EP2136175A1 - Profiled rectangular heat transfer plate and compact plate heat exchanger produced with same - Google Patents

Abstract

The plate (3) has a thermal active surface (17) limited on both sides by plate sections (12, 12a) with a passage opening (8, 9). The plate sections are formed outside the surface and diagonally offset to the plate. The plate sections are attached to the surface so that the surface flows directly over the opening. A circumferential profile-free welded edge (20) at front transitions (6, 6a) from the limitation of the surface to the plate sections and diagonally opposite edges (7, 7a) of the surface are formed with radii corresponding to a same radius that the plate sections revolves. An independent claim is also included for a compact plate heat exchanger with a profiled rectangular heat transfer plate.

Description

The invention relates to a profiled rectangular heat transfer plate with passages and a circumferential profile-free welding edge of the same width and a compact plate heat exchanger, which consists of a housing with the front side and shell side arranged inlet and outlet nozzle and a disk pack embedded therein, in each case two connectionless joined heat transfer plates on the circumference of Passage openings are welded sealingly to a pair of plates and connection-free adjoining pairs of plates at the periphery of the plate pairs and in which a medium flows through the frontal passage openings formed plate interstices of the adjacent plate pairs and flows through at least a second medium on the shell-side connecting piece of the housing, the plate interspaces of the plate pairs ,

From the EP 0984 233 B1 is a longitudinally profiled heat transfer plate for a plate heat exchanger with a hard soldered plate package 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 bounded by a peripheral edge region which lies in a plane with the apex of the ribs, wherein 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 this way in welded compact plate heat exchangers, in which the media of the adjacent plate interstices are flowed through with high pressure and temperature differences. 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 Tensions when welding to constant stresses in the plate pack, which must be absorbed by the weld and the hard-soldered connection. 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 wave profile having a straight and at an angle α extending wave structure in the edge region of the heat transfer surface and the Head parts forms a circumferential free of the heat transfer plate profile-free welding edge of equal width. 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 is not affected in the plate interspaces. 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 a leaky plate package can lead. 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.

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 placed 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 soldering oven. 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 at the periphery of the passages to plate pairs done stress-free can to keep the welds of a welded plate package free of internal stresses, which also have the peripheral edges of the heat transfer plates 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, wherein a plate package in a housing is metallically sealed, even at very high pressure differences and temperature differences of -200 to + 1200 ° C in de n adjacent plate interspaces ensures constant pressure stability and its throughput is variable within a wide limits with little space required.

According to the invention the object is achieved with a generic heat transfer plate mentioned above, in which 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 are formed outside the thermally effective surface and each other diagonally offset on the heat transfer plate and are placed so to the thermally effective surface, that the thermally effective surface directly through the passage opening wherein the encircling profile-free welding edge is formed at the frontal transitions from 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 surrounds 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 largely exposed plate sections and the associated improved heat dissipation and lateral expansion options when welding the plate pairs at the passages and the plate pairs at the peripheral edges of the During the welding process occurring stresses were minimized so that after welding no discrepancies of the plate pairs were to be recognized and welded from these pairs of plates plate pack was approximately free of stress. 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 active 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 connectionless joined plate pairs at 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 pack is clamped together with the housing plate and the side parts under a predetermined clamping pressure and welded after reaching the clamping pressure, the housing parts with the side panels together to form a pressure-stable housing shell are.

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, regardless of pressure 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 filling material is inserted between the side parts and the plate pack, which is clamped together with the plate pack, the cover plates and the side parts. 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 and pressure resistant and do not affect the service-free operation and the potential applications of 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 connection piece for the inflow and outflow of a 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 package over the length of the plate package is supported by at least two offset ribs, which closes the housing shell of the housing circulate. 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 one-level through openings of the heat transfer plates of two adjacent plate packs are short-circuited by a pipe bend, which penetrates the upper and / or lower housing plate gas-tight and each partition is mutually fixed to the front part and extends at least over the length of the plate packs to be separated and the front side between two adjacent plate packs and the opposite end part 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 flowing media can be performed both in DC and in countercurrent, the condition is given that the thermal process in the compact plate heat exchanger to different applications for the thermal treatment two or more 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 Separate packet stack and the plate interstices of the staggered plate packs of a stack of plates in each case 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 to the circumference of the passage opening of the heat transfer plate of the adjacent plate pack, are flowed through the jacket side and that the second medium flows through the plate interstices of all clamped together in the housing plate packs frontally in a flow direction. 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. Thus, thermal bridges between the adjacent plate packs or stacks of plates and thus temperature flashovers on the adjacent plate pack or the adjacent plate stack are prevented. 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 thermal effective area opposite the heat transfer plate of Fig. 1 .

1B:

a further embodiment of the heat transfer plate after Fig.1 .

Fig. 2:

a schematically illustrated plate pack with heat transfer plates after Fig.1 or Fig. 1A .

3:

a compact plate heat exchanger with a heat transfer plate after Fig. 1 and Fig. 1A .

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:

a further embodiment of the compact plate heat exchanger with two plate packs,

Fig. 7:

a section AA of Fig. 6 .

Fig. 8:

a section BB of Fig. 6 .

Fig. 9:

a section through another embodiment of a compact plate heat exchanger with three plate packs,

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 section BB of 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 preferably has a wave structure in these cases, which extends straight at an equal angle α to the longitudinal axis and into the edge region 19 of the thermally active surface 17 and in the edge region 19 of the thermally active surface 17 a circumferential profile-free welding edge 20 of the same width forms. 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, wherein the plate sections 12, 12a in the longitudinal axis of the thermally active surface 17 are mutually offset diagonally and outside but above the thermally effective surface 17 lie. 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, 12a with the passage openings 8, 9 outside but above the thermally active surface 17, the profile 18 of the thermally effective surface can be formed up to the passage openings 8, 9, 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 shown, is formed, of course, the thermally effective surface 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 plate pack 2 to be designed into a stack of plate pairs 5 - 5x, wherein the respective adjacent plate 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 limited, 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 the basic system of a compact plate heat exchanger is shown with a housing 1 and a plate package 2 formed as described above.

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 production method, the plate pack is pressure-stable and metallically sealed in a pressure-resistant housing jacket enclosed, which is welded by the end pieces 24, 24a with the appropriately defined inlet and outlet nozzle to a closed housing 1 or sealed sealed sealed.

To further increase the pressure stability of the housing 1 and thus to stabilize the pressure of the jacketed plate package 2 over the thermally effective length are preferably spaced around the housing shell and self-contained ribs 16-16x, which ensure that even at a very high pressure difference in the Plate interspaces 10 and 11 or in pressure shocks always over the length of the plate pack 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-pirnite knit and is on both sides in the plate packet-free space of the housing 1 with discharge plates 30 - 30x covered, which are metallically sealed at one end against the inner surfaces of the end portions 24, 24a and metallically sealed at the other end 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 penetrate coaxially and at the periphery of the delimiting bore of the end plates 41, 41 a of the plate pack 2 and in the penetration region 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 38, which is on the inside of the front part 24a, which is provided with the Einstrittsstutzen 15 and the outlet nozzle 16, set metallic sealed and extends over the length of the two plate packs 2, 2x and opposite the inside of the end portion 24a an overflow region 33 between the plate packs 2, 2x forms for the medium , which 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 and 2x gas-tight welded. 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. On the manifold 34 of the inlet nozzle 13 and the collector 36, the outlet nozzle 14 is fixed in a gas-tight manner, via which a medium 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 end face arranged inlet and outlet nozzle together from the second 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 socket 13 or connecting piece 35b, 35x connected, which are connected to a separate outlet nozzle 14.

reference numeral

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 (16)

Profiled rectangular heat transfer plate (3,3a) with through openings (8,9) and a circumferential profile-free welding edge (20) of the same width for a compact plate heat exchanger, the (1) with a front side and shell side arranged inlet and outlet nozzle (15,16; 13, 14) and a plate pack (2) incorporated therein, in which two heat transfer plates (3, 3a-3x) connected to each other at the periphery (27, 28) of the passage openings (8, 9) form a plate pair (5) and connection-free adjoining plate pairs (5-5x) at the periphery of the plate pairs (3,3a, 3x) are sealingly welded and in which a medium on the front side passage openings (8.9) formed the plate intermediate spaces (11) of the adjacent plate pairs (5-9) 5x) flows through and at least a second medium on the shell side lying connecting piece (13,14) of the housing (1) the plate interspaces (11) of the Plat tenpaare (5-5x) flows through characterized in that the thermally effective surface (17) of the heat transfer plate (3) on both sides by a plate portion (12; 12a) having a through opening (8; 9) is limited, wherein the plate portions (12, 12a) outside the thermally active surface (17) and mutually diagonally offset on the heat transfer plate (3) are formed and so to the thermally effective surface (17) are placed, that the thermally effective surface (17) is directly flowed through the passage opening (8,9) and wherein the circumferential profile-free welding edge (20) at the frontal transitions (6; 6a) of the boundary of the thermally effective surface (17) to the plate sections (12; 12a) and the diagonally opposite corners (7; 7a) of the thermally effective surface (17) are formed with radii equal to the radius, which rotates the plate sections (12; 12a). Profiled rectangular heat transfer plate according to claim 1, characterized in that the profile (18) of the thermally effective surface (17) in the adjacent region of the passage openings (8; 9) expires. A profiled rectangular heat transfer plate according to claim 1, characterized in that between the profile (18) of the thermally active surface (17) and the passage openings (8; 9) has a profiled inflow region (4) or outflow region (4a) extending transversely to the thermally effective surface. is provided. Profiled rectangular heat transfer plate according to one of claims 1 to 3, characterized in that the profile (18) of the profiled thermally active surface has a continuous wave structure, which extends transversely or at an equal angle to the thermally effective surface (17). Profiled rectangular heat transfer plate according to one of claims 1 to 3, characterized in that the profile (18) of the profiled thermally active surface has a herringbone-like wave profile. Compact plate heat exchanger, consisting of a housing (1) with inlet and outlet ports (15,16; 13,14) arranged at the front and shell side and at least one plate pack (2) incorporated therein, in each case two heat transfer plates (3,3a) adjoining each other in a connectionless manner Claim 1 inside and outside at the periphery (27; 28) of the passage openings (8; 9) to a pair of plates (5) and connection-free adjoined plate pairs (5-5x) at the periphery of the plate pairs (3,3a, 3x) are sealingly welded and in which a medium flows through the plate-shaped passage openings (11) of the adjacent plate pairs (5-5x) via the end openings (8, 9) and at least one second medium via the casing-side connection pieces (13, 14) of the housing (1) Traversed plate interspaces (11) of the plate pairs (5-5x), characterized in that one of at least two connectionless stacked Plattenp aaren (5-5x) existing and by two end plates (41,41a) for connecting the inlet or outlet nozzle (15; 16) limited plate pack (2) in Housing (1) via the upper housing plate (21), the lower housing plate (22) and the side parts (23,23a) is clamped metallically sealed, in which the plate pack (2) together with the housing plate (21,22) and the side parts (23,23a) are braced under a predetermined clamping pressure and after reaching the clamping pressure, the housing parts (21,22) with the side parts (23,23a) are welded together to form a pressure-resistant housing shell. Compact plate heat exchanger according to claim 6, characterized in that between the side parts (23, 23a) and the plate pack (1) a filling material is inserted, which together with the plate pack (2), the cover plates (21,22) and the side parts (23, 23a) is braced. Compact plate heat exchanger according to claim 7, characterized in that the filler material is a metal mesh or a wire mesh or a glass graphite knit. Compact plate heat exchanger according to one of claims 6 to 8, characterized in that the end plates (41, 41a) are non-profiled end plates (41, 41a) of a thickness greater than the thickness of a heat transfer plate (3), the input or output Outlet nozzle (15; 16) is welded or connected via a seal to the end plates (41; 41a). Compact plate heat exchanger according to one of claims 6 to 9, characterized in that the end faces (24,24a) of the housing (1) are gas-tight welded or releasably gas-tight and pressure-resistant fixed to the housing shell. Compact plate heat exchanger according to one of claims 6 to 10, characterized in that the uniform pressure stability of the plate package (2) over the length of the plate package (2) at least two offset ribs (26,26x) is supported, the housing shell of the housing (1). circulate closed. Compact plate heat exchanger according to claim 11, characterized in that the ribs (16-16x) consist of rib sections which are formed or welded in the lower and upper cover plate (21, 22) and the side parts (23, 23a) and their adjacent ends welded together or the ribs (16-16x) in the form of the housing shell are prefabricated rings shrunk onto the housing shell. Compact plate heat exchanger according to one of claims 6 to 12, characterized in that in a housing (1) at least two plate packs (2-2x) are arranged, each by a with the end portions (24 and 24a) of the housing (1) connected partition (38; 38a - 38x) are separated, the plate spaces (10; 11) of the adjacent plate packs (2-2x) being separated are alternately flowed through by each of the two media in the opposite, in which mutually the passage openings (9) and the passage opening (8) of the heat transfer plates (3) of two adjacent plate packs (2,2a - 2x) by a pipe bend (31; ), which penetrates the housing plate (21, 22) in a gas-tight manner and each partition wall (38, 38a-38x) is mutually fixed on the front part (24, 24a) and extends over at least the length of the plate packs (2, 2a-2) to be separated. 2x) extends and the end face between two adjacent plate packs (2,2a - 2x) and the front part (24a or 24) an overflow region (33; 33x) is formed. Compact plate heat exchanger according to one of claims 6 to 13, characterized in that in the housing (1) one or more stacked and separated by a partition wall (38; 38a - 38x) stack of packages (40,40a - 40x) are used and each stack of packages (40 , 40a - 40x) consists of plate packages (2, 2a-2x) staggered uniformly in the horizontal plane, which are separated from one another by separating plates (39; 39a-39x), the plate interspaces (11) of the staggered plate packets (2-2x ) of a package stack (40-40x) and the plate interspaces (11) of the staggered plate packs (2-2x) of a plate stack (40-40x) each jointly from the first medium in the same flow direction directly from the housing (1) gas-tight welded distributor (34) and collector (36) and via assigned connecting pieces (35; 35a; 35b; 35x), which are each gas-tightly welded at the circumference of the passage opening (8,9) of the heat transfer plate (3) of the adjacent plate pack (2; 2x), are flowed through on the shell side and that the second medium in a flow direction Plate interstices (10) of all in the housing (1) clamped together plate packs (2-2x) flows through the front side. Compact plate heat exchanger according to claim 14, characterized in that the plate interspaces (11) of the respectively uniformly offset plate packs (2-2x) of a plate stack (40-40x) are flowed through separately assigned inlet and outlet nozzles (12, 14) which are arranged on the circumference ( 27, 28) of the passage opening (8; 9) of the heat transfer plate (3;) of the offset adjacent plate pack (2; 2x) and in the penetration region (25; 25a) of the housing (1) are gas-tight welded. Compact plate heat exchanger according to one of claims 6 to 15, characterized in that between each partition wall (38-38x) and the longitudinal sides of the respective adjacent plate pack (2-2x) or package stack (40-40x) a filling material (29; 29a) is inserted and the filling material (29; 29a) is sealed by means of a deflector (30; 30x).

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