EP2136175B1 - Heat transfer plate, plate pair, plate stack, compact plate heat exchanger and its manufacturing process - Google Patents

Description

The invention relates to a heat transfer plate for a fully welded compact plate heat exchanger having a thermally effective surface with a profile, a first and a second passage opening for a second flowing medium, which are arranged over the thermally effective surface, and a circumferential profile-free welding edge. The invention further relates to a fully welded compact plate heat exchanger and a method for its production.

From the EP 0984 233 B1 For example, an elongated profiled heat transfer plate for a plate heat exchanger having a brazed plate pack is known. This heat transfer plate has a rectangular shape which is arc-shaped at the end faces. In the arcuate head portions a lying on a common center line inlet or outlet opening is provided for the one medium, wherein the center line is equal to the longitudinal axis of the heat transfer plate. The heat transfer surface is formed with a herringbone pattern and parallel to the main flow direction elevation and of a circumferential edge region limited, which lies with the apex of the ribs in a plane, the elevations and ribs emanating from this plane. To form a plate pack, two heat transfer plates are welded to the cartridge along their peripheral edges and form a plate gap, which is flowed through the inlet and outlet openings of the one medium and two stacked cassettes are welded around the inlet and outlet openings around and form one Plate gap, the shell side is flowed through by the second medium. In addition, at least the contiguous heat transfer plates in each second plate interspace are brazed to where the profile or elevations of the heat transfer surface contact to achieve a plurality of connection points with the goal that the elevations do not transmit forces between the heat transfer plates. Such a formed heat transfer plate has on the one hand as a result of the surveys on an unfavorable flow characteristics in the formed plate interstices and on the other hand reduces the effective thermal surface. Furthermore, despite the brazed supports no pressure stability in the adjacent plate interspaces can be achieved, which makes it possible to use a plate pack formed in welded compact plate heat exchangers, in which the media of the adjacent plate interstices with high pressure and temperature differences are flowed through. But also the welding of two heat transfer plates on the peripheral edge region, which lies with the apexes of the ribs on a plane, the ribs and the elevations emanating from this plane, and the subsequent welding of the cassettes at the passage openings to a plate package leads due to the inevitable occurring Tension in welding to constant tension in the plate package, which is caused by the Weld and the brazed joint must be included. However, these stresses can lead to cracks in the joints at high pressure and temperature differences in the plate gaps and thus to a leaking of the plate pack and to a changed flow characteristics in the plate interstices, which significantly affects the efficiency of a compact plate heat exchanger.

From the DE 10 2004 022 433 B4 a rectangular heat transfer plate is known, the heat transfer surface is limited by arcuate head portions and in which an inlet or outlet opening on a center line, which is equal to the longitudinal axis of the heat transfer plate, located in the head parts. In this heat transfer plate, the rectangular part of the heat transfer surface and the two head parts are formed with a corrugated profile having a rectilinear and transverse [alpha] wave structure in the edge region of the heat transfer surface and the head parts surrounding a profile-free welded edge at the periphery of the heat transfer plate same width forms. To form the plate pack two of these heat transfer plates are welded at the periphery of the passages to plate pairs forming the plate space for the shell side flowing medium and then the plate pairs are welded to the circumferential profile-free welding edge and form the plate gap for the medium, the plate package on the one - flows through and outlet openings. The heat transfer plates and the plate pairs are joined together without tools and rely exclusively on the points of contact of the profile of the heat transfer surface, so that on the one hand, the heat transfer surface is completely used thermally and on the other hand the flow characteristics in the plate gaps are not affected. Although this heat transfer plate has the profile-free circumferential welding edge of the same width over a homogeneously circumferential welding path, which usually allows a uniform weld, but the problem was found that the welding of two heat transfer plates can be performed without tension to a pair of plates. Consequently, there is tension distortions of the two heat transfer plates, which make a gas-tight welding of the pairs of plates on the profile-free welding edge on the one hand production technology considerably and on the other subject to the running circumferential weld a constant voltage, depending on the pressure conditions in the plate interspaces with the duration to cracks in the circumferential weld and thus can lead to a leaky plate package. Consequently, additional technical measures are required in the storage of the plate pack in a housing to relieve the circumferential welds of these voltages and to operate a plate pack formed with these heat transfer plates, even at high pressure and temperature differences with pressure-stable plate interspaces in a housing.
Furthermore, it is off CH 245 491 A a heat exchanger consisting of at least one bundle in pairs sealed sealing plates known. DE 198 46 518 A1 discloses a heat exchanger having a stack of shell-shaped heat exchanger plates according to the preamble of claim 1. This known plate stack forms a hangerless exhaust gas heat exchanger, with soldering preference being given to welding.

From the US 5,983,992 and the EP 1281 921 A2 a heat transfer plate for a plate heat exchanger is known in which two media flow through a formed from these heat transfer plates plate package from the outside and inside in countercurrent. The Heat transfer plates consist of a rectangular profiled heat transfer surface which is arranged at an angle to the end face mutually staggered inlet and outlet openings so that the inlet and outlet openings are laterally adjacent to the longitudinal sides of the heat transfer surface. The flow connection on one side of the heat transfer plate from the inlet opening via the angled heat transfer surface to the outlet takes place on the one hand via a correspondingly profiled and triangular-shaped manifold section having one longitudinal side and a correspondingly profiled and triangular-shaped collector section and the other side of the angled lying Heat transfer surface limited, wherein the other side is flowed on the shell side, in which the mutually free areas between the heat transfer surface and the peripheral edge of the heat transfer plates are formed only with spacer cams. To form the plate pack heat transfer plates are stacked and soldered together in a brazing furnace. This heat transfer plate has only a short thermally effective length. In addition, this heat transfer plate is not suitable due to their structural design for compact plate heat exchangers with a small footprint, which must ensure a reliable function with high efficiency, even at high pressure and temperature differences in the adjacent plate interstices.

The object of the invention is therefore to improve the heat transfer plates mentioned above in that the ratio of the designed surface of a heat transfer plate is improved in favor of the thermally effective heat transfer surface and interpret the heat transfer plate so that the welding of heat transfer plates on the periphery of Passages to plate pairs can be done stress-free to keep the welds of a welded plate package free of internal stresses, also the peripheral edges of the heat transfer plates have a uniformly homogeneous course, which ensures an automated welding of the plate pairs at the peripheral edges and to propose a compact heat plate with this heat transfer plate, in which a plate pack is metallically sealed in a housing, even at very high pressure differences and temperature differences of -200 to +1200 ° C in the adjacent plate interstices ensures a constant pressure stability and its throughput is small in a small space within wide limits variable.

According to the invention the object is achieved with a generic heat transfer plate mentioned above, wherein the thermally effective surface of the heat transfer plate is bounded on both sides by a plate portion having a passage opening, wherein the plate portions outside the thermally active surface and each other are formed diagonally offset on the heat transfer plate and so thermally effective surface are placed, that the thermally effective surface is flowed directly through the passage opening and wherein the circumferential profile-free welding edge are formed at the frontal transitions of the boundary of the thermally effective surface to the plate portions and the diagonally opposite corners of the thermally effective surface with radii equal to the radius that circumscribes the plate sections.

Due to the diagonally offset plate sections and the uniform radii at the peripheral edges of the heat transfer plate has surprisingly been found that due to the exposed plate sections for the most part and the associated improved heat dissipation and lateral expansion possibilities when welding the pairs of plates at the passages and the plate pairs at the peripheral edges of the stresses occurring during the welding process were minimized so that no warping of the plate pairs were detectable after welding and approximate a plate package welded from these plate pairs was free of tension. Consequently, it was a prerequisite that the connecting welds of a welded plate package need not compensate for stresses and the manufacturing process for welding the pairs of plates at the peripheral edges in conjunction with the uniform radii designed simplified with a consistent sealing weld quality could be performed.

By the above the thermally effective area defined passage openings and the proportion of the thermally effective area was increased to the total area of a heat transfer plate, so that with the same material use a higher efficiency of a heat transfer plate is achieved.

Preferably, the profile of the thermally effective surface is formed with a wave profile profile that expires in the adjacent region of the passage openings.
However, it can also be advantageous if between the profile of the thermally effective surface and the passage openings, a profiled inflow region or outflow region extending transversely to the thermally effective surface is provided. Both embodiments do not affect the advantages achieved with the heat transfer plate and are freely selectable depending on the selected wave structure and the pressure loss to be reached in the plate package.

Preferably, the profile of the profiled thermally effective surface on a continuous wave structure which extends transversely or at an equal angle to the thermally active surface.
However, the profile of the thermally effective surface may also have a herringbone-like wave profile. In these cases, it is advantageous if between the wave structure and the passage openings of the already mentioned inflow or outflow is placed to distribute the inflowing medium over the thermally effective area more evenly or smoothly introduce over the discharge area in the outlet opening.

The compact plate heat exchanger consists of a housing with frontally and shell side arranged inlet and outlet nozzle and at least one incorporated therein plate pack consisting of two each connectionless joined heat transfer plates according to the invention, the sealing at the periphery of the passages to a pair of plates and connection-free adjoined plate pairs on the periphery of the plate pairs are welded and in which a medium flows through the end-lying passage openings formed plate interstices of the adjacent plate pairs and at least a second medium flows through the shell-side connecting piece of the housing, the plate interspaces of the plate pairs, wherein at least one of two connectionless stacked plate pairs existing and by two End plates for connecting the inlet or outlet nozzle limited plate package in the housing übe r the upper housing plate, the lower housing plate and the side parts is clamped metallically sealed, in which the plate package are clamped together with the housing plate and the side parts under a predetermined clamping pressure and after reaching the clamping pressure, the housing parts are welded together with the side parts to a pressure-resistant housing shell.

This compact plate heat exchanger according to the invention is very economical to produce and ensured by the clamping of the plate pack between the upper and lower housing plate and the two side parts, which are welded to a housing shell after clamping, even without further aids a very pressure stable embedded plate package, which is independent of printing and temperature differences in the adjacent plate interspaces over the length of the thermally effective surfaces and also over the length of the heat transfer plates themselves has a high pressure stability. Consequently, even without an additional metallic connection of the mutually supporting heat transfer plates, for example by brazing, it can be ensured that the flow cross sections of the plate interspaces remain stable and thus the designed flow characteristic and the pressure loss of the plate pack remain constant. Rather, by the compact embodiment, a compact plate heat exchanger can be provided, which requires a very small footprint with the same capacity compared to comparable heat exchangers.

In addition, a plate package formed with the heat transfer plate according to the invention can also be used in compact plate heat when it is to be operated in countercurrent or direct current or else in crossflow.

In certain design types of compact plate heat exchangers, it is advantageous if a filler material is inserted between the side parts and the plate package, which together with the Plate package, the cover plates and the side parts is braced. This can be inserted in a very simple way and without tools, the filler to minimize a possible bypass flow.

In this case, the filling material is preferably a metal mesh or a wire mesh or a glass graphite knit.

The fillers are wear-free and temperature-resistant and pressure-resistant and do not affect the service-free operation and the potential applications of the compact plate heat exchangers.

Preferably, the end plates of the plate pack are non-profiled end plates having a thickness greater than the thickness of a heat transfer plate, wherein the inlet or outlet nozzle is welded or connected via a seal to the end plates. Through these end plates, the connecting pieces for the inflow and outflow of the second medium can be easily attached to the plate pack. Rather, by the end plates, the lower and upper cover plate of the housing with the same stability and pressure safety of the plate pack can be made thinner, since the inner clamping forces of the plate pack are already approximately compensated by the two cover plates.

As with other known housings for heat exchangers, the front sides of the housing are gas-tight welded or releasably gas-tight and pressure stable fixed to the housing shell. The manner of the frontal closure of the housing is dependent on the type and intended use of Kompaktplattenwärmeübertragers.

In compact plate heat exchangers, which are to be used for very high pressures, it is advantageous if the uniform pressure stability in the plate pack over the length of the plate pack is supported by at least two staggered ribs, which circumscribe the housing casing of the housing closed. The arrangement of the closed ribs is ensured in particular for longer plate packs, but generally no pressure deformation across the length of the plate package deformation due to the internal pressure in the plate package on the housing shell occurs inevitably due to the freely joined heat transfer surfaces to a change in the cross section of the plate interspaces would lead in the plate package and thus negatively influenced the flow characteristics of the media. On the other hand, the thickness of the plates which form the housing shell can also be reduced by the closed ribs, which can be arranged several times on the housing jacket, without adversely affecting the pressure stability of the plate package.

The ribs may consist of rib sections which are formed or welded in the lower and upper cover plate and the side parts and whose adjacent ends are welded together or the ribs are prefabricated rings in the form of the housing shell, which are shrunk onto the housing shell.

According to another preferred embodiment of the invention at least two plate packs are arranged in a housing, each separated by a partition connected to the end portions of the housing, wherein the Plattenzwischenraume the adjacent plate packs are alternately flowed through by each of the two media in countercurrent, in the mutually the adjacent on one level through openings of the heat transfer plates of two adjacent plate packs are short-circuited by a pipe bend, the upper and / or lower housing plate permeates gas-tight and each partition is alternately fixed to the front part and extends at least over the length of the plate packs to be separated and frontally between two adjacent plate packs and the opposite end portion forms an overflow area. In this way, the compact plate heat exchanger can be designed to be very pressure stable with a size of heat transfer plates, which can be designed very pressure stable, for very high throughput in the high pressure range and also for large pressure differences between the media flowing through. Due to the changing flow direction of the media in the individual plate packs and the possibility that the two media flowing can be performed both in DC as well as in countercurrent, the condition is given that the thermal process in the compact plate heat exchanger to different applications for the thermal treatment of two or several media can be better adapted.

According to another preferred embodiment of the invention in the housing one or more juxtaposed and separated by a partition stack of parcels are used and each stack of parcels consists of uniformly offset in the horizontal plane plate packs, which are separated from each other by separating plates, wherein the plate interstices of the staggered plate packs Packet stack separated and the plate spaces of the staggered plate packs of a stack of plates together from the first medium in the same flow direction directly from a gas-tight welded to the housing manifold and collector and associated spigot, each gas-tight welded at the periphery of the passage opening of the heat transfer plate of the adjacent plate pack shell side are flowed through and that the second medium in a flow direction the Plate interspaces of all clamped together in the housing plate packs flows through the front side. With this embodiment, the compact plate heat exchanger can be designed with a very high throughput, which requires a relatively small footprint. Due to the large number of plate packs, which also consist of heat transfer plates of a size that is very stable in pressure, this embodiment of the compact plate heat exchanger can also be used up to the highest pressure ranges for thermal treatment of the media.

An advantage of this embodiment is also when the plate interstices of each uniformly staggered plate packs of a plate stack are flowed through separately associated inlet and outlet ports, which are gas-tight welded at the periphery of the passage opening of the heat transfer plate of the offset adjacent plate pack and in the penetration region of the housing. In this way, the shell side flowed through plate interstices of the plate packs of the plate stack, which are offset in a common horizontal plane, are simultaneously flowed through by different media, wherein the front-side flowed through plate interstices of Kompaktplattenwärmeübertragers are only flowed through by a medium. Consequently, this extends the field of application of the compact plate heat exchanger and such a compact plate heat exchanger can be operated with a significantly improved cost-benefit ratio.

According to a further preferred embodiment of the invention, a filling material is inserted between each partition wall and the longitudinal sides of the respective stack of packages and the filling material is sealed by means of a Ableitblechs. This will be temperature bridges between the adjacent Disk packs or plate stacks and thus prevents temperature flashovers on the adjacent plate pack or the adjacent plate stack. At the same time it is excluded in this way that creates a bypass between the longitudinal sides of the plate packs and the partitions.

By this multiple arrangement of plate packs with heat transfer plates, which can be designed in a size that has a very high stability on the pressure side and the additional reinforcement of the housing with circumferential ribs, the conditions is created that the compact plate heat exchanger easily with any large heat transfer surfaces for the highest Pressure ranges can be designed pressure stable.

Further details of the invention will become apparent from the following detailed description and the accompanying drawings, in which a preferred embodiment of a Kompaktplattenwärmeübertragers are shown.

• Fig. 1: : eine erfindungsgemäße Wärmeübertragungsplatte,
• Fig. 1A: : eine erfindungsgemäße Wärmeübertragungsplatte mit einem gespiegelten Profilverlauf in der thermisch wirksamen Fläche gegenüber der Wärmeübertragungsplatte von Fig. 1,
• Fig. 1B: : eine weitere Ausführungsform der Wärmeübertragungsplatte nach Fig.1,
• Fig. 2: : ein schematisch dargestelltes Plattenpaket mit Wärmeübertragungsplatten nach Fig.1 oder Fig. 1A,
• Fig. 3: : einen Kompaktplattenwärmeübertrager mit einer Wärmeübertragungsplatte nach Fig. 1 und Fig. 1A,
• Fig. 4: : einen Schnitt durch einen Gehäuseabschnitt mit einem eingelegtem Plattenpaket nach Fig. 2,
• Fig. 5: : einen Schnitt A-A von Fig. 3,
• Fig. 6: : eine weitere Ausführungsform des Kompaktplattenwärmeübertragers mit zwei Plattenpaketen,
• Fig. 7: : einen Schnitt A-A von Fig. 6,
• Fig. 8: : einen Schnitt B-B von Fig. 6,
• Fig. 9: : einen Schnitt durch eine weitere Ausführungsform eines Kompaktplattenwärmeübertragers mit drei Plattenpaketen,
• Fig. 10: : eine weitere Ausführungsform eines Kompaktplattenwärmeübertragers mit drei Plattenstapeln,
• Fig. 11: : einen Schnitt A-A von Fig. 10,
• Fig. 12 : einen Schnitt B-B von Fig. 10.

In the drawings show:

• Fig. 1 : a heat transfer plate according to the invention,
• Fig. 1A : a heat transfer plate according to the invention with a mirrored profile profile in the thermally effective area relative to the heat transfer plate of Fig. 1 .
• Fig. 1B : another embodiment of the heat transfer plate after Fig.1 .
• Fig. 2 :: a schematically represented plate package with heat transfer plates after Fig.1 or Fig. 1A .
• Fig. 3 :: a compact plate heat exchanger with a heat transfer plate behind Fig. 1 and Fig. 1A .
• Fig. 4 :: a section through a housing section with an inserted plate package after Fig. 2 .
• Fig. 5 :: a section AA of Fig. 3 .
• Fig. 6 : another embodiment of the compact plate heat exchanger with two plate packs,
• Fig. 7 :: a section AA of Fig. 6 .
• Fig. 8 :: a cut BB from Fig. 6 .
• Fig. 9 FIG. 1 shows a section through a further embodiment of a compact plate heat exchanger with three plate packs, FIG.
• Fig. 10 : another embodiment of a compact plate heat exchanger with three plate stacks,
• Fig. 11 :: a section AA of Fig. 10 .
• Fig. 12 : a cut BB from Fig. 10 ,

In the Fig. 1 shown heat transfer plate 3 and the in Fig. 1A shown heat transfer plate 3a with mirrored profile profile of the thermally effective surface opposite the thermally effective surface of the heat transfer plate 3 are drawn from a die heat transfer plates 3, 3a, which consist of a profiled rectangular thermally effective surface 17, on both sides by plate sections 12, 12a with a passage opening eighth or 9 is limited.

The thermally effective surface 17 is, as in Fig. 1 to Fig. 1A shown, provided with a retracted profile 18, which in these cases preferably has a wave structure which extends straight at an equal angle [alpha] to the longitudinal axis and into the edge region 19 of the thermally active surface 17 and in the edge region 19 of thermally effective surface 17 forms a circumferential profile-free welding edge 20 of equal width. Of course, the wave structure of the profile 18 may also include a herringbone-like wave structure or other wave structures, which is then also formed into the edge region 19 of the thermally active surface and a profile-free welding edge 20 of equal width.

The thermally effective surface 17 is on both sides of plate portions 12; 12a limited, wherein the plate portions 12, 12a in the longitudinal axis of the thermally active surface 17 are mutually offset diagonally and outside but over the thermally effective surface 17. The plate sections 12; 12a have a circular peripheral edge and a dimension resulting from the sum of the diameter of a passage opening 8; 9 of the width of the profile-free welding edge 20 of the thermally effective surface 17 results. The transitions 6, 6a of the plate sections 12, 12a to the edge region 19 of the thermally active surface and the diagonally opposite corners 7, 7a of the thermally active surface 17 are formed with a radius equal to the radius of the plate sections 12, 12a. In this way it is achieved that on the one hand, the heat transfer plate 3 is rotated by a homogeneous welding edge 20 of equal width, which is very advantageous for the welding of the plate pairs to a plate package and on the other hand, improved evasion and improved heat dissipation in the welding of two heat transfer plates. 3 to a plate pair on the circumference of the passage openings 8 and 9 achieved.

Due to the dimension and position of the plate sections 12, 12 a with the passage openings 8, 9 outside but above the thermally active surface 17, the profile 18 of the thermally effective surface up to the Through openings 8, 9 are formed, as in Fig. 1 and Fig. 1A shown or as in Fig. 1B can be impressed between the passage openings 8, 9 and the thermally effective surface 17, a correspondingly profiled inlet or outflow region 4, via which the thermally effective surface 17 is flowed. If a plate pack 2 of heat transfer plates 3, as in Fig. 1B is formed, of course, the thermally effective area of the heat transfer plate 3 of the plate pair is formed with a mirrored profile 18, as in Fig. 1A shown.

An in Fig. 2 shown plate package 2 consists of a number of stacked plate pairs 5 - 5x, the stack of plate pairs 5 - 5x by profile-less end plates 41; 41a is limited on both sides, which are provided according to the design of Kompaktplattenwärmeübertragers with openings that are congruent to the passage openings 8; 9 of the heat transfer plates 3, 3a lie and where the inlet or outlet pipe 13; 14 are connected.

A pair of plates 5 consists of a heat transfer plate 3 and a heat transfer plate 3a, the connectionless joined together and the circumference 27; 28 of the passage openings 8; 9 gas-tight inside and outside to a pair of plates 5 are welded. In this case, the heat transfer plate 3a relative to the heat transfer plate 3 a mirrored profile profile in the thermally active surface 17, so that the profiles 18 of the thermally effective surfaces 17 of the heat transfer plates 3 and 3a, supported by the wave crests on a plurality of connection-free and point-shaped support points and Form the plate gap 11, which is flowed through the shell side.

The plate pairs 5 formed in this way are stacked according to the capacity of the disk pack 2 to be designed into a stack of disk pairs 5 - 5x, with the adjacent disk pairs 5, 5a; 5x are welded gas-tight to each other on the circumferential profile-free welding edge 20. In this case, the plate pairs 5-5 are stacked in such a way that always two thermally effective surfaces 17 of the heat transfer plates 3, 3a are mutually supported, so that on the intersecting crests of the mirrored profiles 18 turn a variety of connection-free and point-shaped support points arise form the plate gap 10, which is traversed through the passage openings 8, 9.

The so-connected plate pairs 5-5x are on both sides with profile-less end plates 41; 41a, which are each welded gas-tight over the profile-free welding edge 20 of the adjacent heat transfer plate 3 or 3a of the first or last plate pair 5, 5x to the plate package 2.

In these end plates 41, 41 a bores are formed according to the intended embodiment of Kompaktplattenwärmeübertragers lying congruent to the passage openings 8, 9 and lying on the inlet and outlet pipe 13; 14, which penetrate a housing plate 21 and 22 sealed, are determined by a welded connection or releasably sealed connection. Preferably, the end plates 41; 41a has a greater thickness than the heat transfer plates 3, 3a in order to partially compensate for the internal pressure of a plate pack 2 and to relieve the cover plates 21 or 22 of the housing 1 on the pressure side.

In the Fig. 3 to Fig. 4 is the basic system of a compact plate heat exchanger with a housing 1 and a, as described above, formed Plate package 2 shown.

The housing 1 consists of a separately prepared upper housing plate 21 and lower housing plate 22, which are penetrated according to the design of the compact plate heat exchanger of the inlet and outlet ports 13, 14 for the medium and with the end plates 41; 41 a of the plate pack 2 are connected to the side parts 23, 23 a, and the end faces 24, 24 a at the turn according to the design of the compact plate heat exchanger, the inlet and outlet ports 15; 16 are set.

The compact plate heat exchanger consisting of these housing parts and the plate pack formed as described above is executed without seals in such a way that the upper cover plate 21 and lower cover plate 22, which seal the plate packet 2 without seal, together with the side parts 23, 23 a and between the side parts 23, 23a and the plate pack 2 on both sides inserted filling material 29, 29a, in the plate packet-free space each with a discharge plate 30; 30a; 30b; 30c clamped under a predetermined clamping pressure and after reaching the clamping pressure and maintaining the clamping pressure, the upper housing plate 21 and the lower housing plate 22 with the side parts 23, 23a is welded tightly to a housing shell.

With this method of manufacture, the plate pack is pressure-stable and sealed metallic sealed in a pressure-resistant housing shell, which is welded by the end portions 24, 24a with the corresponding fixed inlet and outlet nozzle to a closed housing 1 or sealed sealed.

To further increase the pressure stability of the housing 1 and thus to the pressure stabilization of the jacketed Plate packs 2 over the thermally effective length are preferably provided around the housing shell spaced and self-contained ribs 16-16x, which ensure that even at a very high pressure difference in the plate interspaces 10 and 11 or at pressure shocks always over the length of the plate package. 2 a constant clamping pressure on the housing shell acts on the plate pack 2.

The ribs 16-16x may be ribs 16-16x welded to the shell, which are welded together at the adjoining ends, or closed ribs 16-16x, which have the shape of the shell 1 and are shrunk onto the shell 1.

As in the Fig. 4 . 5 . 7 . 8th . 11 and 12 shown, the filling material 29 - 29x is always between the longitudinal sides of the plate pack 2 and the inner surfaces of the side parts 23, 23a of a plate package and extends over the length and width of the inner surface of the side parts 23, 23a.

The filling material 29-29x is preferably a metal mesh or wire mesh or a glass-graphite knit and is covered on both sides in the plate-packet-free space of the housing 1 with deflector plates 30-30x which are metallically sealed at one end against the inner surfaces of the end parts 24, 24a and at the other end are metallically sealed against the adjacent end faces of the plate package 2.

The clamped in the housing 1 on the housing shell with the filler 29, 29a and Ableitblechen plate pack 2 is tool-free metallically sealed on the axially extending inner surfaces of the housing 1 and is connected to inlet nozzle 13 (14) and outlet nozzle 14 (13), which the housing plate 21st and / or 22 coaxially penetrate and at the periphery of the delimiting bore of the end plates 41, 41 a of the Plate pack 2 and in the penetration area 25; 25a of the housing 1 are preferably welded.

The housing parts 21, 22 and side parts 23, 23a forming the housing 1 are designed in a dimension in which an inserted plate package 2 is clamped metallically sealed in the housing 1 in the horizontal and in the vertical plane and between the two end faces 12; 12a of the plate pack 2 and the end parts 24; 24a of the housing 1, a free inlet or outlet area remains, both, as already mentioned, by Ableitbleche 30 - 30x opposite the filling material 29; 29x are metallically sealed.

In the Fig.5 - 8 is a compact plate heat exchanger shown in which in one of the basic system of the housing after Fig. 3-5 formed housing 1 two with the long sides juxtaposed plate packs 2, 2x the same dimension are clamped. The two plate packs 2, 2x are separated by a partition wall 38, which is fixed metallically sealed on the inside of the end portion 24a, which is provided with the inlet nozzle 15 and the outlet nozzle 16 and extends over the length of the two plate packs 2, 2x and relative to the inside of the end portion 24a an overflow region 33 between the plate packs 2, 2x forms for the medium that flows through the plate interstices 10 of the plate packs 2, 2x frontally.

The flowed through by a media side panel plate spaces 11 of the two plate packs 2, 2x are shorted at the output of the plate pack 2 and at the entrance of the plate pack 2x by a pipe bend 31, the gas-tightly penetrates the lower housing plate 22 with its ends and the circumference 27 of the openings 9 of adjacent heat transfer plates 3; 3a of the plate packs 2, 2x gas-tight welded.

In the length of the inner surfaces of the side parts 23, 23a of the housing and on the length of the two sides of the partition 38, in turn, a filler material is used on both sides in the frontal inlet and outlet region of the housing 1 and both sides of the overflow region 33 by Ableitbleche 30 - 30x metallic is sealed, on the one hand to prevent a temperature flashover between the plate packs 2, 2x and on the other hand to prevent a bypass.

In this embodiment, the plate packs 2, 2 are traversed by each medium in the opposite direction of flow, wherein the media involved can flow both in cocurrent and in countercurrent through the compact plate heat exchanger.

Fig. 9 shows a section of a further possible embodiment of the Kompaktplattenwärmeübertragers with three juxtaposed plate packs 2, 2a, 2x, which in turn in a housing 1 according to the basic system of Fig. 3-5 are tense.

In this embodiment, the partition walls 38, 38x for separating the plate packs 2, 2a, 2x mutually set sealed to the inner surfaces of the end portions 23, 23a and thus form the mutual overflow region 33; 33x for the medium, the front side, the interstices 10 of the plate packs 2, 2a, 2x flows through. The plate interspaces 11 of the plate packs 2, 2a. 2x, the jacket side are flowed through, alternately shorted at the output of the plate package 2 and at the entrance of the plate package 2a and at the output of the plate package 2a and the input of the plate package 2x by elbows 31, 31x gas-tight, the lower housing plate 22 and the upper housing plate 21 penetrate and respectively at the periphery 27 and 28 of the passage opening 9 and 8 of the adjacent heat transfer plate 3; 4 of the plate packs 2 or 2x are welded gas-tight. The insert of the filling material 29, 29a with the Ableitblechen takes place analogous to the embodiment according to Fig. 3 or 4 and is only extended to the middle plate package 2a.

In this embodiment, the plate packs of each medium are successively and alternately flowed through in the opposite direction of flow, in which case the media involved can flow through the compact plate heat exchanger both cocurrent and countercurrent.

Fig. 10 - 12 show another possible embodiment of the compact plate heat exchanger after Fig. 3 to 5 with, for example, three juxtaposed plate stacks 40 - 40 x, which are formed from separate plate packages 2, 2a - 2x and which in turn together with the filling material 29, 29a and the discharge plates 30 - 30x in a housing 1 according to the basic system of Fig. 1 . 2 are tense.

The plate packs 2, 2a, 2x of each plate stack 40-40x are uniformly offset horizontally and in this case by separating plates 39; 39a separated.
The plate interspaces 11 of the plate packs 2, 2a are connected on the inlet side via separately guided connecting pieces 35, 35a to a distributor 34 which is arranged on the casing plate 21 on the casing side and which is directly in communication with the plate interspace 11 of the plate packet 2x. Analogously, the plate interspace 11 of the plate package 2 x exit side and the plate interstices 11 of the plate packages 2, 2 a on the outlet side via separately guided connection piece 35 b, 35 x connected to a shell side on the arranged on the housing plate 22 collector 36. At the distributor 34 of the inlet nozzle 13 and the collector 36, the outlet nozzle 14 is fixed gas-tight, via the one supplied on the shell side together to the compact plate heat exchanger and is discharged.

The plate interspaces 10 of the plate packs 2, 2 a, 2 x of each plate stack 40-40x are flowed through the front side inlet and outlet nozzles together from the first medium end face depending on the connection of Kompaktplattenwärmeübertragers in countercurrent or direct current.

The juxtaposed plate stacks 40 - 40x are separated by partitions 38, 38x having a length approximately equal to the length of an offset plate packet 2, 2a, 2x. The upper and lower housing plates 21, 22 and the two parallel side parts 23, 23a also have a dimension in which the plate stacks 40-40x and the plate packs 2, 2a, 2x of the plate stacks 40-40x with the filling material 29, 29a in and are metallically sealed with the strained housing 1 and in the housing 1 on both sides a free space is guaranteed, that on the one hand during flow of the end face 12 of the plate packs 2, 2a, 2x the plate stack 40 - 40x a preferred flow to the gap 10 is excluded and on the other hand obstruction-free outflow from the plate interspaces 10 of the plate packs 2, 2a, 2x of the plate stacks 40 - 40 is ensured.

If required, however, the plate interstices 11 of the plate packs 2, 2a, 2x of a plate stack 40-40x can be subjected to different media. In this case, the separately guided inlet-side connecting pieces 35, 35a and the outlet-side connecting pieces 35b, 35x are not connected to the distributor 24 or to the collector 36, but the connecting pieces 35, 35a are directly connected to a separate inlet piece 13 or connecting piece 35b, 35x connected with a separate outlet connection 14 are connected.

LIST OF REFERENCE NUMBERS

1

casing

2 - 2x

plate pack

3 - 3a

Heat transfer plate

4

profile-free inflow area

4a

profile-free outflow area

5 - 5x

pair of plates

6, 6a

frontal transitions

7, 7a

opposite corners

8th

Through opening

9

Through opening

10

Plate gap between 2 plate pairs

11

Plate gap in the plate pair

12, 12a

plate sections

13

inlet connection

14

outlet connection

15

end entry ports

16

end-side outlet nozzle

17

rectangular thermally effective surface

18

profile

19

border area

20

profile-free welding edge

21

upper housing plate

22

lower housing plate

23, 23a

side panels

24, 24a

front part

25, 25a

Penetration area - housing

26, 26x

ribs

27

Circumference of the passage openings

28

Circumference of the passage openings

29 - 29x

filling material

30 - 30x

deflector

31 - 31x

Elbows

32, 32a

Penetration housing

33 - 33x

overflow area

34

distributor

35

spigot

35a

spigot

35x

spigot

36

collector

37

spigot

37a

spigot

37x

spigot

38, 38x

partition wall

39, 39a

Divider

40

package stack

40a

package stack

40x

package stack

41, 41a

endplates

Claims (15)

1. Heat exchange plate for a fully welded compact plate heat exchanger, comprising

   - a thermally active surface (17) with a profile (18) ;

   - a first and a second through-opening (8, 9) for a second flowing medium which are arranged above the thermally active surface (17);

   - a peripheral profile-free welding edge (20),

   wherein

   - the through-openings (8, 9) are arranged in a first and a second plate portion (12, 12a), and the plate portions (12, 12a) are arranged so as to be diagonally offset at opposite end faces of the thermally active surface (17); and

   - the peripheral profile-free welding edge (20) semicircularly encloses the through-openings (8, 9) in the region of the plate portions (12, 12a) and adjoins said through-openings in the region of the transition (6, 6a) from the plate portion (12, 12a) to the end face of the thermally active surface (17) with a quarter-circle shape having the same radius,

   characterized in that the through-openings (8, 9) are arranged in the flow region for a first flowing medium.
2. Heat exchange plate according to Claim 1, characterized in that the profile (18) has a continuous wavy structure which is formed transversely or at an angle to the thermally active surface (17).
3. Heat exchange plate according to Claim 1 or 2, characterized in that the profile (18) has a fishbone-like wavy profile.
4. Plate pair for a fully welded compact plate heat exchanger, comprising two heat exchange plates according to one of Claims 1 to 3, characterized in that the heat exchange plates are welded gas-tight on the inside and outside at the circumference of the through-openings (8, 9).
5. Plate pair according to Claim 4, characterized in that the profiles (18) of the heat exchange plates have a mirrored profile shape, with the result that the profiles (18) are mutually supported via a plurality of punctiform or linear supporting points.
6. Plate pack for a fully welded compact plate heat exchanger, comprising at least two stacked plate pairs according to Claim 4 or 5 which are delimited on both sides by profileless end plates (41, 41a), wherein the plate pairs are welded gas-tight to one another at the profile-free welding edge (20) in each case and the end plates (41, 41a) are in each case welded gas-tight to the adjacent heat exchange plate of the first and the last plate pair at the profile-free welding edge (20).
7. Fully welded compact plate heat exchanger, comprising:

   - a housing with connection pieces (13, 14) which are arranged on the shell side and intended for guiding through the second medium, with connection pieces (15, 16) which are arranged terminally in a respective end part (24, 24a) and intended for guiding through a first medium, and with an upper housing plate (21), a lower housing plate (22) and side parts (23, 23a), wherein the housing plates (21, 22) and the side parts (23, 23a) form a housing shell;

   - a plate pack according to Claim 6 which is incorporated in the housing, wherein the first medium flows between the adjacent plates of two plate pairs and the second medium flows between the plates of one plate pair, wherein the plate pack is braced with the housing plates (21, 22) and with the side parts (23, 23a) and is welded to form a pressure-stable housing.
8. Compact plate heat exchanger according to Claim 7, characterized in that a filling material (29) is inserted between the side parts (23, 23a) and the plate pack, which filling material is braced jointly with the plate pack, the housing plates (21, 22) and the side parts (23, 23a).
9. Compact plate heat exchanger according to Claim 8, characterized in that the filling material (29) is a metal braid or a wire knit or a glass graphite knit.
10. Compact plate heat exchanger according to one of Claims 7-9, characterized in that the end plates (41, 41a) have a thickness which is greater than the thickness of a heat exchange plate (3), wherein the connection pieces (15, 16) are welded on or connected to the end plates (41, 41a) by means of a seal.
11. Compact plate heat exchanger according to one of Claims 7-10, characterized in that a plurality of plate packs are arranged next to one another and are in each case separated by a partition wall (38a-38x) connected to the end parts (24, 24a) so as to alternatingly form an overflow region, and wherein the through-openings (8, 9) in the adjacent plate packs are short-circuited by a pipe bend (31, 31x).
12. Compact plate heat exchanger according to Claim 11, characterized in that at least two plate packs are stacked over one another, wherein the plate packs are uniformly horizontally offset from one another and separated by separating plates (39, 39a), wherein a distributor (34) and header (36) for guiding through the first medium via associated connection pieces (35, 35a, 35b, 35x) are welded gas-tight to the respective plate packs and the housing.
13. Compact plate heat exchanger according to one of Claims 7-12, characterized in that a uniform pressure stability of the plate pack (2) over its length is supported at least by two offset ribs (26, 26x) which run in a closed manner around the housing shell of the housing (1).
14. Method for producing a fully welded compact plate heat exchanger, comprising the following steps:

    - producing a plate pair by sealingly welding two heat exchange plates according to one of Claims 1-3 at the circumference of the through-openings;

    - producing a plate pack by joining together previously produced plate pairs and welding at a peripheral profile-free welding edge;

    - arranging a first and a second end plate on the first and on the last plate pair of a plate pack and welding at the profile-free welding edge.
15. Method according to Claim 14, further comprising the following steps:

    - arranging the plate pack in housing parts which comprise an upper and a lower housing plate (21, 22) and also side parts (23, 23a) and end parts (24, 24a);

    - bracing the plate pack jointly with the side parts (23, 23a) and the housing plates (21, 22) with a predetermined clamping pressure;

    - welding the housing plates (21, 22) and side parts (23, 23a) to form a pressure-stable housing shell while maintaining the clamping pressure;

    - welding or releaseably sealingly closing the housing shell with end parts (24, 24a) to form a closed housing.

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