening. the fourth heat exchanger plate the second heat exchanger plate. In the description, the term active inlet opening means that the inlet opening is open so that coolant can flow through that inlet opening into the coolant channel. A passive inlet opening means that the inlet opening is closed so that no coolant can flow into the coolant channel through the passive inlet opening. The same applies to the concept of active outlet opening, which means that the outlet opening has contact with the coolant channel so that the coolant fl pours out of the active outlet opening. A passive outlet opening is closed so that no coolant can leak out of the coolant channel through the passive outlet opening. Figure 1 shows an inventive heat exchanger plate assembly 1 comprising a first plate 101, a second plate 201, a third plate 301 and a fourth plate 401. The different plates are shown in Figures 2 - 5. The plates are stacked on each other in the number required for a specific heat exchanger. In this way, a heat exchanger is formed comprising a plurality of plate assemblies. The number of plate assemblies is selectable depending on the spectra required by a heat exchanger. A complete heat exchanger will also include a special front plate and back plate (not shown) that are thicker than the individual friend changer plates. The front plate and the back plate include connections etc. In a complete friend changer, the liquid channel closest to the front plate and the back plate will be a water channel. A special heat exchanger plate which creates a water channel with the first plate can therefore be included in the front plate and a special heat exchanger plate which creates a water channel with the fourth plate can therefore be included in the back plate. The front plate and the back plate reinforce the heat exchanger, which makes it more stable and stronger.

The heat exchanger is of the brazed type. Between the first and the second plate a first coolant channel is created 2. Between the second and the third plate a water channel is created 3. Between the third and the fourth plate a second coolant channel is created 4. Between the learned plate and the first plate in an additional plate assembly to create a water channel. In this way, the heat exchanger will have alternating first and second coolant channels surrounded by water channels on both sides.

Both a coolant channel and a water channel include a lower distribution passage, a heat transfer passage and an upper distribution passage. The vertical length of the lower distribution passage is advantageously less than half the width of the heat exchanger, while the vertical length of the upper distribution passage is advantageously less than two thirds of the width of the heat exchanger.

When the first plate 101 and the second plate 201 are placed next to each other, a first coolant channel 2 is created. The coolant flows into the first coolant channel through a first coolant inlet opening 21, which is an active inlet opening created by the first coolant inlet opening holes 107, 207. The inlet opening holes 107, 207 are provided with concentric sealing sections 113, 213 which abut against each other. The inlet into the first coolant channel is provided with an inlet nozzle 25 in the sealing section. The inlet nozzle is formed by nozzle depressions 114, 214 in one or both of the sealing sections, which are embossed in the second pressing step.

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 coolant 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 coolant inflow pressure and is selected to achieve a smoothing. all the coolant ducts in a complete heat exchanger. The angular position of the inlet nozzle is chosen so that the coolant can be distributed evenly over the entire width of the heat exchanger in each coolant channel. The inlet nozzle can be directed at any angle, depending on e.g. the design of the corrugated pattern in the lower distribution passage and on the bypass section around the inlet opening. Preferably, the angle of the inlet nozzle is between 0 and 180 degrees with respect to a vertical axis, directed towards the vertical central axis of the plate, and more preferably the angle is between 90 and 150 degrees.

In one embodiment, the inlet opening is fully open. This can be advantageous when the heat exchanger is used so that the inlet opening functions as an outlet opening for steam, e.g. in a gas cooler. To avoid vapor blocking the outlet, the sealing section and the nozzle are punched out in the production stage. Instead, a fully open opening is obtained, similar to the outlet opening 22. Such an opening allows steam or a mixture of steam and liquid to flow out through the opening.

To further increase the coolant distribution, the active inlet opening is provided with an active inlet opening bypass 18 around the inlet opening which allows the coolant to flow around both sides of the inlet opening. Each plate includes a bypass section 115, 215 extending around the entire first inlet opening hole. The bypass section has the same press depth as the plate corrugations. The created bypass will thus have a height of two pressing depths, which means that the frictional pressure drop in the bypass will be much smaller than through the corrugated pattern. The bypass 18 will thus distribute a part of the coolant from the inlet nozzle to the distribution area around the active inlet opening.

Some of the coolant from the inlet nozzle will also continue in the direction from the nozzle into the corrugated pattern and further towards the second coolant inlet opening 23, which is a passive inlet opening. Since the water outlet opening holes 112, 212 are located at a vertical distance from the lower short side of the plate, a lower horizontal passage 13 is formed in the lower distribution channel between the water outlet opening and the lower short side of the heat exchanger. The coolant can thus flow below the water outlet opening and over to the area around the passive inlet opening. In this example, the coolant flow out of the inlet nozzle has approximately the same angle as the corrugated pattern of the first plate, so that part of the coolant can pass in a substantially horizontal direction below the water outlet opening with a relatively small friction factor and thus with a relatively high flow rate. When the coolant reaches the area around the passive inlet opening, a passive inlet opening bypass 19 around the passive inlet opening facilitates the distribution of coolant in the area around the passive inlet opening. The bypass 19 around the passive inlet opening 232 is created in the same way as at the active inlet opening, in that each plate comprises a bypass section 117, 217 which extends around the entire second inlet opening hole. The bypass section has the same pressure depth as the plate corrugations. The created bypass will thus have a height of two press depths, which means that the friction in the bypass will be much less than through the corrugated pattern. The bypass will thus distribute one day of the coolant to the distribution area around the passive inlet opening. The second inlet opening holes 109, 209 are provided with concentric sealing sections 116, 216 which abut against each other and which thereby seal the passive inlet opening.

The flat, circular section around the water outlet opening holes 112, 212 abuts each other so that the water outlet opening is sealed against the coolant channel. The water outlet opening holes are located at a vertical distance from the lower short side of each plate. A water outlet opening hole has a larger diameter than a coolant inlet opening hole and the center point of the water outlet opening hole is located closer to the horizontal axis of the plate than the center points of the coolant inlet opening holes. In this way, a lower horizontal passage 13 is formed in the coolant channel between the water outlet opening and the short side of the heat exchanger. Through this passage, the coolant can pass below the water outlet opening to the area around the passive inlet opening. This significantly improves the distribution of coolant over the width of the duct, and gives a more even fl fate over the width of the duct and thus through the heat transfer passage.

To further improve the distribution of coolant, the first coolant channel is provided with lower distribution channels 15, 16 located above the active and the passive inlet opening, between the lower distribution passage 10 and the heat transfer passage 11. The lower distribution channels are created mainly by smooth distribution grooves 118, 119, 218, 219 embossed in the plates between the V pattern of the distribution area and the W pattern of the heat transfer area and extending from the long side of a plate to the water outlet opening hole. The lower distribution channels will, on the one hand, facilitate an even distribution of refrigerant into the heat transfer passage 11 and, on the other hand, act as a transition field between the pattern of the distribution area V and the pattern of the heat transfer area W. The height and also the shape of the lower distribution channels can be chosen to optimize the flow distribution. The height of an embossed groove can, for example, be about half the pressing depth of a slab. To improve the mechanical strength of the heat exchanger, a lower distribution chute can also contain one or fl of your contact points. Since corresponding distribution channels are created in the water channel, the height of a lower distribution channel in the coolant channel is preferably not greater than a total of a press depth. The lower distribution channels will have a low flow resistance in the horizontal direction of the duct, compared with the flow resistance through a flow tube in the corrugated pattern of the heat transfer passage which has the same length and width.

If necessary, the lower distribution channels 15, 16 may comprise one or fl your throttling areas to control the fate distribution over the width of the channel in the lower distribution passage. The size and location of the throttling areas are chosen so that the flow through a distribution channel 15 or 16 is as evenly distributed as possible. The throttling can be accomplished by changing the pressing depth at the position of the throttling area in the plate, i.e. by changing the second height of the throttling area and / or by changing the width of the throttling area along the lower distribution channel. In this way, different throttles can be placed in different positions in the lower distribution grooves 15, 16. The throttles give a locally increased flow resistance which gives a fate distribution over the width of the lower distribution gutters, in one example the throttles cover most of the distribution gutters , which creates one or fl your small openings between the distribution passage and the heat transfer passage.

The size and positions of the throttles can be determined by experiments or calculations. The distribution of coolant flowing into the heat transfer passage will thus be improved.

After flowing through the active inlet port 21 and distributed in the lower distribution passage 10, the refrigerant will flow into and pass the heat transfer passage 11 created between the heat transfer areas 103, 203. The heat transfer passage with all contact points between the corrugated pattern of the two plates provides a large surface. and a relatively high friction flow resistance, which ensures an efficient heat transfer between the coolant and the water channel. The W-pattern increases the friction pressure drop slightly in the heat transfer passage compared to a single V-pattern, which improves the heat exchanger's total heat transfer.

Between the heat transfer area of each plate and the upper distribution area, a horizontal smooth distribution groove 120, 220 is embossed in each plate, which creates an upper distribution channel 17 in the first coolant channel. The upper distribution channel allows the fate of the coolant fl to be distributed and at the same time pressure differences that may occur in the heat transfer passage due to variations in the evaporation of the coolant can be equalized before the coolant flows into the upper distribution passage created between the plates' upper distribution areas 104, 204. The upper distribution channel to have a low flow resistance in the horizontal direction of the heat exchanger, which facilitates the distribution of the coolant before it flows into the upper distribution passage 12. The evaporation of the coolant is mainly completed in the upper distribution passage, where an overheating of the coolant vapor can also occur. The height of each distribution groove is approximately half of a plate's pressing depth, since a corresponding horizontal distribution channel is created in the water channel. This gives the upper distribution channel a total height of a pressing depth.

The refrigerant, which is largely evaporated, flows into the upper distribution passage created by the upper distribution areas 104, 204 of the plates. The first coolant outlet opening 22, which is an active opening, is created between 10 15 20 25 30 532 52% 22 the plates at the first coolant outlet opening holes 108, 208. A portion of the coolant will flow into the upper distribution passage on the right side of the vertical shaft 105, and a portion of the coolant will flow into the upper distribution passage on the left side. of the vertical shaft 105. A portion of the coolant will reach a bypass 20 created by bypass sections 121, 221 extending around the entire second outlet opening 24. The second coolant outlet opening holes 110, 210 are provided with concentric sealing sections 122, 222. which abut each other and seal the second outlet opening 24, which is a passive outlet opening. A bypass section has the same pressing depth as the corrugations of a plate. The created bypass 20 will thus have a height that is twice the pressing depth, which means that the flow resistance in the bypass is much less than through the corrugated pattern. The bypass will thus allow a large part of the coolant, which may be overheated, to pass substantially horizontally over to the active outlet opening through the horizontal passage above the water inlet opening.

The flat, circular sections around the water inlet opening holes 111, 211 abut each other so that the water inlet is sealed against the coolant channel.

The water inlet opening holes are located at a vertical distance below the upper short side of each plate. The center of the water inlet opening hole is located closer to the horizontal axis of the plate than the centers of the coolant outlet opening hole. In this way, an upper horizontal passage 14 is formed in the coolant channel between the water inlet opening and the upper short side of the heat exchanger. Through this horizontal passage, the coolant can flow above the water inlet opening from the bypass 20 at the passive outlet opening 24 to the active outlet opening 22 formed between the first coolant outlet opening holes 108, 208. This reduces the flow resistance of the vapor, which may be vapor, significantly improves the distribution in the upper distribution passage. This horizontal passage also prevents steam from accumulating around the passive outlet opening, which would create an insulating area with stagnant steam in the area around the passive outlet opening. The passage also increases the heat exchanger's total efficient heat transfer area with the area around the passive outlet opening.

When the second plate 201 and the third plate 301 are placed next to each other, a water channel 3 is created. The water flows into the water channel through the water inlet opening 42 created by the water inlet opening holes 211, 311. The water leaves the water channel through the water outlet opening 43 are closed so that the water and coolant do not mix. When the second and third plates are stacked, the bypass sections 215, 315 will abut each other and will thus seal the first coolant inlet opening. The same applies to the bypass sections 217, 317 and the bypass sections 221, 321 which also abut each other so that the second coolant inlet opening and the second coolant outlet opening are sealed. The first coolant outlet opening is sealed by the flat sections 223, 323 around the first coolant outlet opening holes 208, 308 which abut each other.

The water inlet opening holes 211, 311 are located at a vertical distance from the edge of the upper short side of each plate. The center of the water inlet opening hole is located closer to the horizontal axis of the plate than the center points of the coolant outlet opening holes. In this way, an upper horizontal passage 34 is formed in the water channel between the water inlet opening and the upper short side of the heat exchanger. This increases the usable cross-sectional area of the inlet opening, which in turn improves the water distribution in the upper distribution passage and reduces the pressure drop in the water channel.

To further improve the water distribution and also to reduce the pressure drop of the water, the water channel is provided with upper water bypasses 40, 41 between the passive second and first coolant outlet openings and the upper corner of the heat exchanger. The upper water bypasses 40, 41 are created by bypass sections 226, 227, 326, 327 outside the second and first coolers. Hold the 24 sub-outlet openings. These bypass sections abut each other when the plates are mounted so that a coolant channel is formed, which means that the water bypasses will have a height of two pressing depths. These water bypasses will thus have a low friction pressure drop and will facilitate the distribution on the water side throughout the upper distribution passage considerably.

When the water is distributed in the upper distribution passage 32, the water passes horizontal smooth distribution grooves 220, 320 embossed in each plate, which creates an upper horizontal upper distribution path 37 in the water channel. This distribution path allows a further distribution of the water so that the water pressure along the entire upper distribution path is substantially equal. The upper distribution path also functions as a transition field between the pattern of the upper distribution passage V and the pattern of the heat transfer passage W. The height of each distribution groove is approximately half the pressure depth of a plate. This gives the upper distribution web a height of a total of one press depth.

After passing the upper distribution path 37, the water will flow into and pass the heat transfer passage 31 created between the heat transfer areas 203, 303. The heat transfer passage with all contact points between the corrugated pattern of the two plates provides a large friend transfer surface and a relatively high friction factor, which ensures an efficient heat transfer between the water and the coolant channels. The W-pattern increases the friction factor slightly in the heat transfer passage compared to a single V-pattern, which improves heat transfer.

When the water has passed the heat transfer passage 31, it flows into the lower distribution passage 30 through two lower distribution paths 35, 36 located between the heat transfer passage and the lower distribution passage. These lower distribution passages are created by substantially smooth distribution grooves 218, 219. 318, 319 embossed in the plates between distribution areas- 10 15 20 25 30 532 521? Its V-pattern and the W-pattern of the heat transfer area, which extend from the long side of a plate to the water outlet opening hole. These distribution passages will both facilitate an even water distribution into the lower distribution passage and act as a transition field between the pattern of the heat transfer passage W and the pattern of the lower distribution passage V. The height and also the shape of the lower distribution paths can be selected to optimize the fate distribution. The height of an embossed groove in an example can be about half the pressing depth of a plate. To improve the mechanical strength of the heat exchanger, a lower distribution path can also contain one or fl of your 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 facilitates an even fate distribution of water into the lower distribution passage.

Some of the water, especially the water from the center of the heat transfer passage 31, will flow into the water outlet opening 43 created by the water outlet opening holes 212, 312 directly from the heat transfer passage located above. Since the corrugated pattern around the water outlet opening allows the water to flow into the water outlet opening from all directions, the water outlet opening is completely open. This allows the part of the water distributed to the lower distribution area to flow into the water outlet opening through the pattern between the water outlet opening and the coolant inlet openings and also from the pattern below the water outlet opening.

To further improve the water distribution, the lower distribution passage 30 is provided with lower water bypasses 38, 39 between the first and second passive coolant inlet openings and the lower corners of the heat exchanger. The lower water bodies are created by. water bypass sections 224, 225, 324, 325 at the first and second coolant inlet orifices. These bypass sections abut each other when the plates are mounted to create a coolant passage, which means that the height of the lower water bypass passage will be twice the pressure depth.

These lower water bypass passages will have a low friction pressure drop and will contribute significantly to directing the water fl fate to the water outlet opening.

To improve the water distribution and to increase the heat exchanger's effective heat transfer area, the water outlet opening holes are located at a vertical distance from the lower short side of each plate. In this way, a lower horizontal passage 33 is created in the water channel between the water outlet opening and the lower short side of the friend exchanger. Through this horizontal passage, the water can flow into the water outlet opening also from below the opening, which increases the efficiency of the heat exchanger. The lower bypass passages together with the upward displacement of the Water Outlet opening significantly improve the outlet water distribution distribution and reduce the outlet pressure drop around the entire circumference of the opening by increasing the usable cross-sectional area.

The second coolant channel 2 is created between the third plate 301 and the fourth plate 401 when they are placed next to each other and it is similar to the first coolant channel. The difference between the first coolant channel and the second coolant channel is only the inlet and outlet openings and the inlet nozzle.

The coolant flows into the second coolant channel through a second coolant inlet port 63, which is an active inlet port created by the coolant inlet port holes 309, 409. The inlet port holes 309, 409 are provided with concentric sealing sections 16 abutting 316 Other. The inlet into the second coolant channel is provided with an inlet nozzle 65 in the sealing section. The inlet nozzle is formed by nozzle recesses 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 coolant distribution in the lower distribution passage 50 created between the lower distribution areas 302 and 402. The size of the inlet nozzle depends partly on the pressure drop of the coolant circuit and is selected for to achieve an even distribution of fate through all the coolant channels in the coolant circuit in a complete heat exchanger. The angular position of the inlet nozzle is chosen so that the coolant can be distributed evenly over the entire width of the heat exchanger in each coolant channel. the inlet nozzle can be directed at any angle, depending on e.g. the design of the corrugated pattern in the lower distribution passage and on the bypass section around the inlet opening. Preferably, the angle of the inlet nozzle is between 0 and 180 degrees with respect to a vertical axis, directed towards the vertical central axis of the plate, and more preferably the angle is between 90 and 150 degrees.

To further increase the coolant distribution, the active inlet opening is provided with an active inlet opening port 59 around the inlet opening which allows the coolant to flow around both sides of the inlet opening. Each plate includes a bypass section 317, 317 extending around the entire inlet opening hole. The bypass section has the same press depth as the plate corrugations. The created active inlet bypass will thus have a height of two pressing depths, which means that the friction in the bypass will be much less than through the corrugated pattern. The bypass will thus distribute a part of the refrigerant from the inlet nozzle to the distribution area around the active inlet opening.

A portion of the coolant from the nozzle will also continue in the direction from the nozzle into the corrugated pattern toward the first coolant inlet port 61, which is a passive inlet port. Since the water outlet opening holes 312, 412 are located at a vertical distance from the lower short sides of the plates, a lower horizontal passage 53 is formed in the lower distribution channel between the water outlet opening and the lower short side of the heat exchanger. The coolant can thus flow below the water outlet opening to the area around the passive inlet opening. The fate of the coolant out of the inlet nozzle in this example has approximately the same angle as the corrugated pattern of the third plate, so that a part of the coolant can pass in a substantially horizontal direction below the water outlet opening with a relatively small friction factor and thus with a relatively high flow rate. When the coolant reaches the area around the passive inlet opening 61 ', a bypass 58 around the passive inlet opening helps to distribute the coolant to the area around the passive inlet opening. The bypass 58 is created in the same manner as at the active inlet opening, in that each plate comprises a bypass section 315, 415 extending around the entire first inlet opening hole. A bypass section has the same pressing depth as the plate corrugations. The created bypass will thus have a height of two pressing depths, which means that the friction in the bypass will be much less than through the corrugated pattern. The bypass will thus distribute a part of the coolant to the distribution area around the passive inlet opening. The first inlet opening holes 307, 407 are provided with concentric sealing sections 313, 413 which abut each other and which thereby seal the passive inlet opening.

The flat, circular section around the water outlet opening holes 312, 412 is adjacent to each other so that the water outlet opening is sealed against the coolant channel. The water outlet opening holes are located at a vertical distance from the lower short side of each plate. A water outlet opening hole has a larger diameter than a coolant inlet opening heel and the center of the water outlet opening hole is located closer to the horizontal axis of the plate than the center points of the coolant inlet opening holes. In this way, a lower horizontal passage 53 is formed in the coolant channel between the water outlet opening and the short side of the heat exchanger. Through this passage, the coolant can pass below the water outlet opening to the area around the passive inlet opening. This significantly improves the distribution of coolant over the width of the plate, which gives a smoother flow through the heat transfer passage and also increases the total effective heat transfer area of the heat exchanger with the area around the passive inlet opening.

To further improve the distribution of coolant, the second coolant channel is provided with lower distribution channels 55, 56 located above the passive and the active inlet opening, between the lower distribution passage 50 and the heat transfer passage 51. The lower distribution channels are mainly created by smooth distribution grooves 318, 319, 418, 419 in the plates between the V pattern of the distribution area and the W pattern of the heat transfer area and extending from the long side of a plate to the water outlet opening hole. The lower distribution channels will, on the one hand, facilitate an even distribution of coolant into the heat transfer passage 51 and, on the other hand, act as a transition field between the pattern of the distribution area V and the pattern of the heat transfer area W. The height and also the shape of the lower distribution gutters can be chosen to optimize the fate distribution. The height of an embossed groove in an example can be about half the pressing depth of a plate. To improve the mechanical strength of the heat exchanger, a lower distribution chute can also contain one or more contact points. Since corresponding distribution channels are created in the water channel, the height of a lower distribution channel in the coolant channel is preferably not greater than a total of a pressing depth. The lower distribution channels will have a low flow resistance in the horizontal direction of the channel, compared to the flow resistance through a flow tube in the corrugated pattern of the heat transfer passage having the same length and width. The lower distribution channels 55, 56 may also comprise one or more throttling areas to control the flow distribution over the width of the channel in the lower distribution passage. The throttles can be quite small so that they resemble one or fl your contact points or they can be relatively large so that only one or a few small openings are created between the distribution passage and the heat transfer passage. After flowing through the active inlet port 63 and distributed in the lower distribution passage 50, the coolant will flow into and pass the heat transfer passage 51 in the same manner as described for the first coolant channel.

Between the heat transfer area of each plate and the upper distribution area, a horizontal smooth distribution groove 320, 420 is embossed in each plate, which creates an upper distribution run 67 in the second coolant channel. The upper distribution chute allows pressure differences that may occur in the heat transfer passage due to variations in the evaporation of the coolant to be equalized before the coolant flows into the upper distribution passage 52 created between the upper distribution areas of the plates 304, 404. The coolant may at this stage be partially or completely evaporated, and may even be overheated. The upper distribution chute will have a low flow resistance in the horizontal direction of the heat exchanger, which facilitates the distribution of the cooling medium before it flows into the upper distribution passage. The height of each distribution groove is approximately half the pressing depth of a plate, since a corresponding horizontal distribution channel is created in the water channel. This gives the upper distribution channel a total height of a pressing depth. The coolant, which is largely evaporated in this cross-section, flows into the upper distribution passage 52 created by the upper distribution areas 304 of the plates. 310, 410. A portion of the coolant will flow into the upper distribution passage on the left side of the vertical shaft 305, and a portion of the coolant will flow into the upper distribution passage on the right side of the vertical axis 305. A portion of the coolant will reach a passive outlet port bypass 60 created by bypass sections 323, 423 extending around the entire first coolant outlet port 64, which is a passive opening. The first coolant outlet opening holes 308, 408 are provided with concentric sealing sections 328, 428 which abut each other and seal the first outlet opening. A bypass section has the same pressing depth as the corrugations of a plate. The created bypass will thus have a height that is twice the pressing depth, which means that the friction in the bypass is much less than through the corrugated pattern. The bypass will thus allow a large part of the coolant, which may be overheated, to pass over to the active outlet opening through the corrugated pattern in the passage above the water inlet opening.

The flat, circular sections around the water inlet opening holes 311, 411 abut each other so that the water inlet is sealed against the coolant channel.

The water inlet opening holes are located at a vertical distance from the upper short side of each plate. The center of the water inlet opening hole is located closer to the horizontal axis of the plate than the center points of the coolant outlet opening holes. In this way, an upper horizontal passage 54 is formed in the coolant channel between the water inlet opening and the upper short side of the heat exchanger.

Through this horizontal passage, the refrigerant can flow above the water inlet port from the bypass 60 at the passive outlet port 62 to the active outlet port 64 formed between the other coolant outlet port holes 310, 410. This significantly improves the refrigerant distribution of the coolant passive outlet opening. The total efficient heat transfer area of the heat exchanger is also increased by the area around the passive outlet opening.

Through the invention, an improved three-circuit flat fan exchanger is obtained, where the heat exchanger exhibits a significantly improved overall thermal performance. This is due to the improved fi fate distribution in the heat exchanger. The invention is not to be construed as limited to the embodiments described above, a number of further variants and modifications are possible within the scope of the appended claims. 10 15 20 25 30 532 524 32 REFERENCE DESIGNS sëšëlïårt * 10: 11: 12: 13: 14: 15: 16: 17: 18: 19: 20: 21: 22: 23: 24: 25: 30: 31: 32: 33 : 34: 35: 36: 37: screen mounting First coolant water channel by coolant Lower distribution passage heat exchange passage Upper fördelníngspassage Lower horizontal passage Upper horizontal passage Lower distribution path Lower distribution path Upper distribution path first kylmedelsinloppsöppningsförbiledning Other kylmedelsinloppsöppnlngsförbiledning Other kylmedelsutloppsöppningsförbilednlng Active inlet port Active outlet opening Passive inlet port Passive outlet opening lnloppsmunstycke Lower distribution passage Heat transfer passage Upper distribution passage Lower horizontal passage Upper horizontal passage Lower distribution path Lower distribution path Upper distribution path 10 15 20 25 30 38: 39: 40: 41: 42: 43: 50: 51: 52: 53: 54: 55: 56: 57: 58 : 59: 60: 61: 62: 63: 64: 65: 101: 102: 103: 104: 105: 106: 107: 108: 532 524 33 Water bypass connection Water bypass Water bypass Vattenförbiled connection Water Inlet opening the water outlet port Lower distribution passage heat exchange passage Upper distribution passage Lower horizontal passage Upper horizontal passage Lower distribution path Lower distribution path Upper distribution path first kylmedelsinloppsöppningsförbiledning Other kylmedelsinloppsöppningsförbiledning Other kylmedelsutloppsöppningsförbiledning Passive inlet port Passive outlet port Active inlet port Active outlet opening lnloppsmunstycke first heat exchanger plate lower distribution area heat transfer region upper distribution area Vertical axis horizontal shaft First coolant inlet opening hole First coolant outlet opening hole 10 15 20 25 30 109: 110: 111: 112: 113: 114: 115: 116: 117: 118: 119: 120: 121: 122: 123: 124: 125: 126: 127: 201: 202: 203: 204: 205: 206: 207: 208: 209: 210: 21 1: 212: 532 524 Other coolant inlet opening holes Other coolant outlet opening holes in Water inlet opening ngshål Vattenut | oppsöppningshå | Sealing Section Munstycksfördjupning bypass section Sealing Section bypass section Lower fördelningsspâr Lower distribution groove upper distribution groove bypass section Tätningssektíon Plan section of Lower water bypass section Lower water bypass section upper water bypass section upper water bypass section second heat exchanger plate Lower distribution area Heat Transfer Area Upper distribution area Vertical axis Horizontal axis first refrigerant inlet port First refrigerant outlet Other refrigerant inlet Other refrigerant outlet Vatteninloppsöppningshå! Water outlet opening hole 10 15 20 25 30 213: 214: 215: 216: 217: 218: 219: 220: 221: 222: 223: 224: 225: 226: 227: 301: 302: 303. ' 304: 305: 306: 307: 308: 309: 310: 311: 312: 313: 314: 315: 316: 532 524 35 Sealing section Nozzle recessing Bypass section Sealing section Bypass section Lower distribution groove Lower distribution groove Upper distribution section groove Upper water bypass section Third heat exchanger plate Lower distribution area Heat transfer area Upper distribution area Vertical axis Horizontal axis First coolant inlet opening hole First coolant Ice outlet opening hole Second coolant inlet opening hole Second cooler opening hole! Water inlet opening hole Water outlet opening hole Sealing section Nozzle recess Bypass section Sealing section 10 15 20 25 30 317: 318: 319: 320: 321: 323: 324: 325: 326: 327: 328: 401: 402: 403: 406: 409: 407: 407: : 410: 411: 412: 413: 414: 415: 416: 417: 418: 419: 420: 532 524 36 Bypass section Lower distribution track Lower distribution track Upper distribution track Flat section Bypass section Lower water bypass section Lower water bypass section In the upper water bypass section Upper distribution area Vertical axis Horizontal axis First coolant inlet opening hole First coolant outlet opening hole Other coolant inlet opening hole Second coolant outlet opening hole Water inlet opening hole Water outlet opening hole Sealing section Nozzle opening Spout opening r Lower distribution groove Upper distribution groove 421: 423: 424: 425: 426: 427: 428: 532 EZÅ 37 Flat section Bypass section Lower water bypass section Lower water bypass section Upper water bypass section Upper water bypass section Sealing section

Claims (22)

5 10 15 20 25 30 532 524 Év š š PATENTIKRAV A heat exchanger plate (101; 201; 301; 401) for use in a three-circuit heat exchanger assembly (1), the plate comprising a first distribution area (102; 202; 302; 402) with three opening holes (107 , 109, 112; 207, 209, 212; 307, 309, 312; 407, 409, 412), a heat transfer area (103; 203; 303; 403) and a second distribution area (104: 204; 304; 404) with three opening holes (108, 110, 111; 208, 210, 211; 308, 310, 311; 408, 410, 411), the plate comprising a corrugated pattern with ridges and valleys, characterized in that the middle the opening hole (112; 212, 312; 412) in the first distribution area is located at a vertical distance from the short side of the plate so that a fate passage is obtained between the middle opening hole and the short side of the plate when two plates are stacked to form a fate channel therebetween. . Plate according to claim 1, characterized in that the middle opening hole (111; 211; 311; 411) in the second sealing area is placed with a vertical distance from the short side of the plate so that a fl gap passage is obtained between the the middle opening hole and the short side of the plate when two plates are stacked to form a fl fate channel between them. . Plate according to Claim 1 or 2, characterized in that an opening hole (107, 109, 110; 207, 209, 210; 307, 308, 309; 407, 408, 409) is provided at a corner of the plate. a planar, annular bypass section (115, 117, 121; 215, 217, 221; 315, 317, 323; 415, 417, 423) adapted to form a coolant bypass passage around an opening when two plates are stacked to form a coolant flow channel between the plates. 10 15 20 25 532 524 250) Plate according to claims 1 to 3, characterized in that a water bypass section (124, 125, 126, 127; 224, 225, 226, 227; 324, 325, 326, 327; 424, 425, 426, 427) is arranged at a corner of the plate so that a water passage is obtained between two adjacent bypass sections when two plates are stacked to form a water channel between the plates. . Plate according to one of Claims 1 to 4, characterized in that the first distribution area (102; 202; 302; 402) has a skeletal pattern with a first design, the second distribution area (104; 204; 304; 404) has a skeletal pattern with a second design and where the heat transfer area (103; 203; 303; 403) has a skeletal pattern with a third design, where the first design of the skeletal pattern is directed in a first angular direction and where the second design of the skeletal pattern is directed in an opposite direction. angular direction. . Plate according to one of Claims 1 to 5, characterized in that the third design of the cartilage pattern is directed in the same angular direction as the first design of the cartilage pattern. . Plate according to one of Claims 1 to 6, characterized in that the third design of the cartilage pattern has changes in direction than the first and the second design. . Plate according to one of Claims 1 to 7, characterized in that the first and second tibial patterns resemble a V and the third tibial pattern resembles a W. Plate according to one of Claims 1 to 8, characterized in that a lower distribution groove (118, 119; 218, 219; 318, 319; 418, 419) is arranged between the first distribution area and the heat transfer area so that a The lower distribution channel is obtained between two adjacent lower distribution grooves when two plates are stacked to form a fl fate channel between the plates. 10 15 20 25 532 EEC HC 10. A plate according to claim 9, characterized in that the lower distribution groove (118, 119; 218, 219; 318, 319; 418, 419) comprises at least one restriction area so that a flow restriction is obtained in the lower distribution channel. Plate according to one of Claims 1 to 10, characterized in that an upper distribution groove (120; 220; 320; 420) is arranged between the friend transfer area and the second distribution area so that an upper distribution channel is obtained between two adjacent upper distribution grooves. tracks when two tiles are stacked to form a fl fate channel between the tiles. Heat exchanger assembly, comprising four plates according to any one of claims 1 to 11, characterized in that the first plate (101), the second plate (201), the third plate (301) and the fourth plate ( 401) differ from each other. in Heat exchanger assembly according to claim 12, wherein a first coolant channel (2) is arranged between the first plate (101) and the second plate (201), a water channel (3) is arranged between the second plate (201) and the third the plate (301) and a second coolant channel (4) are arranged between the third plate (301) and the fourth plate (401), and each fl fate channel (2, 3, 4) comprises a first distribution passage (10; 30; 50) arranged between two adjacent first distribution areas (102, 202, 302, 402), a heat transfer passage (11; 31; 51) arranged between two adjacent heat transfer areas (103, 203, 303, 403) and a second distribution passage ( 12; 32; 52) arranged between two adjacent second distribution areas (104, 204, 304, 404), characterized in that a horizontal passage (13; 33; 53) is arranged in the first distribution passage between the middle water opening (43 ) and the adjacent short side of the assembly. 10 15 20 25 532 EZÃ Hi Heat exchanger assembly according to claim 12 or 13, characterized in that a horizontal passage (14; 34; 54) is arranged in the second distribution passage (12; 32; 52) between the central water opening (42) and the adjacent the short side of the assembly. Heat exchanger assembly according to one of Claims 12 to 14, characterized in that a water bypass (38, 39, 40, 41) is arranged in a water distribution passage (30, 32) between a coolant opening (21, 22, 23, 24; 61, 62, 63, 64) and a corner of the assembly. Heat exchanger assembly according to one of Claims 12 to 15, characterized in that a coolant bypass (18, 19, 20; 58, 59, 60) is arranged around a coolant opening (21, 23, 24; 61, 62). 63) in a coolant distribution passage (10, 12; 50, 52). Heat exchanger assembly according to one of Claims 12 to 16, characterized in that the active inlet opening (21) is provided with an inlet nozzle (25) and in that the active inlet opening (63) is provided with an inlet nozzle. (65), where the angle of the inlet nozzle is between 0 and 180 degrees relative to a vertical axis and where the inlet nozzle is directed towards the central vertical axis of the assembly. A heat exchanger assembly according to claim 17, characterized in that the angle of the inlet nozzle is between 90 and 150 degrees. 19. Heat exchanger assembly according to one of Claims 12 to 18, characterized in that the lower distribution channel (15, 16; 35, 36; 55, 56) is arranged between a lower distribution passage (10, 30, 50) and a heat transfer passage (11, 31, 51). 20. Heat exchanger assembly according to one of Claims 12 to 19, characterized in that an upper distribution channel (17, 37, 57) is 532 524 holes arranged between a heat transfer passage (11, 31, 51) and an upper distribution passage (12). , 32, 52). 21. A heat exchanger assembly according to any one of claims 12 to 20, characterized in that the heat exchanger plates (101; 201; 301; 401) are joined by gluing, soldering, brazing, adhesion or welding. A three-circuit heat exchanger, comprising a plurality of heat exchanger assemblies according to any one of claims 12 to 21, and further comprising a faceplate and a backplate.