DE102016012842A1 - Plate heat exchanger - Google Patents

Abstract

The present invention relates to a plate heat exchanger having a plate pack (110) comprising a plurality of planar, parallel heat transfer plates (200, 201, 202, 203, 204, 205) and a plurality of profiled intermediate plates (300, 301, 302, 303, 304 ), wherein between each two adjacent heat transfer plates of the plurality of heat transfer plates (200, 201, 202, 203, 204, 205) in each case an intermediate plate of the plurality of intermediate plates (300, 301, 302, 303, 304) is arranged.

Description

The invention relates to a plate heat exchanger with a plate pack and a method for performing a heat exchange of fluids of a burner using such a plate heat exchanger.

State of the art

Heat exchangers may be used to transfer thermal energy from a warmer fluid to a colder fluid. The term fluid here refers to a medium which is in a gaseous and / or liquid state. For example, a warmer exhaust gas, which is produced during combustion in a burner, can be used to preheat the combustion air required for the combustion, a mixture of combustion air and fuel gas or fuel gas. This increases the combustion efficiency.

So-called plate heat exchangers have for this purpose a plate pack of a plurality of heat transfer plates. These individual heat transfer plates can be perforated in such a way that different channels are provided, through which different fluids for heat exchange can be performed.

An example of such a plate heat exchanger is, for example, in US 2011/0017436 A1 shown. Between the individual heat transfer plates, a plurality of pins is arranged in each case, which act as spacers in order to ensure a constant distance between adjacent heat transfer plates and to prevent bending or sagging of adjacent heat transfer plates.

Such plate heat exchangers, as used for example in the US 2011/0017436 A1 are shown, however, are usually very expensive to produce. In particular, it takes a high design effort to apply the plurality of individual pins as spacers on the individual heat transfer plates.

It is desirable to provide an improved plate heat exchanger that can be manufactured in a simple, inexpensive and fast manner.

Disclosure of the invention

According to the invention, a plate heat exchanger and a method for carrying out a heat exchange with the features of the independent claims are proposed. Advantageous embodiments are the subject of the dependent claims and the following description. Advantages and preferred embodiments of the plate heat exchanger according to the invention and the method according to the invention will become apparent from the following description in an analogous manner.

The plate heat exchanger according to the invention comprises a plate pack with a plurality of planar, parallel heat transfer plates and with a plurality of profiled intermediate plates. In each case between two adjacent heat transfer plates of the plurality of heat transfer plates, an intermediate plate of the plurality of intermediate plates is arranged in each case. The plate pack thus always has a heat transfer plate alternately, followed by an intermediate plate, thereafter again a heat transfer plate, then again an intermediate plate, etc. on.

At least one intermediate plate of the plurality of intermediate plates is formed as a plate having at least one non-profiled portion and at least two profiled portions in a main plane of extension of the plate. In these non-profiled regions, the respective intermediate plate is flat or profile-free, smooth and flat, and extends substantially in a two-dimensional plane and has a comparatively very small height or extension in a direction perpendicular to this plane. The at least one non-profiled area defines in particular the main extension plane of the plate.

In particular, the at least one non-profiled region forms the larger portion of the plate in comparison to the at least two profiled regions. In particular, 55%, 60%, 65%, 70%, 75%, 80%, 85%, 90% or 95% of the width of the panel may be formed by the at least one non-profiled area. Conveniently, 55%, 60%, 65%, 70%, 75%, 80%, 85%, 90% or 95% of the area of the panel may be formed by the at least one non-profiled area.

In this context, a "plane heat transfer plate" is to be understood as meaning that the heat transfer plate is profileless, smooth or flat. The heat transfer plate thus extends substantially in a two-dimensional plane and has a comparatively very small height, thickness or extension in a direction perpendicular to this plane. For example, this height or thickness of the heat transfer plates may each be between 0.5 mm and 2.0 mm, in particular between 0.8 mm and 1.5 mm. Length and width of the Heat transfer plates can each be, for example, up to several meters, for example between 1 m and 5 m in each case. Conveniently, the heat transfer plates are each of rectangular or substantially rectangular shape. In particular, all heat transfer plates are identical or substantially identical in construction.

In this context, a "profiled intermediate plate" is to be understood as meaning that the intermediate plate is folded, corrugated or ribbed at least partially or at least in a partial region. The intermediate plate extends in particular substantially in a two-dimensional plane and has at least in a partial region a profile which has a height in a direction perpendicular to this plane. In particular, the intermediate plate is integrally formed, i. the intermediate plate is in particular made of a workpiece, in particular of a plate which is profiled accordingly.

Conveniently, the intermediate plates are each of rectangular or substantially rectangular shape. As with the heat transfer plates, the height or thickness of the intermediate plates may each be between 0.5 mm and 2.0 mm, in particular between 0.8 mm and 1.5 mm. In particular, the length and width of the intermediate plates can each also be between 1 m and 5 m.

It is understood that the plate heat exchanger may have further expedient elements, in particular a frame or a frame construction in which the plate pack is arranged. For example, this frame may be formed from a variety of supports (e.g., steel, aluminum, plastic, or other suitable material) and act as a support for the plate pack. The plate heat exchanger may further comprise elements for sealing the plate pack.

The plate heat exchanger is expediently adapted to pass a first fluid and a second fluid through the plate pack, between which a heat exchange can take place in the plate packet.

The specific values for length, width, height and thickness of the heat transfer and / or intermediate plates may be selected depending on operating parameters of the plate heat exchanger, for example as a function of temperature and / or pressure and / or composition of the fluids passed through the plate heat exchanger. The material from which the heat transfer and / or intermediate plates are made can also be selected depending on such operating parameters.

The heat exchange in the plate pack takes place in particular via the heat transfer plates. The intermediate plates preferably do not or hardly contribute to the heat exchange, but are used in particular for structural or static purposes, expediently as a spacer and / or as a support for adjacent heat transfer plates. In particular, the intermediate plates are provided as support plates or partition plates between the heat transfer plates. The combination of flat and profiled plates, a particularly high stability of the plate package can be achieved in a constructively low-cost manner. The plate heat exchanger is fail-safe, low-maintenance and has a long service life.

The invention thus enables an innovative, simple construction of the plate heat exchanger. The combination of flat and profiled plates allows a simple, inexpensive and fast production of the plate heat exchanger. In particular, no special, elaborately made additional elements are provided for the plate heat exchanger. The plate heat exchanger can be manufactured from simple, inexpensive standard items. As heat transfer plates, for example, flat plates can be used, which can be obtained in a simple manner from corresponding suppliers. For the intermediate plates, for example, flat plates can be folded in a simple manner in order to profile these plates in a predetermined manner.

Advantageously, a distance between each two adjacent heat transfer plates is defined by the respective intermediate plate arranged therebetween. The intermediate plates are expediently folded in such a way that the heat transfer plates have a predetermined distance from each other. In particular, this distance is defined by the profile or by the height of the profile. In conventional plate heat exchangers, pins are often used as spacers, which are applied individually to heat transfer plates, for example welded on. Per heat transfer plate is usually a variety of pins needed (eg up to several hundred pins), which must be applied individually to the heat transfer plate, which is associated with a huge design effort and requires a relatively long production time. Advantageously, no such pins are used as spacers for the plate heat exchanger according to the invention, but the intermediate plates act as spacers. Consequently only one intermediate plate is used instead of a plurality of pins per heat transfer plate as a spacer, whereby a fast and low-complexity production of the heat exchanger is made possible.

Preferably, profiles of each two adjacent intermediate plates are rotated relative to each other by a predetermined angle. This angle is particularly preferably 90 °. Adjacent intermediate plates are to be understood as meaning two intermediate plates which are arranged on opposite sides of the same heat transfer plate, that is to say in particular on the front and rear sides of the same heat transfer plate. In particular, the profile of the intermediate plates is designed such that a rotation of 180 ° results in an identical profile. Thus, the profiles of each second intermediate plate extend in particular in the same extension direction. In particular, every other intermediate plate is identical or essentially identical. This embodiment of the intermediate plates makes it possible to guide two fluids in a structurally simple manner, in particular in mutually crossed flows for heat exchange through the plate pack.

Preferably, two adjacent heat transfer plates and the intermediately arranged intermediate plate form a channel unit for the passage of a fluid. As such channel unit is to be understood in particular a dense or sealed space between the two adjacent heat transfer plates, through which a fluid can be passed. Due to the special shape or the special profile of the intermediate plate, the channel unit may be divided into a plurality of individual channels or sub-channels, which extend parallel to one another and allow a flow of the same fluid in the same direction of flow.

Preferably, the channel unit between two adjacent heat transfer plates is bounded laterally and / or axially by a profile of the corresponding intermediate plate arranged therebetween, and a flow direction of the channel unit is defined by a main extension direction of the profile of the corresponding intermediate plate. The profile or at least part of the profile makes it possible in particular to connect the intermediate plate with the adjacent heat transfer plates in such a way that the space between the heat transfer plates can be closed and sealed. The profile thus limits the channel unit. The respective fluid can thus be guided in a flow through the channel unit, which runs parallel or at least substantially parallel to the main extension direction of the profile, so that this main extension direction defines the flow direction of the channel unit.

Preferably, three adjacent heat transfer plates and the respective intermediate plates arranged between them form two adjacent channel units. A first of these two adjacent channel units preferably extends or defines a first flow direction. The other of the two adjacent channel units preferably extends into or defines a second flow direction. The first flow direction and the second flow direction are advantageously orthogonal to one another. Since the profiles of two adjacent intermediate plates, as explained above, are preferably twisted by 90 ° with respect to one another, the main directions of extension of the profiles of two adjacent intermediate plates are preferably also rotated by 90 ° relative to one another and thus orthogonal to one another. Since the flow directions of the channel units are defined by these main directions of extension, thus the flow directions of adjacent channels are orthogonal.

In particular, the same fluid can thus be conducted in the same direction of flow through every second channel unit. A heat transfer plate is thus used in particular for each two adjacent channel units. Along one side of the heat transfer plate is thus passed through one of these two channel units, a first fluid in the first flow direction, along the other side of the heat transfer plate is passed through the second of these two channel units, a second fluid in the second flow direction. Thus, a heat exchange of the two fluids in the two adjacent channel units can take place via the heat transfer plate. The intermediate plates, as explained above, preferably do not contribute or hardly contribute to the heat exchange, but function expediently both as spacers between adjacent heat transfer plates, as well as for sealing the channel units and for guiding the corresponding fluid conducted through the channel units.

According to a particularly preferred embodiment, the plate is folded in each of the at least two profiled regions in each case such that a first support region and a second support region are provided. The at least one non-profiled region thus advantageously defines a main extension plane of the plate. This first support region extends in a first plane parallel to the main extension plane and this second support region extends in a second plane parallel to the main extension plane. These first level and second level lie on opposite sides respectively the main extension plane, each at a predetermined distance from the main extension plane. The respective intermediate plates are preferably formed profiled in one piece, ie, the intermediate plates are each made of a workpiece, which is profiled accordingly.

The support areas may be formed, for example, each as levels. In particular, the bearing areas serve to support the heat transfer plates or to fix the intermediate plate to the heat transfer plates. This special design provides a structurally simple design of the intermediate plates to allow a particularly high stability of the plate pack and to ensure the functions of the intermediate plates as spacers between adjacent heat transfer plates, for sealing the channel units and for guiding the corresponding fluid.

For example, in each of these profiled regions, the plate may in particular be folded so as to extend in a first direction perpendicular to the main plane of extension (e.g., vertically upwardly with respect to the main plane of extent) to the first bearing region. From this first support region, the plate may then extend in a second direction perpendicular to the main extension plane to the second support region, which is opposite to the first direction (e.g., vertically downwardly with respect to the main extension plane). For example, the plate may extend from the second support area in the first direction.

It should be noted that a distance of one of the bearing areas can also be expediently zero. In this case, the respective contact area coincides with the main extension plane. Advantageously, at least one of the intermediate plates of the plurality of intermediate plates is in this case formed as a plate having at least one non-profiled region and at least two profiled regions. Analogous to the above description, the respective intermediate plate is planar in these non-profiled areas, extends substantially in a two-dimensional plane, has a comparatively very small height in a direction perpendicular to this plane, defines a main plane of extension of the plate and in this case preferably forms a first edition area. In each of the at least two profiled regions, the plate is preferably in each case folded in such a way that a second support region is provided which extends in a plane parallel to the main plane of extension at a predetermined distance from the main extension plane. The respective intermediate plates are preferably formed profiled in one piece.

Preferably, a first profiled region is arranged on a first edge region of the plate and a second profiled region on a second edge region. The first edge region and the second edge region are preferably opposite. In this context, an edge region is to be understood as an area in front of one of the four edges of the expediently rectangular plate. Thus, in particular the edges or edge regions of the intermediate plates are formed profiled. It is understood that the intermediate plate may have further profiled areas, which may lie between the first and the second edge region. Profiled areas in the edge areas of the plate are expediently used for sealing the channel units, profiled areas between these edge areas act in particular to stabilize adjacent heat transfer plates.

Advantageously, a first heat transfer plate rests on the first support region, and a second heat transfer plate is disposed on the second support region and is disposed in the plate package adjacent to the first heat transfer plate. The corresponding intermediate plate is, for example, welded to the respective bearing area with the respective heat transfer plate or connected to each other in any other appropriate manner. The channel unit is thus suitably sealed by this connection between the heat transfer plate and the intermediate plate.

The at least one intermediate plate and two adjacent heat transfer plates preferably form a channel unit. This channel unit is preferably delimited by the first profiled area and the second profiled area of the at least one intermediate plate. The flow direction of the channel unit is preferably defined by a main extension direction of the first profiled area and the second profiled area of the at least one intermediate plate. Furthermore, the channel unit can be sealed in particular by the first and the second profiled region. Particularly preferably, the channel unit is limited by profiled regions, which are arranged on two opposite edge regions of the corresponding intermediate plate.

In this context, the main direction of extension should be understood as a direction along which the profile essentially extends. As explained above, the corresponding plate in the profiled areas in particular has a profile which has a height or extension perpendicular to the main extension plane. Without limiting the generality, the main extension plane is called the xy plane. The profile thus generally has a height or extension in the z-direction. This profile extends in particular either in the x-direction or in the y-direction, the main extension direction is thus in particular either the x-direction or the y-direction. In particular, therefore, cross sections through the intermediate plate in the z-direction along the main extension direction are always identical or substantially identical.

A distance between the first support portion and the second support portion preferably defines the distance between the two adjacent heat transfer plates. The respective distances of the support areas to the main extension plane are thus expediently designed such that the intermediate plate can act as a spacer between the heat transfer plates.

Advantageously, at least two adjacent intermediate plates are each formed as a plate with at least one non-profiled area and with at least two profiled areas. The main directions of extension of the first profiled area and of the second profiled area of the at least two adjacent intermediate plates are advantageously rotated relative to one another by a predetermined angle. This angle is preferably 90 °. As explained above, the profiles of adjacent intermediate plates are thus preferably rotated by 90 ° relative to each other, whereby adjacent channel units are realized with orthogonal flow directions.

Preferably, the plate of the intermediate plate may have at least one single-sided profiled area. In contrast to the profiled areas, the panel is folded in this single-sided profiled area in such a way that a further first support area or a further second support area is provided.

According to a preferred embodiment, at least one flow guide element is introduced into at least one intermediate plate of the plurality of intermediate plates. In particular, these flow guide elements form resistors which can change the flow of the fluid passed through the corresponding channel unit. In particular, the fluid is brought by these flow guide from a laminar to a turbulent or at least partially turbulent flow. By such (at least partially) turbulent flows, the effectiveness of the heat exchange process, in particular the effectiveness of the heat transfer and heat transfer, and thus expediently the thermal efficiency of the plate heat exchanger in comparison to a laminar flow can be increased. Arrangement, position, number, shape and / or size of the flow guide can be chosen in particular such that the flow can be influenced as desired.

Conveniently, the flow guide elements can additionally contribute to the stability of the plate pack and, in particular in addition to the profile of the intermediate plate, can also serve as a spacer between adjacent heat transfer plates. In particular, the flow guide elements are introduced into the intermediate plate between the first and second profiled regions arranged on respectively opposite edge regions. Depending on the particular application, it may prove expedient to arrange further profiled areas between the first and the second profiled area in order to serve as spacers and / or for stability, or to dispose of any further profiled areas if the introduced flow guide elements are sufficient for Stability or serve as a spacer.

Advantageously, the at least one flow guide is inserted into at least one opening in the at least one intermediate plate, in particular inserted. These openings may be removed during the manufacturing process e.g. be machined into the corresponding intermediate plates. During manufacture of the plate heat exchanger, the flow directors can be easily inserted into the openings, e.g. be plugged in.

Preferably, at least one Strömungsleitpin and / or at least one Strömungsleitplatte are introduced as the at least one flow guide. Such Strömungsleitplatte is to be understood in particular as a plate which has much smaller dimensions than the intermediate plate. The flow baffle may for example be straight or curved or have another expedient shape. For example, such Strömungsleitplatte may be formed as a sheet of a metallic material or made of another suitable material, for. made of plastic.

In the course of the method according to the invention, the plate heat exchanger is used for carrying out a heat exchange of fluids of a burner. In such a burner, fuel gas or a gas mixture of fuel gas and combustion air is burned to a combustion exhaust gas. For example, natural gas or a natural gas-oxygen mixture can be used as fuel gas. Fuel gas or combustion air or the gas mixture of combustion gas and combustion air is passed as a first fluid through the plate pack of the plate heat exchanger and then the Burner supplied. The combustion exhaust gas is passed from the burner to the plate heat exchanger and passed as a second fluid through the plate pack of the plate heat exchanger. Since this combustion exhaust gas has a comparatively high temperature, it is particularly appropriate to preheat the colder combustion air or the mixture of combustion air and fuel gas or the fuel gas by means of heat exchange. By this preheating combustion efficiency can be increased.

The material from which the heat transfer and / or intermediate plates are made may conveniently be selected depending on a sulfur content and / or a sulfuric acid dew point of the fluids, in particular, generally an acid dew point, which applies to all acids in the first and second fluids, respectively refers. The acid dew point of sulfur-containing fuel gases is for example in a range between 120 ° C and 150 ° C. For example, can arise in the combustion of sulfur-containing fuel gases SO ₂ and SO ₃ , which further react with water vapor in the exhaust gas to sulfuric acid and sulfuric acid. For example, highly corrosive sulfuric acid condenses when falling below the corresponding acid dew point. In such cases, in particular corrosion-resistant material is used for the heat transfer and / or intermediate plates, for example stainless steel. For example, with very low acid content in the fluids, carbon steel can be used for the heat transfer and / or intermediate plates.

For example, the burner may be used for a process furnace to cause a reaction or acceleration of a reaction therein. For example, the process furnace in a synthesis gas plant (eg hydrogen or ammonia plant), DRI plant (Direct Reduced Iron), incinerators (INCINERATORS), in a cracked gas oven (ethylene cracker), EDC furnace (Ethylene Dichloride Furnace) or a so-called "Hot Thermal Heater " be used.

Preferably, the burner may be used for syngas production. Synthesis gas is a gas mixture of hydrogen and carbon monoxide to understand that can be used in a variety of industrial processes as a basic chemical. The ratio of hydrogen to carbon monoxide of the synthesis gas can be adjusted in particular by synthesis gas production. For example, synthesis gas can be produced from coal, petroleum, natural gas, biomass or organic waste. The burner may be used to generate process temperatures needed for process stages of syngas production. For example, by means of the burner for this purpose, a carburetor or the combustion chamber of a carburetor can be heated.

It is also conceivable that the plate heat exchanger is expediently used for heating a process gas, e.g. in the course of synthesis gas production, hydrogen synthesis, ammonia synthesis, etc. For example, can be heated by the plate heat exchanger, a process gas which has been cooled by a previous process section, but requires a higher temperature for a subsequent process section.

Further advantages and embodiments of the invention will become apparent from the description and the accompanying drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination indicated, but also in other combinations or in isolation, without departing from the scope of the present invention.

The invention is illustrated schematically with reference to an embodiment in the drawing and will be described in detail below with reference to the drawing.

list of figures

• 1 schematically shows a preferred embodiment of a plate heat exchanger according to the invention in a perspective view and in an exploded view.
• 2 schematically shows a part of a plate pack of a preferred embodiment of a plate heat exchanger according to the invention in exploded views.
• 3 schematically shows an intermediate plate of a preferred embodiment of a plate heat exchanger according to the invention in a perspective view and in a cross-sectional view.
• 4 schematically shows intermediate plates according to preferred embodiments of a plate heat exchanger according to the invention in each case in a cross-sectional view.
• 5 schematically shows a channel unit according to a preferred embodiment of a plate heat exchanger according to the invention in a cross-sectional view.
• 6 schematically shows an intermediate plate and parts of an intermediate plate of a preferred embodiment of a plate heat exchanger according to the invention in each case in a perspective view.

In 1 a preferred embodiment of a plate heat exchanger according to the invention is shown schematically and designated 100. In 1a is the plate heat exchanger 100 shown in a perspective view, in 1b in an exploded view.

The plate heat exchanger 100 includes a plate pack 110 which is in a frame 101 is arranged. The frame 101 acts on the one hand as a holder for the plate package 110 and continues to serve the plate pack 110 seal. The frame 101 is composed of a variety of steel beams, which in 1b by way of example with the reference numerals 101 . 101b . 101c are designated. Furthermore, the plate heat exchanger 100 a reversal chamber 102 on.

It can be a first fluid F ₁ and a second fluid F ₂ through the plate pack 110 be directed to allow heat exchange between these two fluids. For example, combustion air, a fuel gas (eg natural gas) or a mixture of combustion air and fuel gas as the first fluid F ₁ be used. This first fluid F ₁ is preheated in the heat exchanger and can then be supplied to a burner for combustion, whereby a combustion exhaust gas is generated. This combustion exhaust gas may act as a second fluid F ₂ through the plate pack 110 be directed. The combustion exhaust gas F ₂ has a comparatively high temperature, the first fluid F ₁ has a comparatively low temperature, for example ambient temperature. Thus, in the course of the heat exchange, thermal energy from the combustion exhaust gas F ₂ in the disk pack 110 on the first fluid F ₁ be transferred and preheat this, and thus to increase the efficiency of the burner.

The first fluid F ₁ may be in a first flow direction through a first half 111 of the disk pack 110 in this example, vertically down, that is, in the negative x direction. After passing through this half 111 of the disk pack 110 flows through the first fluid F ₁ the reversal chamber 102 , The flow direction of the first fluid F ₁ is then reversed and the first fluid F ₁ can a second half 112 of the disk pack 110 flow through in a second flow direction, which is parallel and opposite to the first flow direction, in this example, vertically upward, so in the positive x direction. The second fluid F ₂ can along a flow direction through the plate pack 110 which is perpendicular to the first and second flow direction, in this example in the positive y-direction. The flow directions of the first fluid F ₁ and the second fluid F ₂ are thus always orthogonal to each other.

This reversal chamber 102 in particular serves to increase the thermal length of a channel. The plate heat exchanger 100 can with the plate package 110 and the frame 101 even without this reversal chamber 102 be made as it is in 1c is shown. In this case, in particular, a simple cross-flow is created. The first fluid F ₁ is doing through both halves 111 and 112 of the disk pack 110 along the same flow direction, in the example shown vertically down or in the negative x direction.

In 2 is part of the disk pack 110 of the plate heat exchanger 100 out 1 shown schematically in an exploded view.

The plate pack has a plurality of planar, parallel heat transfer plates 200 and a variety of profiled intermediate plates 300 on. In 2a are exemplary five heat transfer plates 201 to 205 and four intermediate plates 301 to 304 shown. In 2 B are exemplary two adjacent intermediate plates 301 and 302 shown.

As in 2a can be seen, in each case an intermediate plate is disposed between two adjacent heat transfer plates. Between the two adjacent heat transfer plates 201 and 202 is the intermediate plate 301 arranged. Between the heat transfer plates 202 and 203 is the intermediate plate 302 arranged, etc.

The individual heat transfer plates 200 are in particular of identical design, in each case as a profile-free, flat plate, which extend substantially in a two-dimensional plane. This level is in 2a without restriction of the generality as xy-level called. The heat transfer plates 200 each have a comparatively very small height or extent in a z-direction perpendicular to this xy-plane. For example, the heat transfer plates 200 each have a length, ie an extension in the x-direction, of 2.5 m, a width, ie an extension in the y-direction, of 1.0 m and a height or thickness of 1.5 mm.

The intermediate plates 300 are in contrast to the heat transfer plates 200 profiled. As in 2a can be seen, has a first intermediate plate 301 a profile which extends in the x direction. A second intermediate plate 302 on the other hand has a profile which extends in the y-direction. The profile of the first intermediate plate 301 is thus 90 ° with respect to the profile of the second intermediate plate 302 twisted. A main extension direction of the profile of the first intermediate plate 301 , ie the x-direction, is thus 90 ° opposite one Main extension direction of the profile of the second intermediate plate 302 , so the y-direction, twisted.

The profile of a third intermediate plate 303 is again at 90 ° to the profile of the second intermediate plate 302 twisted and is identical to the profile of the first intermediate plate 301 , Each second intermediate plate is thus designed in particular identical. In 2a On the one hand, for example, the intermediate plates 301 and 303 each identical design and on the other hand, the intermediate plates 302 and 304 ,

For clarity, in 2 B two of the intermediate plates 300 shown schematically, for example, the first intermediate plate 301 and the second intermediate plate 302 , As in 2 B can be seen, the first intermediate plate 301 five profiled areas 311 and four unprofiled areas 312 on. In these unprofiled areas 312 is the first intermediate plate 301 just trained and each extends at least substantially in the xy plane. These unprofiled areas 312 thus define a main extension plane of the first intermediate plate 301 , which in this example corresponds to the xy plane without restriction of generality.

In the profiled areas 311 is the first intermediate plate 301 each folded such that it has a profile which has an extension or height in the z-direction perpendicular to the main extension plane. These profiles run or extend in the x-direction. The x-direction thus corresponds to a main extension direction of the profiles of the first intermediate plate 301 , In particular, cross sections through the intermediate plate in the zy plane along this x direction are always at least substantially identical.

Analog also has the second intermediate plate 302 five profiled areas 321 and four unprofiled areas 322 on. Also the second intermediate plate 302 is in these unprofiled areas 322 just trained so that even those non-profiled areas 322 the xy plane as the main extension plane of the second intermediate plate 302 define.

The second intermediate plate 302 is in the profiled areas 321 each also folded such that it has a profile which has an extension or height in the z-direction perpendicular to the main extension plane. However, these profiles extend in contrast to the profiles of the first intermediate plate 301 not in the x-direction, but in the y-direction. The y-direction thus corresponds to a main extension direction of the profiles of the second intermediate plate 302 , The main directions of extension of the profiles of the adjacent intermediate plates 301 and 302 are thus rotated by 90 ° to each other.

Due to this special profiling of the large number of intermediate plates 300 and by the special combination of intermediate plates 300 and heat transfer plates 200 can in the disk pack 110 a variety of channel units 400 will be realized. As in 2a can be seen, each form two adjacent heat transfer plates and the intermediate plate arranged therebetween, a channel unit for the passage of a fluid.

The first heat transfer plate 201 , the first intermediate plate 301 and the second heat transfer plate 202 thus form a first channel unit 401 with a flow direction identical to the first extension direction, ie the x-direction. Thus, through the gap between the first heat transfer plate 201 and second heat transfer plate 202 the first fluid F ₁ flow in positive or negative x-direction.

The second heat transfer plate 202 , the second intermediate plate 302 and the third heat transfer plate 203 form a second channel unit 402 with a flow direction identical to the second extension direction, ie the y-direction. Through the space between the second heat transfer plate 202 and third heat transfer plate 203 can thus be the second fluid F ₂ flow in positive or negative y-direction.

The second heat transfer plate 202 is thus for both the first channel unit 401 as well as for the second channel unit 402 intended. Along one side of the heat transfer plate 202 thus flows the first fluid F ₁ and along the other side of the heat transfer plate 202 the second fluid flows F ₂ , allowing a heat exchange between the first fluid F ₁ and the second fluid F ₂ can be done.

The third heat transfer plate 203 , the third intermediate plate 303 and the fourth heat transfer plate 204 form a third channel unit 403 , The flow direction of this third channel unit 403 is again identical to the first extension direction, ie the x-direction. Through this third channel unit 403 , so through the gap between the third heat transfer plate 203 and fourth heat transfer plate 204 , analogous to the first channel unit 401 the first fluid F ₁ flow in positive or negative x-direction. The third heat transfer plate 203 is for both the second channel unit 402 as well as for the third channel unit 403 provided so that on the third heat transfer plate 203 a heat exchange can take place.

The fourth heat transfer plate 204 , the fourth intermediate plate 304 and the fifth heat transfer plate 205 form a fourth channel unit 404 whose flow direction is analogous to the flow direction of the second channel unit 402 is identical to the second extension direction, ie to the y-direction. Through the fourth channel unit 404 can be analogous to the second channel unit 402 the second fluid F ₂ flow in positive or negative y-direction. At the fourth heat transfer plate 204 Thus, a heat exchange can also take place. The fifth heat transfer plate 205 is in turn also provided for a fifth channel unit, which in 2a is no longer shown.

This concept of adjacent intermediate plates with 90 ° twisted profiles and channel units 400 thus sets through the plate package 110 continued. In this variety of channel units 400 Thus, the flow directions adjacent channel units are each orthogonal to each other. The flow direction of each second channel unit is accordingly identical. Each second channel unit is thus provided for the flow of the same fluid. Each of the two fluids flows on the opposite sides of the heat transfer plates, so that a heat exchange can take place on the heat transfer plates.

The following are with reference to the 3 and 4 different embodiments for the intermediate plates according to preferred embodiments of the invention explained.

In 3 is an intermediate plate 500 shown schematically according to a preferred embodiment of the invention. In the upper half of 3 is the intermediate plate 500 shown in a perspective view and in the lower half in a cross-sectional view.

As in 3 can be seen, the intermediate plate has 500 a non-profiled area 511 and two profiled areas 521 and 522 on. In the unprofiled area 511 extends the intermediate plate 500 between the x-coordinates x ₁ and x ₄ flat or flat. This unprofiled area 511 thus defines the main extension plane E _H the intermediate plate 500 , which in this example corresponds to the xy plane.

The profiled areas 521 and 522 are on opposite edge areas of the intermediate plate 500 arranged. In the edge regions is the integrally formed intermediate plate 500 in this case folded such that it has there in each case a profile which a height or extension in a direction perpendicular to the main extension plane E _H has, in this example in the z-direction. These profiles extend or respectively extend in the y-direction, so that the y-direction in this example is the main extension direction of the profiles or the profiled regions 521 and 522 equivalent.

The intermediate plate 500 is in each of the profiled areas 521 and 522 each folded such that a first support area E _A1,1 respectively. E _A1,2 and a second edition area E _A2,1 respectively. E _A2,2 to be provided. Each of these bearing areas is formed in this example in each case as a flat surface.

The first edition areas E _A1,1 and E _A1,2 thus extend in one to the main extension plane E _H parallel first level. The second edition areas E _A2,1 and E _A2,2 extend in a to the main extension plane E _H parallel second level.

This first level is at a first distance of Δz ₁ above the main extension plane E _H , The second level is at a second distance of Δz ₂ below the main plane of extension E _H , These first and second levels are thus respectively on opposite sides of the main extension plane E _H each at a predetermined distance from the main extension plane E _H ,

It should be noted that one of the distances Δz ₁ or Az _{2 may} also be zero. In this case, the respective circulation area falls E _A2,1 respectively. E _A2,2 with the main extension plane E _H together.

The following is the special shape of the profile of the intermediate plate 500 in the profiled area 521 described:

For example, the intermediate plate 500 folded at a coordinate x ₁ such that it is perpendicular to the main plane of extension E _H in the positive z direction by the first distance Az ₁ to the first supporting region E _A1,1 runs. Between the coordinates x ₁ and x ₂ , the intermediate _plate runs 500 flat and parallel to the main extension plane E _H and forms the first edition areas E _A1,1 , The first edition areas E _A1,1 has a width of Δx ₁ .

At the coordinate x ₂ is the intermediate plate 500 folded so that it is perpendicular to the main plane of extension E _H in the negative z-direction by the distance .DELTA.z to the second support area E _A2,1 runs. The distance Δz corresponds to the sum of the first distance Δz ₁ and the second distance Δz ₂ .

Between the coordinates x ₂ and x ₃ , the intermediate _plate runs 500 flat and parallel to the main extension plane E _H and forms the second edition E _A2,1 , The second edition areas E _A2,1 thus has a width of .DELTA.x ₂ .

In a similar way is the intermediate plate 500 in the profiled area 522 folded: At a coordinate x ₄ , the intermediate plate is perpendicular to the main plane of extension E _H in the positive z direction by the first distance Az ₁ to the first supporting region E _A1,2 , Between the x ₄ and x ₅ , the intermediate _plate runs 500 parallel to the main extension plane E _H and forms the first edition areas E _A2,1 , At the coordinate x ₅ , the intermediate _plate runs 500 perpendicular to the main extension plane E _H in the negative z-direction by the distance .DELTA.z to the second support area E _A2,2 , Between the coordinates x ₅ and x ₆ forms the intermediate plate 500 the second edition E _A2,2 ,

At the first edition areas E _A1,1 and E _A1,2 For example, a first heat transfer plate can be attached, for example by welding. At the second edition areas E _A2,1 and E _A2,2 An adjacent second heat transfer plate can be fastened, eg welded.

By this particular cohesive connection between support area and corresponding heat transfer plate, the gap between these adjacent heat transfer plates and thus the corresponding channel unit can be sealed.

The area E _B1 the intermediate plate 500 , which at the x-coordinate x ₂ perpendicular to the main plane of extension E _H between the first edition area E _A1,1 and the second edition E _A2,1 runs, thus serving as a first boundary surface of the corresponding channel unit. The area E _B2 , which at x ₅ perpendicular to the main plane of extension E _H between the first edition area E _A1,2 and the second edition E _A2,2 runs, serves as a second boundary surface of the corresponding channel unit.

Thus, the corresponding channel unit between these two adjacent heat transfer plates is through the first profiled area 521 and the second profiled area 522 the intermediate plate 500 limited and the flow direction of the channel unit is through the main extension direction of the first profiled area 521 and the second profiled area 522 the intermediate plate 500 , that is, defined by the y-direction.

The intermediate plate 500 thus serves both to limit and seal the channel unit, as well as a spacer between the adjacent heat transfer plates. A distance between the respective heat transfer plates is defined by the distance Δz between the first support area E _A1,1 respectively. E _A1,2 and the second edition E _A2,1 respectively. E _A2,2 Are defined.

In 4 schematically further preferred embodiments of the intermediate plate are analogous to 3 each shown in a cross-sectional view.

The intermediate plate 500a in 4a has analogous to the intermediate plate 500 out 3 at its edge regions a first profiled area 521 and a second profiled area 522a on. Furthermore, the intermediate plate 500a another third profiled area 523a on. Thus, the intermediate plate 500a two unprofiled areas 511a and 512a on.

The profiled areas 521 and 522a at the edge areas of the intermediate plate 500a are for example analogous to the profiled areas 521 and 522 the intermediate plate 500 according to 3 educated.

In the third profiled area 523a is the intermediate plate 500a initially folded from the main extension plane in the positive z-direction to a first bearing surface A _1a , From the first contact surface A _1a off is the intermediate plate 500a in the negative z-direction up to a second contact surface A _2a folded. From the second support surface A _2a off is the intermediate plate 500a again in positive z-direction to a third bearing surface A _3a folded. From the third contact surface A _3a off is the intermediate plate 500a folded again in the negative z-direction up to the main extension plane.

The distances between the main extension plane and the bearing surfaces A _1a and A _3a is in each case identical in each case. The distance between the bearing surfaces A _1a and A _2a is in particular identical to the distance between the support surfaces A _3a and A _2a ,

The first edition E _{A1,3, a} this third profiled area 523a is in this example by the first bearing surface A _1a and through the third bearing surface A _3a formed and the second support area E _A2,3a this third profiled area 523a is through the second bearing surface A _2a educated.

In 4b is a further preferred embodiment of an intermediate plate shown and designated 500b. Analogous to the intermediate plates 500 and 500a also has the intermediate plate 500b at its edge regions on two non-profiled areas 521b and 522b. Analogous to the intermediate plate 500a has the intermediate plate 500b also a third profiled area 523b and two unprofiled areas 511b and 512b on.

In the third profiled area is the intermediate plate 500b initially from the main extension plane in the negative z-direction to a first bearing surface A _1b folded. From this is the intermediate plate 500b in the positive z-direction up to a second contact surface A _2b folded. From this second bearing surface A _2b is the intermediate plate 500b again in negative z-direction up to a third contact surface A _3b folded. Based on this is the intermediate plate 500b again in the positive z-direction up to a fourth bearing surface A _4b folded and from there again in negative z-direction up to a fifth bearing surface A _5b , From this fifth bearing surface A _5b off is the intermediate plate 500b folded to the main extension plane in the positive z-direction.

The first edition E _{A1,3, b} of the third profiled area 523b is thus in this example by the second bearing surface A _2b and through the fourth bearing surface A _4b educated. The second edition E _{A2,3, b} of the third profiled area 523b is doing through the first bearing surface A _1b , through the third bearing surface A _3b and through the fifth support surface A _5b educated.

In 4c is a further preferred embodiment of an intermediate plate 500c shown schematically, which also at its edge regions two profiled areas 521c and 522c and two non-profiled areas 511c and 512c ,

Between these unprofiled areas 511c and 512c has the intermediate plate 500c However, in this example, no third profiled area, but a one-sided profiled area 523c on.

In this one-sided profiled area 523c is the intermediate plate 500c in the negative z-direction from the main extension plane to a first bearing surface A _1c folded and from this in the positive z-direction again up to the main extension plane. This first contact surface A _1c thus forms another second edition area E _{A2,3, c} , From this one-sided profiled areas 523c thus becomes just another second edition E _{A2,3, c} provided, but no other first edition.

Another preferred embodiment of an intermediate plate 500d is in 4d shown schematically. Also the intermediate plate 500d has at its edges two profiled areas 521d and 522d on. Furthermore, the intermediate plate 500d three more profiled areas 523d . 524d and 525d and four unprofiled areas 511d . 512d . 513d and 514d. The shape of the profiles in the profiled areas 523d . 524d and 525d corresponds to the shape of the profile of the profiled area 523a the intermediate plate 500a out 4a , but mirrored on the x-axis. The profiled areas 523d . 524d and 525d are arranged in the x-direction, in particular at equidistant intervals, ie the widths of the non-profiled areas 511d . 512d . 513d and 514d is particularly identical in each case.

In 4e is a further preferred embodiment of an intermediate plate shown schematically and designated 500e. Analogous to the intermediate plate 500a out 2a also has this intermediate plate 500e at its edge regions two profiled areas 521e and 522e on as well as a third profiled areas 523d and two unprofiled areas 511e and 512e ,

In contrast to the embodiments shown so far, the intermediate plate 500e not folded at right angles, but the profile of the intermediate plate 500e has in each of the three profiled areas on a sinusoidal shape.

The first edition areas E _{A1,1, e} and E _{A1,2, e} of the first profiled area 521e and the second profiled area 522e as well as the second edition areas E _{A2,1, e} and E _{A2,2, e} of the first profiled area 521e and the second profiled area 522e are each not formed as a flat surface, but as support points on rounded areas.

In the third profiled area 523e is the intermediate plate 500e similar to the intermediate plate 500a out 4a initially sinusoidal in the positive z-direction from the main extension plane to a first rounded region A _1e folded, from there sinusoidal in the negative z-direction to a second rounded area A _2e , from there again in a positive z-direction sinusoidal to a third rounded area A _3e and from there back to the main extension level. The rounded areas A _1e and A _3e or their extreme points form the first _{contact area} E _{A1,3, e of} the third profiled area 523e and the second edition area E _{A2,3, e} of the third profiled area 523e gets through the rounded area A _2e or its extreme point formed.

In 5 a channel unit according to a preferred embodiment of a plate heat exchanger according to the invention is shown schematically in a cross-sectional view and designated 401a.

Between a first heat transfer plate 201 and a second heat transfer plate 202a is the intermediate plate 500a arranged as they are in 4a is shown. At the first edition areas of the three profiled areas 521 . 522a and 523a is the intermediate plate 500a each with the first heat transfer plate 201 welded and with the second support areas of the profiled areas 521 . 522a and 523a is the intermediate plate 500a each with the second heat transfer plate 202a welded.

As in 5 can be seen, the channel unit is due to the special shape of the intermediate plate 500a in five subchannels K ₁ to K ₅ divided. These five subchannels K ₁ to K ₅ extend parallel to each other and each allow a passage of a fluid in the same flow direction, which in the example of 5 the y-direction corresponds.

In 6 an intermediate plate according to a preferred embodiment of a plate heat exchanger according to the invention is shown schematically in a perspective view and denoted by 600.

As in 6a can be seen, the intermediate plate has 600 a first profiled area 621 , a second profiled area 622 and a third profiled area 623 as well as two unprofiled areas 611 and 612 on.

In the non-profiled areas are each Strömungsleitelemente 630 in the intermediate plate 600 brought in. This example is in the unprofiled area 611 Strömungsleitpins 631 introduced as flow guide and in the non-profiled area 612 Strömungsleitplatten 632 , which are in particular formed as bent sheets. By such flow guide elements 630 For example, the flow of the fluid passed through the corresponding channel unit can be changed and, in particular, it can be a turbulent flow 601 . 602 . 603 be generated. Through these turbulent currents 601 . 602 . 603 the thermal efficiency of the plate heat exchanger can be increased.

In the 6b and 6c is in each case a section of the intermediate plate 600 shown enlarged. It can be seen that for the as Strömungsleitpin 631 or as Strömungsleitplatte 632 trained flow guide 630 corresponding openings 631a and 632a are provided in the intermediate plate, in which the respective flow guide elements 630 used, in particular can be inserted.

LIST OF REFERENCE NUMBERS

• 1

  100

  Plate heat exchanger

  101

  frame

  101

  steel beams

  101b

  steel beams

  101c

  steel beams

  102

  reversing chamber

  110

  plate pack

  111

  first half of the disk pack

  112

  second half of the disk pack

  F ₁

  first fluid

  F ₂

  second fluid

• 2

  200

  Variety of heat transfer plates

  201

  first heat transfer plate

  202

  second heat transfer plate

  203

  third heat transfer plate

  204

  fourth heat transfer plate

  205

  fifth heat transfer plate

  300

  Variety of profiled intermediate plates

  301

  first intermediate plate

  302

  second intermediate plate

  303

  third intermediate plate

  304

  fourth intermediate plate

  311

  profiled areas

  312

  non-profiled areas

  321

  profiled areas

  322

  non-profiled areas

  400

  Variety of channel units

  401

  first channel unit

  402

  second channel unit

  403

  third channel unit

  404

  fourth channel unit

• 3

  500

  intermediate plate

  511

  unprofiled area

  521

  profiled area

  522

  profiled area

  E _H

  Main plane

  E _A1,1

  first edition

  E _A1,2

  first edition

  E _A2,1

  second edition

  E _A2,2

  second edition

  E _B1

  first boundary surface

  E _B2

  second boundary surface

• 4a

  500a

  intermediate plate

  511a

  unprofiled area

  512a

  unprofiled area

  521

  first profiled area

  522a

  second profiled area

  523a

  third profiled area

  E _{A1,3, a}

  first contact area of the third profiled area

  E _{A2,3, a}

  second edition of the third profiled section

  A _1a

  first contact surface

  A _2a

  second bearing surface

  A _3a

  third contact surface

• 4b

  500b

  intermediate plate

  511b

  unprofiled area

  512b

  unprofiled area

  521 b

  first profiled area

  522b

  second profiled area

  523b

  third profiled area

  E _{A1,3, b}

  first contact area of the third profiled area

  E _{A2,3, b}

  second edition of the third profiled section

  A _1b

  first contact surface

  A _2b

  second bearing surface

  A _3b

  third contact surface

  A _4b

  fourth bearing surface

  A _5b

  fifth bearing surface

• 4c

  500c

  intermediate plate

  511c

  unprofiled area

  512c

  unprofiled area

  521c

  first profiled area

  522c

  second profiled area

  523c

  one-sided profiled area

  E _{A2,3, c}

  second edition of the one-sided profiled area

  A _1c

  first contact surface

• 4d

  500d

  intermediate plate

  511d

  unprofiled area

  512d

  unprofiled area

  513d

  unprofiled area

  513d

  unprofiled area

  521d

  first profiled area

  522d

  second profiled area

  523d

  third profiled area

  524d

  fourth profiled area

  525d

  fifth profiled area

• 4e

  500e

  intermediate plate

  511e

  unprofiled area

  512e

  unprofiled area

  521e

  first profiled area

  522e

  second profiled area

  523e

  third profiled area

  E _{A1,1, e}

  first contact area of the first profiled area

  E _{A2,1, e}

  second edition of the first profiled area

  E _{A1,2, e}

  first contact area of the second profiled area

  E _{A2,2, e}

  second support area of the second profiled area

  E _{A1,3, e}

  first contact area of the third profiled area

  E _{A2,3, e}

  second edition of the third profiled section

  A _1e

  first rounded area

  A _2e

  second rounded area

  A _3e

  third rounded area

• 5

  201

  first heat transfer plate

  202a

  second heat transfer plate

  401

  channel unit

  K ₁

  subchannel

  K ₂

  subchannel

  K ₃

  subchannel

  K ₄

  subchannel

  K ₅

  subchannel

• 6

  600

  intermediate plate

  601

  turbulent flow

  602

  turbulent flow

  603

  turbulent flow

  611

  unprofiled area

  612

  unprofiled area

  621

  first profiled area

  622

  second profiled area

  623

  third profiled area

  630

  flow guide

  631

  Strömungsleitpin

  631 a

  Opening for the Strömungsleitpin

  632

  baffle plate

  632a

  Opening for the flow baffle

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 2011/0017436 A1 [0004, 0005]

Claims (18)

A plate heat exchanger (100) comprising a plate pack (110) comprising a plurality of planar, parallel heat transfer plates (200, 201, 202, 203, 204, 205, 201a, 202a) and a plurality of profiled intermediate plates (300, 301, 302, 303 , 304, 500, 500a, 500b, 500c, 500d, 500e, 600), wherein in each case between two adjacent heat transfer plates of the plurality of heat transfer plates (200, 201, 202, 203, 204, 205, 201a, 202a) in each case an intermediate plate of the plurality intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) is arranged, wherein at least one intermediate plate of the plurality of intermediate plates (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e) as a plate having at least one non-profiled portion (312, 322, 511, 511a, 512a, 511b, 512b, 511c, 512c, 511d, 512d, 513d, 514d, 511e, 512e, 611, 612) and having at least two profiled regions (311, 321, 521, 522, 521a, 522a, 523a, 521b, 522b, 523b, 52 1c, 522c, 521d, 522d, 523d, 524d, 525d, 521e, 522e, 523e, 621, 622, 623) is formed in a main extension plane (E _H ) of the plate. Plate heat exchanger (100) after Claim 1 wherein a space between each pair of adjacent heat transfer plates (200, 201, 202, 203, 204, 205, 201a, 202a) is defined by the respective intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c , 500d, 500e, 600). Plate heat exchanger (100) after Claim 1 or 2 , wherein profiles of each two adjacent intermediate plates (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) are mutually rotated by a predetermined angle of preferably 90 °. Plate heat exchanger according to one of the preceding claims, wherein each two adjacent heat transfer plates (200, 201, 202, 203, 204, 205, 201a, 202a) and the intermediate plate arranged therebetween (300, 301, 302, 303, 304, 500, 500a, 500b , 500c, 500d, 500e, 600) form a channel unit (400, 401, 402, 403, 404, 401a) for the passage of a fluid (F ₁ , F ₂ ). Plate heat exchanger (100) after Claim 4 wherein the channel unit (400, 401, 402, 403, 404, 401a) is bounded by a profile of the corresponding intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e) and wherein a flow direction of the channel unit (400, 401, 402, 403, 404, 401a) through a main extension direction of the profile of the corresponding intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) is defined. Plate heat exchanger (100) after Claim 5 in which in each case three adjacent heat transfer plates (200, 201, 202, 203, 204, 205, 201a, 202a) and the respective intermediate plates (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) form two adjacent channel units (400, 401, 402, 403, 404, 401a), wherein a first of these two adjacent channel units (400, 401, 402, 403, 404, 401a) extends in a first flow direction and wherein the other of the two adjacent channel units (400, 401, 402, 403, 404, 401a) extends in a second flow direction, wherein the first flow direction and the second flow direction are orthogonal to each other. A plate heat exchanger (100) according to any one of the preceding claims, wherein the at least one non-profiled region (312, 322, 511, 511a, 512a, 511b, 512b, 511c, 512c, 511d, 512d, 513d, 514d, 511e, 512e, 611, 612) defines the main plane of extent (E _H ) of the plate, the plate in each of the at least two profiled regions (311, 321, 521, 522, 521a, 522a, 523a, 521b, 522b, 523b, 521c, 522c, 521d, 522d , 523d, 524d, 525d, 521e, 522e, 523e, 621, 622, 623) are each folded in such a way that a first contact area (E _A1,1 , E _A1,2 , E _{A1,3, a} , E _{A1,3 , b} , E _{A1,3, e} ) and a second contact area (E _A2,1 , E _A2,2 , E _{A2,3, a} , E _{A2,3, b} , E _{A2,3, e} ) are provided, wherein the first bearing area (E _A1,1 , E _A1,2 , E _{A1,3, a} , E _{A1,3, b} , E _{A1,3, e} ) extends in a first plane parallel to the main _{extension plane} (E _H ), and wherein the second bearing area (E _A2,1 , E _A2,2 , E _{A2,3, a} , E _{A2,3, b} , E _{A2,3, e} ) in a to the main _{plane of extension} (E _H ) p The first plane and the second plane each lie on opposite sides of the main extension plane (E _H ) in each case at a predetermined distance (Δz ₁ , Δz ₂ ) to the main extension plane (E _H ). Plate heat exchanger (100) after Claim 7 wherein a first profiled region (521, 521a, 521b, 521c, 521d, 521e, 621) is disposed at a first edge region of the plate, and wherein a second profiled region (522, 522a, 522b, 522c, 522d, 522e, 622) is arranged on a second edge region of the plate, wherein the first edge region and the second edge region are opposite. Plate heat exchanger (100) after Claim 7 or 8th , wherein on the first support area (E _A1,1 , E _A1,2 , E _{A1,3, a} , E _{A1,3, b} , E _{A1,3, e} ) a first heat transfer _plate rests and wherein on the second support area (E _A2,1 , E _A2,2 , E _{A2,3, a} , E _{A2,3, b} , E _{A2,3, e} ) a second heat transfer plate rests in the plate pack (110) adjacent to the first heat transfer plate. Plate heat exchanger (100) after Claim 8 and 9 as far back referring to Claim 5 wherein the at least one intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) and the two adjacent heat transfer plates (200, 201, 202, 203, 204, 205, 201a , 202a) form a channel unit (400, 401, 402, 403, 404, 401a), wherein the channel unit (400, 401, 402, 403, 404, 401a) is defined by the first profiled region (521, 521a, 521b, 521c, 521d, 521e, 621) and the second profiled portion (522, 522a, 522b, 522c, 522d, 522e, 622) of the at least one intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d , 500e, 600) and wherein the flow direction of the channel unit (400, 401, 402, 403, 404, 401a) through a main extension direction of the first profiled region (521, 521a, 521b, 521c, 521d, 521e, 621) and the second profiled portion (522, 522a, 522b, 522c, 522d, 522e, 622) of the at least one intermediate plate (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600). Plate heat exchanger (100) after Claim 9 or 10 , as far as referring back to Claim 2 , wherein a distance (Δz) between the first support area (E _A1,1 , E _A1,2 , E _{A1,3, a} , E _{A1,3, b} , E _{A1,3, e} ) and the second support area (E _{A2 , 1} , E _A2,2 , E _{A2,3, a} , E _{A2,3, b} , E _{A2,3, e} ) defines the distance between the two adjacent heat transfer _plates . Plate heat exchanger (100) according to one of Claims 7 to 11 , as far as referring back to Claim 3 wherein at least two adjacent intermediate plates (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) are each formed as a plate with at least one non-profiled region (312, 322, 511, 511a, 512a, 511b, 512b, 511c, 512c, 511d, 512d, 513d, 514d, 511e, 512e, 611, 612) and having at least two profiled areas (311, 321, 521, 522, 521a, 522a, 523a, 521b, 522b , 523b, 521c, 522c, 521d, 522d, 523d, 524d, 525d, 521e, 522e, 523e, 621, 622, 623), the main directions of extension of the at least two profiled regions (311, 321, 521, 522, 521a , 522a, 523a, 521b, 522b, 523b, 521c, 522c, 521d, 522d, 523d, 524d, 525d, 521e, 522e, 523e, 621, 622, 623) of the at least two adjacent intermediate plates (300, 301, 302, 303 , 304, 500, 500a, 500b, 500c, 500d, 500e, 600) are mutually rotated by a predetermined angle of preferably 90 °. Plate heat exchanger (100) according to one of Claims 7 to 12 in that the plate has at least one single-sided profiled area (523c) in which the plate is folded such that a further first support area or a further second support area (E _{A2,3, c} ) is provided. The plate heat exchanger (100) according to any one of the preceding claims, wherein at least one flow plate is provided in at least one intermediate plate (600) of the plurality of intermediate plates (300, 301, 302, 303, 304, 500, 500a, 500b, 500c, 500d, 500e, 600) (630, 631, 632) is introduced. Plate heat exchanger (100) after Claim 14 wherein the at least one flow guiding element (630, 631, 632) is inserted into at least one opening (631a, 632a) in the at least one intermediate plate (600). Plate heat exchanger (100) after Claim 14 or 15 wherein at least one Strömungsleitpin (631) and / or at least one Strömungsleitplatte (632) are introduced as the at least one flow guide. A method of performing heat exchange of fluids of a burner using a plate heat exchanger (100) according to any one of the preceding claims, wherein fuel gas or combustion air or a gas mixture of combustion gas and combustion air is passed as a first fluid through the plate pack (110) of the plate heat exchanger (100) and then supplied to the burner, and wherein a combustion exhaust gas is led from the burner to the plate heat exchanger (100) and passed as a second fluid through the plate pack (110) of the plate heat exchanger (100). Method according to Claim 17 wherein the burner is used in the synthesis gas production.

Images