EP2846121B1 - High pressure plate heat exchanger - Google Patents

Description

The invention relates to a high pressure plate heat exchanger. This has a plate pack, which has media flowed through first and second channels, which are arranged in cross-flow, or in the case of multi-path in the cross-countercurrent. In this case, the first channel provided for the first medium are formed in a tubular manner between individual plates connected to a pair of plates and the second channel provided for the second medium in a wave form between pairs of plates connected to a plate stack.
A plate pack of the type described above is from DE 43 43 399 A1 known. Here, a plate heat exchanger with flowed through in cross-flow channels is disclosed, which are formed for the one medium wave-shaped between each connected to a plate pair of individual plates and the other medium tubular between the assembled into a plate stack plate pairs. The individual plates for channel formation are equipped with a plurality of parallel rows of aligned in the flow direction of a medium cam or embossed support structures, which are formed offset from each other in the longitudinal direction from row to row.
A plate heat exchanger from the DE 43 43 399 A1 previously known type has proven itself in everyday practice. However, for the high-pressure application, ie for media pressures of greater than 25 bar, the previously known constructions are not suitable. This particular not because the prior art plate heat exchanger for higher pressures do not have sufficient mechanical stability and deform at higher pressures beyond the allowable level.

US3610330 A and WO2010149858 A1 disclose high pressure plate heat exchangers each having a plate pack disposed in a pressure space provided by a housing. It is therefore the object of the invention to propose a plate heat exchanger suitable for high pressure applications.
To solve this problem, the invention proposes a high-pressure plate heat exchanger with a rectangular plate pack, which is arranged in a pressure chamber provided by a housing, wherein the plate pack of media through-flowable first and second channels, which are arranged in cross-flow and tubular for the first medium between formed into a pair of plates interconnected individual plates and the second medium undulating between interconnected to a plate stack plate pairs, said tubular channels formed in the longitudinal direction parallel to the longitudinal edges of the individual plates and the individual plates along their longitudinal edges together to plate pairs and the plate pairs along their transverse to the longitudinal edges of the individual plates extending edges are joined together to form a plate stack, wherein the tube side for the first medium and the shaft side as a pressure side for the second Serve medium and the housing has tube side of the plate stack subsequent flange cover, which are at least partially spherical and have a correspondence of the geometric configuration of the plate package rectangular opening for receiving the plate pack, the individual plates provided with several parallel rows of extending in the longitudinal direction embossing sections are, wherein the embossing portions of adjacent rows are offset in the longitudinal direction to each other. For reasons of optimized efficiency, that is to say of optimized heat transfer, the second medium under pressure is to be guided on the shaft side of the plate pack. The tube side of the plate package carries the first, under reduced pressure medium. In the from the DE 43 43 399 A1 Prior plate heat exchangers, the tube-side forming tubular channels extending transversely to the longitudinal direction of the plate package forming individual plates. In this case, production reasons, the transverse extent of a single plate is limited by the width of the embossing tool, whereas a quasi-endless, that is arbitrarily selectable extent in the longitudinal direction is possible.
It has been found in practice that the tube side of prior art plate heat exchangers can be achieved in high pressure applications with a view to a desirable manner Heat transfer is too short. It has therefore been proposed to connect a plurality of known plate heat exchangers on the tube side one behind the other so as to be able to provide the required distance on the tube side. Such fluidic interconnection of individual plate heat exchanger makes the use of appropriate connections, connecting pipes, hoses, deflections and / or the like required, which disadvantageously on the pipe side to a part can cause significant pressure loss. As a consequence, the heat exchanger efficiency disadvantageously decreases, but this can not be avoided in the case of previously known constructions.

The embodiment of the invention provides a remedy. In contrast to the previously known construction, a plate stamping rotated by 90 degrees is proposed so that the tube side, i. the tubes run in the longitudinal direction of the plate. Thus, the channels formed for the first medium in a tubular manner between individual plate plates connected to one another are formed parallel to the longitudinal edges of the individual plates. This results in the result that it is possible to dispense with the fluidic series connection of a plurality of plate heat exchangers, since an embodiment of the individual plates in the desired length can take place with the result of adapted for the high pressure application case dimensioning of the tube-side flow channels. Thus, the embodiment of the invention is particularly suitable for high pressure applications, without the risk of pressure drops due to pressure drop on the pipe side. It can also remain the pressure retaining plates or the package side walls, as a design has to be made only to the lower pressure of the pipe side.

Plate heat exchangers, unlike, for example, tube bundle heat exchangers, are comparatively unstable to pressure. In particular, in the case of an only edge-side connection of the individual plates, if the pressure is applied too high, bulging of the individual plates and / or tearing of connection points existing between the individual plates may occur. To avoid this, it is proposed with the embodiment according to the invention to arrange the plate package formed from individual plates within a pressure chamber, which is provided by a housing. The plate pack is surrounded in the intended use of a pressure prevailing in the pressure chamber support pressure, which acts as a back pressure on the plate package. The construction according to the invention proves to be advantageous in this respect in that pressure retaining plates or package side walls are to be designed only with reference to the comparatively low pressure of the tube side, ie the first medium, which means that they are used unchanged in their design compared to the prior art can be, and this at the same time suitability for a high-pressure application in the context of the invention. This leads advantageously to the fact that even at comparatively high pressures of up to 100 bar and more comparatively thin-walled individual plates can be used, for example, have a plate thickness of 1.2 mm to 2.0 mm, preferably from 1.3 mm to 1.8 mm, more preferably of 1.5 mm.

The housing which provides the pressure chamber is preferably spherical in shape and / or circular with respect to at least one cross section for receiving the pressures prevailing in the operating case, deviating from the rectangular shape of the plate package. On the one hand to provide a standstill in the case of operation the prevailing pressures housing, on the other hand allows the media supply to a parallelepiped plate pack, is further provided with the invention constructive that the housing has tube side of the plate package subsequent flange cover, which are at least partially spherical. This ensures structurally that in the transitional, that is, bonding area in the plate stack housing side voltage peaks are avoided, so that with sufficient safety margin comparatively high pressures can be absorbed, while minimizing the required housing wall thicknesses and plate thicknesses. With the construction according to the invention, therefore, there is proposed a housing providing a pressure space which projects the outside of the shaft, i. to the surrounding atmosphere through a cylindrical shell and the tube side by a spherical sheath separates, which are avoided as a result housing side voltage peaks in the transition region from the shaft side to the tube side.

The inventive design makes it possible for the first time to use plate heat exchanger in the high pressure area, namely at working pressures in terms of the second medium of about 50 bar, preferably from about 60 bar, even more preferably from about 100 bar, up to 120 bar. Previous designs do not allow such printing applications. The working area of previously known constructions ends rather at a pressure of about 20 bar, possibly of about 30 bar. Pressures of over 30 bar, let alone 60 bar and more are not possible with the previously known embodiments. Surprisingly, the pressure range of more than 120 bar possible with the embodiment according to the invention is surprising, without restriction by differential pressures, since the thickness of the exchanger plates used on the one hand and the housing wall thickness on the other hand are comparatively thin. In this respect, the wide pressure application range of the high-pressure plate heat exchanger according to the invention results as Synergy effect from the explained individual features.

According to a further feature of the invention, connecting wedges are arranged in the corner regions of the plate stack between two adjacent plate pairs. These connection wedges are preferably connected to the adjacent pairs of plates by positive engagement by welding. The connecting wedges serve two purposes. On the one hand, a stabilization of the entire plate package construction is achieved. On the other hand, the connecting wedges are used for fluidic separation of the shaft and tube sides.

To form the individual flow channels, the individual plates provide embossing sections as known per se from the prior art. In this case, the individual plates are provided with a plurality of parallel rows of longitudinally extending embossing sections, and embossing sections of adjacent rows are aligned with one another in the longitudinal direction. In contrast to the prior art, it is provided according to the invention to design a tighter embossed embossed image. This, in contrast to the prior art tighter imprint image leads to an improved support of the individual plates with each other and thus to a reinforcement of the entire plate package, which proves to be particularly in the case of high pressure application.

Figur 1

in einer Seitenansicht einen Hochdruckplattenwärmetauscher nach der Erfindung;

Figur 2

in einer Schnittdarstellung den Hochdruckplattenwärmetauscher nach Figur 1 gemäß Schnittlinie II-II;

Figur 3

in schematisch perspektivischer Darstellung ein Plattenpaket;

Figur 4

in einer perspektivischen Ausschnittsdarstellung den Ausschnitt IV nach Figur 3;

Figur 5

in einer perspektivischen Ausschnittsdarstellung den Ausschnitt V nach Figur 3 und

Figur 6

in einer Seitenansicht das Plattenpaket nach Figur 3.

Further features and advantages of the invention will become apparent from the following description with reference to FIGS. Show

FIG. 1

in a side view of a high-pressure plate heat exchanger according to the invention;

FIG. 2

in a sectional view of the high-pressure plate heat exchanger FIG. 1 according to section line II-II;

FIG. 3

in a schematic perspective view of a plate package;

FIG. 4

in a perspective sectional view of the section IV after FIG. 3 ;

FIG. 5

in a perspective sectional view of the detail V after FIG. 3 and

FIG. 6

in a side view the plate package after FIG. 3 ,

FIG. 1 can be seen in a side view of a high-pressure plate heat exchanger 1 according to the invention. This has a housing 2, which - as the sectional view FIG. 2 recognize - provides a pressure chamber 3. Within the pressure chamber 3, a plate pack 4 is arranged, which for the sake of clarity in FIG. 2 is shown only schematically.

The FIGS. 3 to 6 let the plate package 4 partially detect. As can be seen from these illustrations, the plate pack 4 is formed from individual plates 14. In this case, two individual plates 14 together form a plate pair 15 and a plurality of plate pairs 15 coupled to one another constitute a plate stack 16.

Like the exemplary presentation after FIG. 4 can discern, the plate package 4 shown here consists of a plate stack 16, which has four pairs of plates 15 which are arranged between two serving as cover plates individual plates 14. The individual plates 14 are each formed identically and connected in mirror image to each other to a pair of plates 15. This connection preferably takes place cohesively by welding, along the longitudinal edges 17. In this case, first tubular channels K1 are formed between the individual plates 14 forming a plate pair 15, specifically for the medium M1 participating in the heat exchange in the intended use. By joining the plate pairs 15 to a plate stack 16 along the transverse edges 18 arise between the adjacent individual plates 14 adjacent plate pairs 15 wave-shaped channels K2 for the other heat exchange participating medium M2, which is guided in cross-flow to the medium M1. The second medium M2 is the pressurized high pressure medium.

As it turns out FIG. 3 results, each individual plate 14 with a plurality of parallel rows of extending in the direction of the longitudinal edges 17 embossing sections 21st Mistake. These embossing sections 21 of adjacent rows are offset from one another in the longitudinal direction, whereby surface supports between adjacent individual plates 14 result in a row between successive embossing sections 21.

In the corner regions 19 of a plate package 4 15 connecting wedges 20 are arranged between the individual plates 14 adjacent plate pairs. On the one hand, these connecting wedges 20 separate the shaft side from the tube side in the inlet and outlet region of the media M1 and M2 and, on the other hand, serve to stabilize the overall plate package 4 as a whole.

As FIG. 2 can be removed, the housing 2 is formed from a ring portion 7 and two flange 8 and 9. In this case, the flange cover 8 and 9 each provide an opening 10 for the tube side, which are formed in correspondence with the geometric configuration of the plate package 4 and serve to receive the plate package 4. In this case, the flange cover are at least partially spherical, preferably in the manner of a dished bottom, with which the housing 2 connects to the plate stack 4 on the shaft side in a spherical configuration.

The respective flange cover 8 and 9 are equipped with a flange 11, which in turn carries a respective flange plate 12 connected thereto by means of screws 13. The flange plates 12 are equipped with connecting pieces 5 for the first medium, that is to say the low-pressure medium. On the shaft side, the plate package 4 via connection piece 6 in fluid communication with the second medium, that is, the high-pressure medium.

In the intended use case, the pressurized second medium M2 corresponding to the in FIG. 2 drawn arrows on the shaft side introduced into the plate pack 4 and leaves after a flow through the plate pack 4, the high-pressure plate heat exchanger 1 again via the provided connecting piece 6. In the course of the intended use, the introduced fluid flows into the pressure chamber 3 provided by the housing 2, so that on the plate package 4 acts an internal pressure identical external pressure, whereby the plate pack 4 and the individual plates 14 of the plate pack 4 are set completely depressurized, or at one-sided loading with the first medium M1 of the low pressure side only be loaded with the lower pressure of the first medium M1.

In cross-flow to the second medium, the medium flows at lower pressure, that is, the first medium, in accordance with the arrows FIG. 2 across the tube side of the plate pack 4. Both tube and shaft sides can be operated in a multipath manner. In this case, deflections between the plate pack 4 and housing are provided on the tube side or provided on the shaft side deflections in the plate pack 4 and between plate pack 4 and housing. Due to the multi-way circuit operation in cross-countercurrent is possible.

As well as the representation after FIG. 6 can be removed, the tube-side channels K1 are determined in their geometric dimensions, inter alia, by the distance of the mutually offset in adjacent rows embossed sections 21. This distance A is in FIG. 6 drawn by way of example.

reference numeral

1

High pressure plate heat exchanger

2

casing

3

pressure chamber

4

plate pack

5

spigot

6

spigot

7

ring section

8th

flange

9

flange

10

opening

11

flange

12

flange

13

screw

14

Single plate

15

pair of plates

16

plate stack

17

longitudinal edge

18

cross-border

19

corner

20

connecting wedge

21

embossed section

A

distance

M1

first medium

M2

second medium

K1

first channel

K2

second channel

Claims (6)

1. A high pressure plate heat exchanger comprising a rectangular plate packet (4) which is arranged in a pressure room (3) provided by a housing (2), wherein the plate packet (4) comprises first and second channels (K1, K2) through which media (M1, M2) can flow, which channels are arranged in countercurrent and are formed for the first medium (M1) as tubes between individual plates (14) that are connected to form a pair of plates (15) and for the second medium (M2) in form of waves between pairs of plates (15) that are connected to each other to form a plate stack (16), wherein the tubular channels (K1) extend in the longitudinal direction in parallel to the longitudinal edges (17) of the individual plates (14) and the individual plates (14) are connected to each other along the longitudinal edges thereof to form pairs of plates (15) and the pairs of plates (15) are connected to each other along their edges (18) extending transversely with respect to the longitudinal edges (17) of the individual plates (14) to form a plate stack (16), wherein the tube side serves as pressure side for the first medium (M1) and the wave side serves as pressure side for the second medium (M2) and the housing (2) comprises flange covers (8, 9) which are connected on the tube side of the plate stack (16) and which are at least partially spherical and comprise a rectangular opening that is shaped correspondingly to the geometric design of the plate packet (4) for receiving the plate packet (4), wherein the individual plates (14) are provided with several parallel rows of embossment sections (21) which extend in the longitudinal direction, wherein the embossment sections (21) of adjacent rows are offset with respect to each other in the longitudinal direction.
2. A heat exchanger according to claim 1, characterized in that the flange covers (8, 9) are respectively designed as torospherical heads.
3. A heat exchanger according to claim 1 or 2, characterized in that connection wedges (20) are arranged between two adjacent pairs of plates (15) in the corner area (19) of the plate stack (16).
4. A heat exchanger according to one of the preceding claims, characterized in that the individual plates (14) comprise a plate thickness comprised between 1.2 mm and 2.0 mm, preferably between 1.3 mm and 1.8 mm, more preferably of 1.5 mm.
5. A heat exchanger according to one of the preceding claims, characterized in that the plate packet (4) which is arranged inside the housing (2) is surrounded by a support pressure.
6. A heat exchanger according to one of the preceding claims, characterized in that on the wave side the plate packet (4) is open towards the pressure room (3) provided by the housing (2).

Images