DE1908800A1 - Plate capacitor - Google Patents

Description

Dipl.-Ing. Heinz U »« r. Patent attorney D - 8 MOnaSan 81, Coiimostrafc 81 Telephone: (0811) 48 38 20

HISAKA WORKS Ltd.

150, Konoike, Higashiosaka-shi, Osaka / Japan L 8606 Gg / h «

Plate capacitor

The invention relates to a plate capacitor and is particularly concerned with one that has a A multitude of narrow channels for cooling liquid and vapor are provided, which pass through a multitude of vertical, with a mutual parallel spacing of arranged heat transfer plates are formed, and which further with a device is provided, which seals the individual plates. In the context of the present invention, the efficiency Such condensers can be improved in terms of heat exchange and in terms of condensation of the steam.

A condensation of vapor in which its liquefaction is carried out, is often carried out in a wide variety of industrial operations, especially in the chemical industry. The condensation of steam will occur usually carried out using heat exchangers. Among the various types of such heat exchangers there are also tube, coil and lamellar heat exchangers or coolers. Pur the mutual heat exchange For liquids of different temperatures, the plate condenser is usually preferred to the tube cooler, because he is a bigger one with regard to the transfer of confusion Has coefficients and because it fulfills a significantly improved heat exchange function. The conventional plate capacitors However, they still have numerous disadvantages

au 9804/1109

Dipl-ing. Heinz Lesser. Patent attorney D - '8 Munich 81. Cosimastroße 81 Telephone: (08Π) 48 38 20

can be described in more detail, they often work inadequately in the company and are therefore unable to do what they are supposed to do Requirements to meet.

In conventional plate capacitors, a multitude of thin, heat-transferring plates are arranged vertically with a mutual parallel spacing, which form narrow channels under each other through which alternately steam and cooling liquid are passed, so that a heat exchange takes place between two separate channels Causes condensation of the steam. Such condensation system performs, but by the concentration of the vapor to form a precipitate (Tripfchenbildunp) of the steam _o at the surface of the vertical, thin-walled metal sheets v progresses condensation / axes concentrated droplets, so it that finally due to its own weight along the surface the plates fall off. Such falling droplets are distributed over the entire width of the plates and form thin layers of liquid that cover the entire surface of the plate. It can readily be seen that the thickness of such liquid layers increases in the vertical direction downwards. Because of the presence of such thin liquid layers, which cover the surface of the thin plates, the plates are thereby isolated from direct contact with the vapor, which results in a reduced heat exchange, ie, in this way covered upper covered plate surfaces reduce the efficiency of such Disk konder? = sators.

The condensation of steam by cooling along the plates

is divided into three stages , namely a coating: -? .-

stage, a waste stage and a stage in which both

909884/1109 '"

Dipl. 'Ng. Heinz L »n« r, patent attorney D - 8 MOnaSan 81, Cofimastraft · 81 Telfon: (0611) 48 38 20

the coating as well as the waste exist. The efficiency of the heat exchange, i.e. the efficiency of the condensation, now depends on which of the three above-mentioned Stages or states exist. For example, the vapor can be condensed over the surface of a metal plate in the form of a successive layer of liquid if the surface is kept clean, but it is condensed in the form of mutually isolated drops of liquid when the surface is covered with a water-repellent layer. The value of the coefficient of heat transfer is im the latter case many times greater than in the former case. So far, however, there have been no known proposals for such plate capacitors in which only a tiny condensation takes place.

The conventional plate capacitors also have the following disadvantage. Regarding their mechanical Embodiment is to be determined for such capacitors, that the effective width of the steam channels near a steam inlet is half as great as that of the channel near the middle area of the plate. In the direction of flow of the There are therefore different flow velocities of the steam, which results in a pressure loss or drop, which has a detrimental effect on heat transfer. Furthermore, the ratio of such plate capacitors is the effective heat transfer area in relation to the total area of the panels is very small, i.e. the surface of the panels is facing Sub-areas that do not contribute to heat transfer. The conventional capacitors also grow up Difficulty in supplying the steam, which must be supplied in an amount sufficient to render it the maximum Corresponds to the amount of steam that can be condensed by the effective heat transfer area.

909884/1109

Dipl.-Ing. Η · ϊηζ lesser. Patent attorney D - 8 Mündien 81. Codmastrafc · 81 ·. Telephone: (0811) 48 38 20

In the arrangement of the multitude of channels, the conventional plate capacitor seals use. It it cannot be prevented that such seals come into contact with the supplied steam, which then destroys these seals, in particular when if he has organic solvents with him. It is Pay particular attention to the fact that such seals are directly exposed to the high-temperature and high steam Pressure accelerates the destruction of such seals.

Taking into account the above, the The invention is based on the object of creating a plate capacitor of the type mentioned, which has a high degree of efficiency in terms of heat transfer and in terms of its ability to condense steam, the area which is occupied by the condensed liquid layer should be reduced as much as possible. According to one Part of the feature of the invention is that this is achieved in that a vortex flow is generated, and in that the amount of steam supplied is increased with a simultaneous, effective one Reduction of the pressure loss. In the context of the invention a more effective seal for such plate capacitors suggested the seAbst strongest pressures in the Resists operation of such capacitors.

With a plate capacitor according to the invention with a A plurality of narrow channels for the cooling liquid and the vapor, which are formed by a plurality of vertical, mutually parallel spaced apart heat transfer plates, and with means for sealing them A device for collecting the droplets is now provided for plates. This collection facility includes the inside the condensed liquid agitation plate arranged by the vapor channel formed by the heat transfer plates, and eftien channel for this condensed liquid, which is in series

909884/1109

Dipl.-Ing. Heinz Lesser. Patent attorney D- 8 Munich 81, Gwimortrafee 81 ■ Telephone: (0811) 48 38 20

is arranged with the guide plate. The guide plate is aligned obliquely downwards within the channel and in the vicinity of such a collecting device there is at least one steam inlet and at least one outlet for the from Steam condensed liquid is provided.

Further features and advantages of the invention are disclosed in US Pat the following description of preferred embodiments recognizable. It shows:

Figures 1 A and

Figure 2

Figure 3 A

Figure 3

Front views of a heat exchange plate according to two inventive Embodiments,

a perspective view for illustration the channels for the condensate from the steam ized liquid and for the cooling water, each formed between adjacent heat transfer plates,

in perspective view of part of a collecting device according to the invention heat transfer plate provided for droplets for illustration the condensation process of the steam,

a perspective view corresponding to FIG. 3A for the modification of the condensation process of steam in the case of a plate which is not provided with a hem device according to the invention,

0988A / 1109

Dipi.-Ing. Heinz - Figure 6 Utscf. Patent attorney D - 8 Mümfi.n 81. Coiimodrafc · 81 Phone: (0811) 48 38 X
- fi - characters 4 A and 4 B - ο -
Front views of heat transfer - plates for the formation of steam channels Figure 6 or cooling water channels according to a white further execution unpjs form, characters Figure 6 5 A and 5 B Front views of further embodiments men of heat transfer plates according to the invention, Figure 6 A. a front view of another Aus management form of a heat transfer plate te according to the invention leading to education a steam channel is determined, Figure 6 characters
* B. a section along the line 6B -6 B of the Figure 6 A, C. . i -
A front view of another embodiment shape of a heat transfer plate for the formation of cooling water channels, D / a section along the line ÖD - 6D of the Figure 6 C, E- in perspective view and enlarged Scale a part of an invention measure heat transfer plate to Ves? - visualization of the effect of the appropriate collecting device that Flow of condensed liquid showing 7A- 7D on an enlarged scale vertical section «

909884/1109

Dipl.-Inq. Hw'nx Im · «, pot attorney D - 8 Munich 81, Coiimortrofe 81 Telephone: (0611) 48 38 20
-.7 - different embodiments of the
collective device according to the invention, Figures 8 A - ⁿ . D. Front views of further execution
forming a heat transfer plate
according to the invention for the formation of
Steam channels, Figure 9 a perspective corresponding to FIG
tive view to illustrate a
another system of heat transfer
panels according to the invention, Figure 9 A on a larger scale a partial transverse
SQhnitt the in the system according to Figure 9
Used collecting device
according to the invention, Figure 9 B in an improved scale a part-vor
the view of the collection device
Figure 9 A ₁ Figure 10 A a plan view, in section, of the
lined up heat transfer
plates according to the invention for Veran
Visualization of the facility for Abdich
ten of those formed by these plates
Channels, Figure 10 B a detail on a larger scale
the sealing device according to Figure 10A

909884/1109

- - 1908800 Dipl.-Ing. Heinz Head. Patent attorney D - 8 MOndia 81. Cotimatfrafce 81 Telephone: (0611) 48 38 20
O Figure 10 C - η -.
a Dar corresponding to FIG. 10B Figure 12 A position to illustrate a - alternative embodiment of you management facility, Figure 11 one-corresponds to Figures 10 B and 10 C Figure 12 B rotating representation for illustration a further, alternative design shape of the sealing device, on a larger scale and horizontally cut the edge of a heat transfer " Figures 13 A-13 C plate according to another design " form of invention, one of FIGS. 10 B, 10 C and 11 ent Talking representation for visualization the direction of the gasket is included Plates with an edge according to the Dar position according to Figure 12 A, Figures 11 »A and 1 * B FIG 12 B corresponding Imaging Logo • gen illustrating the sealing installation for plate capacitors conventional embodiment for the same tentative illustration of the form exercise the edge of the usual heat transfer support plates, and Front views of heat transfer conventional plates AUEF of embodiment.
-

90988 /; / 1109

Dipl.-Ing. Heinz UsMf, Potentanwalt D - 8 MOndten81, Coiimatirafc 81 - Telephone: (0811) 48 38 20

In Figures 1 A and 1 B are zwd. Types of heat exchange plates shown which are used in the context of the present invention. The heat transfer plate shown in Figure 1 A is provided with a surface 1 a, which forms a steam channel, the plate shown in Figure 1 B is provided with a surface 1 b to form a cooling water channel. A vapor inlet 2 is formed near the upper edge of the heat transfer plate 1, while an outlet 3 for condensed liquid is formed near the lower end of this plate. The width or length of the inlet 2 corresponds almost to the effective width of the plate i, while the width or length of the outlet 3 is smaller than this effective plate width. The vapor is fed in via inlet 2, it is then passed downwards over surface 1 a, where it is simultaneously cooled and condenses on surface 1 a, the condensed liquid is discharged via outlet 3. The inventive collection means for collecting the condensate droplets, so the precipitate to the plate surface comprises a plurality of guide plates or parts ¹ Ia, and a plurality of channels ¹ J BYou the condensed liquid. The guide parts 4 a are arranged within the effective heat exchange surface of the surface 1 a of the plate 1. As can be seen in particular from Figure 3 A, the guide parts ^ 4 a are directed obliquely downwards, depending on the OrSsse of the effective heat transfer surface on the surface 1 a, these guide parts k a are arranged both in a row and in a plurality of such rows can. In each row, the lower end of all guide parts lies on a straight line common to all lower ends, so that a condensed liquid falling down from such a lower end of a guide part does not drop in one row through a possible contact with a guide part of another row is splashed.

909884/110 9

19088QO

Dipl.-Ing. Ή «ηι Leuer. Patehtonwolt D - 8 Munich 81. CMimwtroft 81 Telephone: (0611) 48 38 20

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As can be seen from FIG. 1, a sealing ring 5a is placed on the peripheral edge of the plate and fastened to the plate, the surface 1a, i.e. the effective heat transfer surface of the plate, is thus surrounded by this sealing ring 5a. ¹ Both the steam inlet 2 and the outlet 3 for the condensed liquid are located within this effective heat transfer surface, while the channel 6 b for the cooling water is located outside, i.e. also outside the sealing ring 5 a. The cooling water channel 6 b is sealed by a sealing washer 5 b, which surrounds the channel and is also attached to the surface of the plate 1,

As already stated, the one shown in Figure 1B is used Heat transfer plate for the formation of cooling water channels, 'also here is the steam inlet 2 b and the Aualass 3 b for condensed Liquid through sealing washers 5 c or 5 d against sealed the cooling water channel. The one through the sealing washer 5 e covered area forms the effective heat transfer area * The cooling water is fed into its channel via an inlet 6, then flows in the direction of arrows 9a, 9b and 9c and flows through the channel 6 b from that in the adjacent heat exchange plate 1 is formed. The transverse wall 8 forms the the aforementioned flow channel for the cooling water.

FIG. 2 shows the relative arrangement of the heat transfer plates shown in FIG. If the plates are lined up to form the plate capacitor, then the plates with the surface la are arranged alternately to the places with the surface 1b, namely parallel and at a distance from one another, in such a way that one of these surfaces is against the rear face of the other surface is aligned. As a result, the Dampfelnlaflskanäle 2 and Z b or the channels 3 and 3 b for the condensed liquid

^{~:; :} ; τ η ■■■ - -n η mi | i ι mim mi ι ι _ iiiib ι ι ι.ι'ΊΤΤΠ

909884/1109. * - ■ ■

Dipl.-Inj Heinz letMf. Patent attorney D - 8 Mönchen 81, Cotimastraft 81 Telephone: (0611) 48 38 20

- 11 -

connected to one another in the manner shown in the drawing. In this context? it should be noted in particular that the position of the inlet channels 6 for the cooling water and the channels 6 b are alternately different in the case of plates corresponding to one another. If you number the individual plates from left to right with the numbers 1 to ¹ I, the cooling water channels are formed between plates 1 and 2 and the nth plates 3 and ¹ J, while a steam channel is formed between plates 2 and 3. The mode of operation of such a flat capacitor will now be briefly described.

As already mentioned, the steam to be condensed is fed to the system via the inlet opening 2 of the plate number 1, in the direction of the arrow 7 a. At the same time, cooling water is fed to the system via channel 6 of plate number U , as illustrated by arrow 7b. The supplied steam is introduced into the steam channel formed between plates number 2 and number 3, it flows in the direction of arrow 7a through steam inlet channels 2 and 2b of plates number 1 and number 2. The incoming cooling liquid is in the cooling water channel between the plates Number 3 and number Ί introduced, it flows through this in the direction of arrows 9 a, 9 b and 9 c because of the intended transverse wall 8 and is finally diverted via channel 6 b of plate number 3, then flows through channel 6 of plate number 2 and flows through the cooling water channel formed between the plates number 1 and number 2 in the direction of arrows 9 a, 9 b and 9 c, which is also caused here by the transverse wall 8. Finally, this flow of cooling water is diverted through channel 6b of plate number 1.

During the above-described flow of the steam and the cooling water, heat transfer between the steam and the Cooling water made, through the plates number 2 and

90988 4/1109

Dipl.-Ing. Hainz Lexer, patent attorney 0-8 MOndSen 81, CoiinKJstrafce 81 · Telephone: (0811) 483820

- 12 -

Number 3, in which process the steam is cooled and condensed on the surfaces of plates number 2 and number 3 that define the steam channel. . .. _;

The condensation process is now shown in FIGS. 3A and 3B of the steam shown schematically. The cooled steam is deposited on the surface 1 a in the form of dew drops 10 a. In the first stage of a small condensation are such dew droplets 10 a over essentially the entire " Width of the surface i a downcast. As the condensation progresses, the droplets 10 a grow in size and flow due to their own weight over the surface 1 a downward. This downward flow of the upper drops 10 a creates a merging of the upper and lower drops, so that gradually through these growing drops a more or less egg closed liquid 10 b is created, which then strikes a guide part ^ a with increased · flow velocity By now the guide part 4 a aligned obliquely downwards 1st, the condensed liquid it collects first obliquely directed downwards, and it reaches the lower end edge of the guide part, then it is in the guide channels y b flow vertically downwards, as illustrated in the drawing with arrows. Because now the lower If the ends of the guide parts lie on a common straight line with respect to one another, the liquid flowing downwards will be

not impaired by guide parts of the adjacent row, the condensed liquid can therefore be directed to the outlet channel 3.

In the above-described process of liquefying the vapor, three types of thin liquid layers are now formed. The first liquid layer 10 b is formed in the vicinity of the upper surface of the guide part H a on the surface 1 a,

90988Λ / 110 9

Dipl.-Ing. HMnz Ussfer, patent attorney D - 8 Munich 81, Coiimastrofe 81 Taltfon: (0611) 48 38 20

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the second liquid layer 10 c is on the upper surface of the guide part 4 a and the third, thick liquid layer 10 d is formed along the channel k b for the condensed liquid on the surface 1 a! It should be noted, however, that part of this liquid falls from the lower end of the guide parts * without coming into contact with the surface 1 a j this will have an influence on the heat transfer and the condensation process * which - however, in the context of the present invention is reduced to a minimum, as will be evident from the further description in connection with FIG. 3B. It is also to be noted that the area of the liquid layer 10 d in relation to the total effective. Heat exchange from the surface is so minimally small that the formation of this liquid layer 10d plays practically no role at all, so that the efficiency of the heat transfer is not impaired as a result; In contrast to this, with regard to plates which are not provided with such guide parts according to the invention, reference is made to FIG. 3B! that a liquid layer 10 e is formed over almost the entire width of the surface 1 a of the plate 1, which gradually increases in thickness towards the lower edge of the plate. In contrast to the aforementioned liquid layer 10d, which can be expected within the scope of the present invention, the ratio between the area occupied by the liquid layer 10e and the total effective heat transfer area is extremely large.

Further embodiments of heat transfer plates according to the invention are now shown in FIGS. K A and 4 B. It should be noted that the Dampfeihlasskanäie 2 and 2b and the outlet channels 3 and 3b for condensed liquid essentially

90 98 8 4/1109

19088Ö0

Dipl.-Ing. H «hi uuer. PoUntanwdll D - 8 Mond> e «81. Co» imo »traij · 81 · Telephone: (0811) 48 38 20

- in -

They correspond to the corresponding channels of the design forms IA and i B. The plate 1 with surface i b is provided with two cooling water inlet channels 46 ah at the lower corners and with two triangular cooling water outlet channels 46 c at the upper corners, while the plate ί with upper surface la with four cooling water channels 46 b and 46 d in the four Corners is provided. Oils shown embodiments differ from the above-described embodiments in the Änörd ~ hung a transverse wall HH of the plate i with surface ί b, the illustration shows that this transverse wall Mti extends between the seals 5c and 5d, so that two separate KÜhlwasserkahäie educated; will. The inflowing cooling water thus forms two separate flows which, in FIG. 4 B with the! Strömuhgspfellen are indicated kl * The arrangement of the -S "ührüngs partly # Ii. Ä for kondönsierte liquid on the plate 1 with ΘΒ§ρ · ä fiäche 1 is shown in Figure U A j is Met · virtually one by one with the embodiment. Figure 1 A idihtische Ähördnung made »with the exception / that in the two middle rows the two lower guide parts to the two above them arranged guide parts are arranged in a mirror image: * The same applies to the two upper guide parts in both rows. Dig so modified Änordriühi des wasserkartäls gives the vote> that a pump for supplying the cooling liquid under a reduced bast arbiit combined with the advantage that the flow resistance of the cooling water can be increased and thus the efficiency of the heat transfer can be improved »

In Figures 6 A to 6 D and 7 A to? Further embodiments according to the invention are shown schematically or less schematically. In the embodiment according to FIGS. 6 A and 6 B, the guide parts 4 a are for condensed liquid according to the above-described form through a plurality of guide recesses 6 k a ers the guide channels Ib for condensed liquid of the above

909884/1109 '

Dipl.-lnq Heinz [do. Patent Attorney D - 8 Munich 81, Cotimastrofte 81 - Telephone: (0811) 48 38 20

- 15 -

The described embodiments are replaced by recesses 6 * 4 b. The recesses 6 ^ a and 64 b are formed on the surface 1 a of the plate 1. As the illustration shows, the recesses 6 * 4 b are formed near the two side edges of the plate 4, the recesses 64 a extend upwards to a central area of the surface 1 a. In contrast, in the embodiment according to FIGS. 6 C and 6 D, the recess 64 b is formed in the central area of the .Oberfläche 1a and the recesses 64 a extend upwards to 1s, both. Rare areas of the surface 1 a. The recesses> 4 a and 64 b mentioned are refornit at the same time in the surface 1 a of the plate 1 by means of a conventional pressing process. If one arranges the plates .genräss Firur 6 A and c; emiiss 6 C alternately, then this means that ^r -the viscera removal unp; s successively in Bezue running crosswise, this arrangement is shown schematically in cross Flrur 7 A shown and from this illustration it can be seen that the recesses 6 ^ a of adjacent plates protrude into the KUhlwasserkanal and weehi5f'lse111 r; touch. In this context it can be noted that adjacent plates are also arranged in such a way that their recesses, or more precisely, the raised '.-.' In '. * »Ie of these recesses are not mutually exclusive touch.

In the Pleurer. 7 A Ms 7 D are, for example, only shown cross-sectional shapes of the recesses. Among the depicted The shape of the recess 64 is similar to Fic; ur 7 C assigned a guide part 67, which is located below the recess 64 a and extends along this. The hallway 7 D embodies a modified version. By such Recesses in the surface of one of the heat exchange plates are provided, thereby the effective heat transfer surface and there are in the steam and in the cooling water currents Eddies are generated, which increase the heat

909884/1109 ..., _{BAD 0RIQ1NAL}

j Oipl.-Ιης. H «M Imw, Patentanwalt D - 8 MOnehen 81. Coiimorfrofce 81 ■ Telephone -: '(QBII) 48-38 20

- 16 -

result in transfer. It should be noted that the cross-sectional profile the recesses mentioned here do not appear the illustrated embodiments is to be limited.

The collecting device proposed within the scope of the present invention can also be provided in the form of an intermediate plate which is provided with a plurality of guide ribs for condensed liquid on its surfaces and which is clamped between two heat transfer plates. Such an embodiment is shown in FIGS. 9, 9 A and 9 B, in which the mentioned intermediate plate is denoted by 91. This intermediate plate is arranged between two heat transfer plates with surfaces 1 a and 1 b and a plurality of guide ribs for condensed liquid are arranged on its two surfaces. In FIG. 9A, the vapor flow channel is denoted by V and the channel for the cooling liquid is denoted by W. 92 denotes a steam inlet opening, 93 an outlet opening for condensed liquid., 96 A the cooling water inlet channel and 96 b the cooling water outlet channel. These channels correspond in their function to the corresponding channels in the embodiments according to FIGS. 1 A and 1 B. The guide ribs mentioned several times are marked with 9 ^ a> these are also aligned obliquely downwards here, and FIG. 9-A shows them Recognize the arrangement in the cross-section. It will be appreciated ,, that the ribs 94 a are formed in that the surface of the plate wirdj provided with sipes 91 wherein said left standing surface parts outside to be bent in a plane surface substantially perpendicular to the top ■ _ the plate stands. From the cross-section it can also be seen that ribs lying one above the other in the vertical direction are bent alternately, that is, when two incisions are placed one above the other, the remaining surface parts are bent in different directions. The differentiated representation of the figure. 9 allows

90 9 884/1109

Dipl.-Ing. H "ini Uitif, Pätfcilänwoff D - 8 Müridi" n 81, Cö "ima" tro8 81 Telephone: (0811) 48 38 20

know how such an intermediate plate <ji interacts with two heat transfer plates assigned to their surfaces or the guide ribs of their two surfaces. The outermost end caps of the guide ribs 9 ² J ä preferably touch the surface of the associated heat transfer plate * Since the openings 95 are now provided, the steam flowing through the channel V is constantly diverted between the two surfaces of these intermediate surfaces 91, as can be seen in particular from FIG. 9 A It can be seen that the deflection is effected by the ribs 9 * ί ä * This constant deflection has the consequence that the steam flowing through the channel V remains in the chamber for a longer time, which results in an improved condensation effect. The arrangement described here brings about AUCR nor the distributing _t that Zwischenplätte 9Ϊ the Platt ei-1 ver · strengthens * so it will be a reinforcement of the association made

The cross section according to FIG. 9 A can still be seen *. that the plates 1 can be _{versed with molding 97 #} . which hlwässerkänäle Kd within the W mutually are in contact with each other ^ to also as a stiffening effect of the association * These standing in contact with each Ausformunger 97bewiricen an effective control of the flow dös Kühlwassera If the mentioned ZwischeHplatte is provided 91, then, because of the enlarged ^ ssertett cross-sectional area of the steam channel V of the steam inlet channel must be increased accordingly, which of course must also result in a corresponding increase in the size of the channel for the condensed liquid «

It is understood that _t lift Rahrieh the previously described embodiments Eünielmerkmale of Ainet! Embodiment can be combined with one-time kiosks of the other, the Kbmbirtättiön8ra8l "Llchkeiten are geared towards the misplacement of the use" ine "hl # r addressed PlSttenkondettätöre * Xn each individual case iflust be ensured in order to achieve the invention

Dipl.-Ing. Heini UiUt. Patent attorney D - 8 Munich 81, Coiimqsfrafci 8ί - TeUfon: (0611) 48 38

that over vorerewMhlte areas of WärmeäüstäüsGhplätten that Köndensätiönströpfen ^ are collected and that the condensed liquid Ström _s it is passed to appropriate käririj be individual currents controlled given to an outlet towards wherein. Oils hereby änge which would be discussed in detail in connection with FIGS

Be summarized.

In the figures "I ¹ IA and,! ¹ ! B are

of flat condensers of conventional design, the effective width La in the vicinity of a Dampfifl · * 'lasskänäis 153 is with these "previously known plates half as large as the width Lb of the channel in about its Mitiäerem Bereleh, dei" with Xb "From the position it can be seen without further ado that along the Strftmufigskänäls for the demisf a turmoil in the" Sti * ömüfigsgesGhwindisk§it builds up j soft? according to various physical laws, it has a pressure loss to the pole the surface de? Plate has areas that do not participate in the heat transfer: "With the vörbekännten Plattertköndenäätors with plates of this type, difficulties also arose with the supply of steam", which could only be found in elis * sölohea Meftge > the maximum amount of steam corresponding to soft through the effective heat transfer rates could be. Serve to overcome these disadvantages! The execution forms already described according to the invention also have the design forms according to the guidelines for A and 5 B as well as according to FIGS. 8 A to 8 D *

Dipl.-Ing Η · ίηΐ L «tt * r. Patent attorney D - 8 MOnatat 81, Cciimastrafc «81 - T« l «fon: (0811) 48 38 20

- 19 -

In the embodiment according to FIG. 5 A, the heat transfer plate is 1 provided with surface 1 a with a steam inlet channel 52, which lies within the area that is of the Sealing ring 5 a surrounded 1st. This from the sealing ring Surrounded area corresponds almost to the full plate area la. The steam inlet passage 52 is arranged through a vertically Supported !!. 5 ^ reinforced or stiffened. The current? channel 52 corresponds in cross section to a flow channel 52 b in the plate 1 with surface 1 b, further details of these two plates do not require any explanation, as here corresponding Punctures with the execution ^ shape according to the figures 1 A and 1 B exist.

In the execution form according to the figures B A and R B is the

Heat transfer plate 1 with surface i a. is provided with a steam inlet duct 82 which, within the area of the sealing ring; 5 a surrounding area 1 a * As in the embodiments described so far, in which the steam inlet duct extended over almost the entire width of the individual panels, The Danp ^ inlet duct 82 extends here almost over the entire length of the plate 1 within that of the sealing ring ^ a surrounding area, below this channel 82 is the outlet channel P3 for the condensed liquid is arranged, which abil against the channel B2 through a transverse wall 89 separates is «The right end of the transverse wall 89 ends at a distance | voi 'the sealing ring 5 a ,. as can be easily seen from Figure B A.

In the two embodiments discussed here according to Figures 5 A / B and 8 A / B, the width or length of the steam inlet channel is identical to that of the .effective Heat transfer surface * This has the consequence that in the in The steam flowing into the steam channel has no pressure loss is created, and that the incoming steam over the

0 9 8 8 4/1109

BATH ORIGINAL Dipl.-Ing. Heinz Lasser, tntentonwalt D - 8 Munich 81, Cosimastraft 81 TeUfon: (0811) 48 38 20

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entire width or length of the surface 1 a can be distributed, it being through guide parts for the condensed liquid pe '. is driven. The incoming steam can therefore over the entire effective heat transfer area can be condensed and reflected on this. As the condensation progresses, the condensed drops grow and, due to their own weight, fall downwards collected by the guide parts, which then a controlled flow of the condensed liquid to the outlet channel cause. The steam channel 82 b, the channel 8.3 b for the condensed liquid, the cooling water inlet channel 86 a and the Kühlwaeser outlet channel 86 b are in the plate with surface 1 b shaped, these channels correspond in their shape and arrangement to the channels described in the plate with the surface 1 a. It should be noted in particular that the V cooling water inlet channel 86 a and the outlet channel 86 b so in the plate with surface 1 b are shaped that the cooling water flowing down, this channel is against the channels 82b and 83b sealed by the sealing ring 5e.

In the execution forms according to Figures 8 C and 8 D are the steam inlet duct 85 and the outlet duct 87 for condensed Liquid formed in diametrically opposite corners of the plate, the channel 85 is in cross section bigger than canal 87. ' ■ "■" ""

It was already noted at the beginning that the seals provided in plate capacitors of conventional design are subject to rapid wear. This problem rapid wear of seals takes the The present invention also applies. The one suggested here Improvement suggests the use of metallic sealing washers or spacers in the edge area of the steam duct before. If such spacers are provided, then this is

9 0 9 8 8 4/1109

Dipl.-Ing. Heinz Lasser, patent attorney D - 8 Munich 81, Cosimastrgft 81 TeUfon: (0611) 48 38 20

- 21 -

a rapid wear of the seals prevents, because this then are not directly exposed to the steam of high pressure and high temperature. Figures 10 A and 10 B show one Embodiment of such spacers, denoted by the reference numerals 102 and in the edge regions of the heat transfer plates are arranged. The distance between the the spacers 102 between fixing plates 1 Is determined by their plank, the one area of these 'spacers 102 is provided with a groove or recess 107 into which a sealing ring 106 can be inserted. The other face this spacer 102 is provided with a projection 103, these projections fit into the (individual channels. As the illustration shows, the edge areas are located 104 of the individual plates on these projections 103 of the spacers 102 so that in the area of these contact surfaces a suitable connection of the plates with the spacers can be made. The representation is also without further recognizable, as also here by the individual plates in turn, vapor channels and channels for cooling liquid are created. The Dlditurigsringe 106 to be used has preferably a circular cross-section, which then becomes an oval «η Cross-section is deformed when the individual panels seal be connected to each other, the 4 sealing ring is then voi; ■ constantly received in 4er recess Io7 of a spacer 102. In particular the enlarged representation according to the figure 10 B shows that the undeformed cross-section of the individual sealing rings should be larger than the cross-section the recesses in which they are inserted. When the individual heat transfer plates are connected to each other are, so the individual DJ youth rings are complete are received in their recesses, then these sealing rings protected by the side wall of the recesses against the steam or against the cooling water, so that these media are unable to attack the sealing rings.

909884/1109

19088OQ

Dipl.-Ing. H «ini LasMr. PqtentanwoU D -. 8 MOndim 81. Cosimastrafi 81 Telephone: (QBIl) 48 38ί 20

- 22 -

open ^ primarily the metallic spacers, which by nature less wear than a sealing material, are subject, so that the desired advantages are achieved. The use of the spacers brings with it rubs with the advantage that the sealing rings can be made smaller, which can lower costs, incurred for replacing such sealing rings.

In Figure IQ C is another embodiment of a fiction according to the sealing spacer, the sealing ring 106t is made of a material that can withstand heat and pressure, such as Metal or as-best. The spacers are 1Q2 b provided here with no recesses, the sealing rings 106 b but also here between adjacent spacers un-> ter pressurization held. Although the herewith In, Proposal brought sealing rings 106 b compared to the aforementioned Sealing rings 106 are more expensive because they are gonefp the provided spacers cheaper than conventional sealing rings, because they can be made thinner, whereby; the cost of a necessary replacement can be reduced can. Although from the representation not easily epr recognizable ,, the cross-section of these sealing rings iQ6b is beautiful conical, which means that the contact surface on the spacer pieces is enlarged, which has the advantage that Sealing rings with such a cross-section can withstand a higher pressure,

Further embodiments are shown in FIGS. 11 and 12 sealing device according to the invention shown in Flg ^ r 11, a spacer is designated by 112, which is attached to his each of the two surfaces is provided with a recess 117 a or 117 b. These spacers 112 are made of one heat, Driffsk and wear-resistant material. In the V A sealing ring 116 is provided in each case

9884/1109

Dipl.-Ing. Heinz Uft «t _r patent attorney D - 8 MOndWi 81, Cosimostrofe · 81 - Telephone: (0611) 48.38 20

- 23 -

made of elastic material such as rubber or a synthetic resin, is made and has a circular cross-section which is slightly larger than the depth of these recesses. This circular cross-section is also deformed here if the individual heat transfer plates sealingly to one another are connected. In Picrur 12 A- is the cross-sectional profile Another embodiment of a spacer shown. The projection 122 of the spacer is with an im «Cross-section V-shaped recess 127 is provided, which can be formed, for example, by a pressing process. Like Figure 12 B shows surrounding V-conveyor recesses 127 of the spacers two adjacently arranged plates a cavity 128 in which a sealing ring 126 circular or rectangular Cross-section can be inserted. If the steam channel V is now partially shown, steam flows through it, and If this steam penetrates into this cavity as a result of its pressure in the direction of arrow 125, then it acts on the Sealing ring 126, this is deformed in such a way that it is pressed to the left. The bigger the acting Therefore, the more effective the sealing effect is. The illustration shows this without further ado, it also reveals that the dictation process is loosely in the by the recesses enclosed cavity is inserted so that it is elastic through the steam pressure acting on it can be deformed. It also needs to be pointed out that the cavity enclosed by the projection 122 is also filled with a seal 123 in order to prevent it from sagging of the projection when pressure is applied to the sealing ring 126, the Püllköroer 123 does not necessarily need To be a sealing material, it can be more like the support bodies of the embodiments described above act around a metallic body.

In the figures 13 A to 13 C different embodiments

909884/1109. .

BATH ORIGINAL

Dipl.-Ing. Heinz Lauer. Patent attorney D - 8 Munich 81, Coiimastrafc · 81 ■ Telephone: (0611) 48 38 20

-2H-

Shapes for sealing the cooling water channel W shown. According to the embodiment according to FIG. 13A, the side edge of the heat transfer plate 1 is shaped in such a way that it is provided with a contact end 132a and a recess 13Ίa. Two heat transfer plates 1 forming the steam channel V are assigned to one another in such a way that the contact end 132 a of one plate rests against the contact end 132 b of the other plate, and that the bottom 13 ¹ J a of the recess of one plate corresponds to the corresponding bottom 13 ¹ J b facing the other plate. A reinforcing or stiffening piece 135, which serves to seal off the steam channel V, is arranged in the intermediate space. Reference numeral 136 denotes a sealing ring for sealing the cooling water channel W; The stiffening pieces 135 and the sealing rings 136 are thus arranged in the edge regions between the individual panels connected to one another; they are kept under pressure by the contact ends of adjacent panels being connected to one another in a suitable manner.

A significantly improved arrangement of the parts 135 and 136 bring the design form according to FIGS. 13 B and 13 G. Here (FIG. 13 B) the sealing rings 136 are not directly acted upon by the high pressure cooling liquid flowing through the channel W, for On the other hand (FIG. 13C), the steam flowing through the channels V cannot act on the stiffening body 136. Both embodiments are still advantageous 13. A comparison with the embodiment according to figure that the special shape of the edge strips of the individual WärmeUbertragungsplatten manages surfaces more investment, which entails the possibility that 136 an increased pressure force can be exerted on the parts 135 and or that these parts are held absolutely securely in place.

Below is now using an exemplary Uhrungsbeispieles the

90 9 8 8 WtA 109 ' ■' ~ -

Dipl.-Ing. Heini Lasier, patent attorney D - 8 Munich 81, Coiimoitra & e 81 Telephone: (0611) 48 38 20

- 2.5 -

Advantage can be demonstrated in the operation of the plate capacitor according to the invention, the collecting device of which has been described with reference to the individual embodiments. For use, the heat transfer plates come to the figures 1 A, 1 B, 2 and 3 A, there are four heat transfer plates of 6.4 - copper made, having a width of 5 cm and a height of 50 cm, with a thickness of 0.1 cm . The effective heat transfer area measures 47 χ 38 cm. (the effective total heat transfer area measures 0.73 m and the area of the vapor area measures 0.1 χ 0.04 m). Each guide point for condensed liquid; is an angle piece with a length of 0.5 cm, one * thickness of 0.02 cm and a "length of the angle piece of 6 cm. On each heat transfer plate 1 with surfaces la 48 such angle pieces are arranged at an angle of inclination of 45 °. Dem The system is then fed from a source 20 m wide in an amount of 130 kg / h, which is drained off shortly before the steam duct 2. Tap water is used from cooling water »The percentage heat transfer can be calculated using the following equations:

Δ. Tm

where K = % heat transfer in Kcal / mh ^Q C.

qs = heat application in keal / mh _:.

^ - Tm = logarithmic mean of the temperature difference ^o G and OTm =, ö'T ₂ - / ^ T, ·

f-

OIL

= ^T s - ^T wi

where Tg temperature of the steam condensation in% o ^{= tem perature in} the vicinity of the cooling water T wl = temperature in the vicinity of the cooling water _{inlet channel in}

% o ^{= tem perature in} the vicinity of the cooling water outlet duct In pC

909 8 84/1109

19-8800

Dipl.-Ing. Heinz Lesser. Patent Attorney D - 8 Munich 81, Coiimastrofc · 81 · Telephone; {0811) 48 38 20

If one compares the application of heat in the case of using a capacitor according to the invention with that of a conventional capacitor, then the former recorded an increase; of 26.5% over the letzteren'bei a condensation temperature of about 97 ⁰ C., an increase of 39% at about 80 ° C and an increase of 90 ° at about 65 ⁰ C, the flow rate of the cooling water is disregarded. The lower the condensation temperature, the greater the increase in heat loading.

With regard to the effect of the vapor pressure, assuming that the flow rate of the cooling water is constant and its temperature in the vicinity of the inlet channel is around 20 ° C, it can be stated that with a lower vapor pressure: a smaller amount of heat can be determined, i.e. the amount of condensed liquid Is then lower * A decrease: the vapor pressure results in a smaller number of vapor molecules that spray on the surfaces of the heat transfer plates. As a result, longer time intervals between the falling condensed _ \ liquid occur, the removal of condensed liquid from the system is so slow. The reduction in steam pressure leads to a reduction in the amount of condensate in the steam. ..- .. ". ·

In the case of conventional plate condensers with no device for collecting the condensate, the percentual heat transfer under the same conditions was 1100 Kcal / mh ° C at a flow rate of the cooling water in the order of 0.6 m / sec and at a condensation temperature of ton 95 % C, while it was 1550 Kcal / mh C in the case of the capacitor according to the invention. The use of the device for collecting the precipitate according to the present invention thus brings about a ¹ % increase in the percentage of heat transfer with only a 5.5% increase in the effective one

9098 8 4/1109

Dipl.-Ing. Heina letter. Patent attorney D - 8 Munich 81. Cosimmtroft 81 Telephone: (0611) 48 38 20

- 27-

Heat transfer; unrcsf lache for what the arrangement of the individual Guide parts for collecting the condensed liquid Cause are. .

9 0 9 3 9 '4/1 1 U 9

Claims (1)

PATENT CLAIMS (1 · / plate capacitor with a large number of alternately arranged Steam channels and cooling water channels, which are formed by a large number of worm transfer tubes; r; e k e η. -η ζ e ic h η et that the surfaces of the heat transfer plates facing the steam channels with a Device for collecting condensed liquid from the vapor are provided, which a guide device for by this collection facility; collected, condensed Liquid is downstream, und.das means for sealing the damnfkanäle and provided for sealing the cooling water channels are. 2. Plate capacitor according to claim 1, through this. g e - indicates that each collection facility has a A plurality of condensed liquid-guiding guide points comprises, which are parallel to one another and obliquely downwards directed at the named surface of the individual heat exchangers are arranged / 3. Plate capacitor according to claim 1 or 2, d ad u r c h marked that the guide device from a plurality of condensed liquid channels consists, which are .formt on the named surfaces of the heat transfer plates. 4. Plate capacitor according to at least claim 1, d a d u r c h marked that each collection facility from a multitude over the one surface of the heat transfer platefa frying projections of a certain ^: ~ ^J 'length bleached ¹ "is -'i which are parallel to each other with spacing Dipl.-Ιης. Heini U «« r. Patent attorney D - 8 Munich 81. Codmwtrafee 81 · Τ · Μοη: (0811) 48 38 20 -'29 - -'are arranged and aligned obliquely downwards. 5. Plate capacitor at least according to claim 1, characterized in that each collecting device from a multitude of in one surface the heat transfer plates formed recesses for Leading the condensed liquid is formed, which arranged parallel to each other at a distance and obliquely after are aligned below, 6. Plate capacitor at least according to claim l _s characterized geke η η ζ eich η et _n that each collecting device is formed from an intermediate plate arranged between two heat transfer plates in the steam channels. 7. Plate capacitor according to claim 6, d a du r c h g e · - k e η η ζ e i c h η e t that every surface of every intermediate plate is provided with a plurality of condensed liquid leading guide parts, which are attached to the Areas arranged parallel to one another with a spacing and are oriented diagonally downwards, 8. Plate capacitor according to AJispruc ^ 6 »dad u r c h g e k e η η ζ e i eh. net that each of the two surfaces each intermediate plate has a multitude of projections a certain length which is parallel to each other are arranged at a distance and diagonally downwards, 9. Plate capacitor according to claim 8, d ad u r c h g e k e η η ζ e i c. h η e t -. ",.; that the steps each Intermediate plate with this one-piece and through a punching and covering process are executed. 809S8A / 1TQI ■ 19088QQ CXpt-lnq. Heim Uw, Potentanwalt D - ■ MOnaSwi 81. GwaKHbeft · 81 · T * Ufon: {0811) «38 30 10, according to Plattenkpndensator Änsopiich 6, dadurc h in daqs Each surface of each intermediate plate is provided with a plurality vonAusformungen, which are aligned parallel to each other with Abstand.angeordnet and obliquely downward. 11, Plattehkondensator at least according to claim 1, d a- _t by in that the heat transfer plates are each provided with at least one steam inlet duct and provided with an outlet duct for condensed liquid which Durchlassftffnungen represent the individual plates. 12. Plate capacitor according to claim 11, dad μ rc H characterized in that der'Dampfeinlasskanal along the top edge of each plate above their collecting device and above their guide device for the liquid condensed from the steam is arranged in a horizontal first course. 13. Plate capacitor according to claim 11, that?} Μ rc h marked that the steam inlet duct along at least one side edge of each heat transfer plate is arranged in vertical er ^ treckμnR. I ¹ I, plate capacitor according to one of claims 11 to 13 », characterized by the fact that the effective cross-sectional area of the steam inlet channel is greater than that of the ΑμβΙ ^ ββΚαηβΙβ for condensed liquid. 15, plate capacitor at least according to claim 1, since ■ -by geke η η ζ eich η et _f that the means'; to seal a steam channel between two of these bil-. : 9Ö9884 / 1 109 Dipi.-lng. Hwnz U »» r. Patent attorney D - 8 M0ndS * n 81, Cosimoftrafc · 81 ■ Telephone: (QtII) 46 3620 - 31 - .Denden heat transfer plates arranged in their edge area Spacers are held between the heat transfer plates fixed with respect to one another are. 16. Plate capacitor according to at least claim 15, characterized marked that each A spacer in at least one surface that is in contact with the edge area of the windshield distortion plates is provided with at least one recess or groove is in which a sealing ring of circular cross-section on (? er.ormr> n 1st, the diameter of which is greater than the Deep ier recess or groove. 17. Plate capacitor after opening 15 or 16, because ρ: eke η η ζ calibrate η et that ^ every spacer from a heat, pressure and wear resist-; standing material. 1 ^. PlTttenkon-ier.sator at least according to claim 1, dad urch r Eke η η ζ η et verifiable, "that the center for sealing""the vapor kanzle ', leweils from two edge portions benachbarter.W ^ rmeübertrap-untrsplatten are formed. 1 a V-shaped recess is provided which are assigned to one another in such a way that the grooves of two adjacent heat transfer plates enclose a cavity in which a door opening moves; ■ borrowed from ^ Timen is. ■ "' BATH ORIGINAL Empty soap