US3783090A - Heat exchanger plates - Google Patents

Heat exchanger plates Download PDF

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Publication number
US3783090A
US3783090A US00226693A US3783090DA US3783090A US 3783090 A US3783090 A US 3783090A US 00226693 A US00226693 A US 00226693A US 3783090D A US3783090D A US 3783090DA US 3783090 A US3783090 A US 3783090A
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United States
Prior art keywords
plate
ridges
grooves
heat exchanger
face
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Expired - Lifetime
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US00226693A
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English (en)
Inventor
J Andersson
N Stadmark
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Alfa Laval AB
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Alfa Laval AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/083—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning capable of being taken apart

Definitions

  • the heat exchanger plates include at least one plate having on one face of its heat transferring part a first group of ridges extending in parallel spaced relation to each other and pressed upward from the plane of the plate, this face also having a first group of grooves extending in parallel spaced relation to each other at an angle to the ridges and depressed from said plane; and the other face has second groups of ridges and grooves formed by the grooves and ridges, respectively, of the first groups.
  • Each of these faces has its ridges substantially abutting an opposing plate so as to define therewith a set of channels between its ridges, each channel extending across a plurality of the grooves in such face.
  • the two sets of channels provide a low resistance to flow of the respective heat exchanging media, while the ridges provide effective spacing means for preventing deformation of op posing plates under the pressure difference between such media.
  • the present invention relates to heat exchanger plates of the kind having spacing members in the form of protuberances and depressions in the heat exchanging surfaces.
  • Such protuberances and depressions usually serve not only as spacing means but also to create, with reference to a desired heat transferring coefficient, a properly adapted disturbance of the flow of the heat exchanging media across the heat exchanging surfaces.
  • the present invention relates particularly to heat exchanger plates in which at least some of the spacing members on the heat exchanging surfaces will create only a small disturbance of the flow of the heat exchanging media. Spacing members of this kind are desirable, for instance, in the so-called distrbution surfaces for a heat exchanging medium. It is also desired sometimes to have spacing 'members of this kind over the entire heat exchanging surfaces, -as when the heat exchanging media are to be subjected to only a small pressure drop in their passage through the plate heat exchanger.
  • the principal object of the present invention is to provide an arrangement of the spacing members on heat exchanger plates which meets the requirements as to good strength of the plates while imposing little resistance to the flow of the heat exchanging media.
  • the heat transferring part of a heat exchanger plate is provided on one face with spaced parallel ridges pressed up from a plane of the plate ice and with spaced parallel grooves, forming an angle with these ridges, depressed from the same plane of the plate.
  • the other face of this heat transferring part has ridges and grooves formed by the grooves and ridges, respectively, on the first face; and each face has its ridges substantially abutting an opposing plate so as to define therewith a set of channels between its ridges, each channel extending across a plurality of the grooves in the same face.
  • the two sets of channels serve for passage of the respective heat exchanging media with relatively small flow resistance.
  • each channel has a wall which is bounded laterally by spaced ridges and which consists of a number of unobstructed parallelogram areas located one after the other in a row, each of which is surrounded along its four sides by the ridges and grooves pressed in difierent directions, where the so-called limit of stretching strain for the plate material has been increased by the cold-forming of the ridges and grooves.
  • heat exchanger plates of a given material can be made as thin as possible for a given difference in pressure between two heat exchanging media, and for a given flow resistance for these media in the finished plate heat exchanger. This is of great importance from a material-saving point of view and also from a production point of view. Also, for the heat-transferring ability of the heat exchanger plates, it is important that they be as thin as possible.
  • the shape of the ridges and grooves may vary in different ways.
  • either the ridges or the grooves may extend without interruptions along the whole or at least a great part of their respective lengths.
  • the ridges as well as the grooves have such interruptions.
  • ridges and grooves which cross each other have interruptions at their common crossing points, the portions of the plate at their interruptions preferably being situated in the same plane as the afore-mentioned plane of the plate.
  • the extensions of the grooves are interrupted by the ridges, the latter having interruptions in their extensions which are so placed that unbroken portions of the plane of the plate extend parallel to the grooves across these ridge interruptions.
  • a plate having an arrangement of spacing members as described above be used together with plates of the same kind in a plate heat exchanger.
  • the advantages of the described arrangement are believed to be utilized in the best way if plates of the same kind are used.
  • the ridges and the grooves should then be so formed in each plate that when two plates are put together in a plate heat exchanger in a conventional manner, ridges on one plate will abut, along the whole or a part of their respective lengths, corresponding ridges parallel thereto on the other plate.
  • FIG. 1 is a plan view of part of a heat exchanging surface of a plate according to the invention
  • FIGS. 2 and 3 are sectional views along the lines A-A and B-B, respectively, in FIG. 1;
  • FIG. 4 shows a section through three cooperating plates according to FIG. 1;
  • FIGS. 5-8 are views corresponding to FIGS. 1-4, respectively, but showing a second embodiment;
  • FIGS. 9-12 are views corresponding to FIGS. 1-4, respectively, but showing a third embodiment;
  • FIGS. 13 and 14 are sectional views 3 Y 7 showing different embodiments of the previously mentioned plane of the plate;
  • FIG. 1 is a plan view of part of a heat exchanging surface of a plate according to the invention
  • FIGS. 2 and 3 are sectional views along the lines A-A and B-B, respectively, in FIG. 1
  • FIG. 4 shows a section through three cooperating plates according to FIG. 1
  • FIGS. 5-8 are views corresponding to FIGS. 1-4, respectively, but
  • FIG. 18 is a perspective view of two cooperating plates according to FIG. 17; and FIGS. 19-21 are sectional views along the lines k-k, l[ and m-m, respectively, in FIG. 18.
  • the embodiment of the plate according to FIGS. 1-4 has spaced parallel ridges 1 pressed up from a plane 2 of the plate, and spaced parallel grooves 3 forming an angle (a) with these ridges, the grooves being depressed from the same plane 2 of the plate.
  • each ridge 1 is uninterrupted along its length, while the grooves 3 are interrupted along their respective lengths by the ridges 1.
  • the pressed-up ridges 1 define between them upwardly opening trough-like channels 4 (FIG. 3), the bottoms of which are constituted by substantially the said plane 2 of the plate.
  • the bottoms of the channels 4 are formed by several parallelogramshaped areas arranged in a row one after the other between the ridges 1.
  • a second group of ridges is formed by the depressed grooves 3, these ridges (like the grooves 3) having interruptions in their extensions; and a second group of grooves is formed by the ridges 1, these grooves (like the ridges 1) being uninterrupted along their respective lengths.
  • channels 5 are formed on this face which have the said plane 2 of the plate as their bottom and which are similar to the first set of channels 4. The latter channels 5 extend between the ridges on this face of the plate, which are formed by the said grooves 3.
  • the plate has on one face a first set of parallel channels 4 and on the other face a second set of parallel channels 5 forming an angle (a) with the first channels.
  • the channels 4 and S are intended for throughflow, in their respective longitudinal directions, of the two heat exchanging media separated by the plate.
  • FIG. 4 it shows how three heat exchanger plates A1, B1 and C1, conotructed according to FIG. 1, define flow passages in a plate heat exchanger.
  • Each plate is turned 90 in its own plane relative to the adjacent plate.
  • each of the channels 5 of the plate A1 forms together with a respective channel 4 of the plate B1 a substantially closed channel 6 between the plates A1 and B1.
  • closed channels are formed between the plates B1 and C1 by the channels 5 of the plate B1 and the channels 4 of the plate C1, the latter closed channels extending at right angles to the channels 6.
  • the pressed-up ridges 1 in FIG. 5 like the depressed grooves 3, have interruptions at certain intervals in their respective lengths. (These interruptions are not necessarily as regularly spaced as shown in this embodiment.)
  • the interruptions in the extension of the ridges 1, which are designated 7, are situated at opposite sides of the parallelogram-shaped areas which form the bottoms of the channels 4 between the ridges 1.
  • the parts of the plate situated at the interruptions 7 are in the same plane as the parallelogramshaped areas, so that unbroken parts of the said plane 2 of the plate extend parallel to the grooves 3 across these interruptions 7.
  • FIG. 8 is a sectional view corresponding to that in FIG. 4 but showing three plates A2, B2 and C2. according to FIG. 5.
  • FIG. 9 The difference between the embodiment of FIG. 9 and that shown in FIG. 5 is that the interruptions in the extensions of the pressed-up ridges 1 in FIG. 9 are situated where these ridges would otherwise cross the grooves 3 instead of between these grooves.
  • Such interruptions in FIG. 9 are designated 8.
  • the parts of the plate situated at the interruptions 8 are in the same plane as the parallelogram-shaped areas between the ridges 1 and the grooves 3, i.e., in the previously mentioned plane 2 of the plate, as can be seen from FIGS. 10-12.
  • FIG. 12 is a sectional view corresponding to those in FIGS. 4 and 8 but showing three plates A3, B3 and C3 according to FIG. 9.
  • the parallelogram-shaped areas between the ridges 1 and the grooves 3 are entirely planar. This is not essential. As shown in FIGS. 13 and 14, these areas may be stifiened by being bent in one or the other direction or provided with a generally corrugated shape in section. Further, these parts of the plate (as will be evident from the following) need not be centered exactly between the crests of the ridges 1 and the underneath sides of the grooves 3.
  • FIGS. 15 and 16 show two kinds of heat exchanger plates, which can utilize any of the arrangements according to FIGS. l-l4.
  • the plate of FIG. 15 is a so-called cross flow plate, in which case a first heat exchanging medium flows across the plate on one side of it (the upper side as shown) from an inlet 9 to an outlet 10, while a second heat exchanging medium flows on the other side of the plate (crossing the flow direction of the first medium) from an inlet 11 to an outlet 12, the plate being gasketed in the usual manner as indicated at 17.
  • the ridges 1 and grooves 3 are illustrated in FIG. 15 by dashed lines.
  • every second plate is turned in its own plane relative to the other plates, so that the ridges of one plate will extend parallel with and abut the underneath side of the grooves of the adjacent plate. It is also possible that every second plate be turned about an axis extending in the plane of the plate.
  • the heat exchanger plate of FIG. 16 is adapted for substantially concurrent or counter-current flow of the two heat exchange media.
  • the heat transferring area of this plate is divided into three areas F, G, and H, which have different kinds of turbulence effecting protuberances and depressions.
  • the plate also has an inlet 13 and an outlet 14 for a first heat exchanging medium which flows on one side of the plate (its upper side as shown) and an inlet 15 and an outlet 16 for a second heat exchanging medium which flows on the opposite side of the plate (countercurrent flow heat exchange).
  • each plate has a strip seal or gasket 17.
  • the flow of the said first heat exchanging medium from the inlet 13 to the outlet 14 is illustrated by arrows 18.
  • the purpose of the above-mentioned division of the heat transferring surface of the plate into areas having difierent designs of the turbulence effecting members is to distribute the heat exchanging media in the best way over the entire width of the heat transferring surfaces on their way from their respective inlets to their respective outlets.
  • the so-called distribution surfaces F and H are provided with turbulence-effecting members so formed that the flow resistance for the medium entering through the inlet 13 or the inlet 15 is substantially less in these distribution surfaces than in the central part G of the plate, the latter part constituting the main heat exchanging surface of the plate. This reduces the effects arising from the fact that certain portions of the heat exchanging media must flow a longer way than other portions across the distribution surfaces.
  • the previously described arrangement of the pressed-up ridges 1 and depressed grooves 3 is particularly useful, in heat exchanger plates of this kind, for the so-called distribution surfaces F and H.
  • FIG. 17 shows a heat exchanger plate P1 of the same kind as in FIG. 16, the distribution surfaces F and H being provided with pressed-up ridges 1 (full lines) and depressed grooves 3 (dashed lines).
  • the squares formed on the plate by these ridges and grooves constitute the previously mentioned parallelogram-shaped areas.
  • One of the ridges in the distribution surface F is designated 19, and one of the ridges in the distribution surface H is designated 20.
  • the plane 2 of the plate (i.e., the plane of the parallelogram-shaped areas) has been displaced a distance a perpendicular to the plane of the plate, so that the pressed-up ridges have a height over the plane 2 of the plate which exceeds by 2a the distance between the plane 2 of the plate and the underneath sides of the depressed grooves 3.
  • the plane 2 of the plate is centered between the crests of the ridges and the underneath sides of the grooves.
  • the plane 2 of the plate is displaced the same way in the area between the ridge 20 and the opening 15.
  • FIG. 18 shows the plate P1 of FIG. 17 and a plate P2 of the same kind which is turned in the aforesaid manner.
  • the ridge 19 of the plate P1 will cross the ridge 20 of the plate P2 in the way that can be seen from FIG. 18.
  • four different areas K, L, M and N are defined within the two cooperating distribution surfaces F and H.
  • FIGS. 19-21 show sections through the two cooperating plates P1 and P2 along the lines kk in the area K, l-l in the area L and mm in the area, M, respectively, in FIG. 18.
  • the two plates P1 and P2 are assumed to have in their distribution surfaces an arrangement of ridges and grooves of the kind shown in FIG. 1.
  • the thickness of the plates P1 and P2 i.e., the distance between the plane of the crests of the ridges 1 and the plane of the underneath sides of the grooves 3
  • the depth of the interspace between the plates i.e., the height of the channels 6 (see FIGS.
  • a series of heat exchanger plates disposed in opposing face-to-face relation, at least one of said plates including a heat transferring part having on one face a first group of ridges extending in parallel spaced relation to each other and pressed upward from a plane of the plate, said one face also having a first group of grooves extending in parallel spaced relation to each other at an angle to said ridges and depressed from said plane, the other face of said heat transferring part having second groups of ridges and grooves formed respectively by the grooves and ridges of said first groups, the ridges of said first group substantially abutting a first opposing plate of said series and defining therewith, and with said one plate at its region-s between said first ridges, a first set of channels for a first heat exchanging medium, each said channel extending across a plurality of grooves of said first group, the ridges of said second group sub stantially abutting a second opposing plate of said series and defining
  • Heat exchanger plates according to claim 1 in which the ridges of said first group have at least one interruption in their respective lengths.
  • Heat exchanger plates according to claim 1 in which both the ridges and the grooves of said first groups have at least one interruption in their respective lengths.
  • each said interruption is located at the point where a ridge of said first group crosses a groove of said first group.
  • Heat exchanger plates according to claim 1 in which said ridges and grooves are straight.
  • Heat exchanger plates according to claim 1 in which said angle is 9.
  • said second opposing plate has ridges and grooves as in said one plate and is oriented with its ridges on one face parallel to and substantially abutting, along at least part of their respective lengths, opposing ridges of said second group on said one plate, whereby each channel of said second set also crosses a plurality of grooves in said one face of said second opposing plate.
  • Heat exchanger plates according to claim 1 in which said one plate has a pair of openings spaced from each other along one edge of the plate for admission of said first medium to and discharge from, respectively, the interspace between said one plate and said first opposing plate, said heat transferring part being located between said admission opening and an edge of said one plate opposite its said one edge and having its ridges of said first group extending substantially in the direction from said admission hole toward said opposite edge, said one plate having a second heat transferring part located between said discharge opening and said opposite edge, said second part having ridges and grooves as in said first part and with the ridges of its first group substantially abutting said first opposing plate but extending substantially in the direction from said opposite edge toward said discharge opening, said first group of ridges of the respective heat transferring parts slanting toward each other while extending in their respective said directions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00226693A 1971-02-19 1972-02-16 Heat exchanger plates Expired - Lifetime US3783090A (en)

Applications Claiming Priority (1)

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SE02132/71A SE353954B (fr) 1971-02-19 1971-02-19

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US (1) US3783090A (fr)
JP (1) JPS52271B1 (fr)
DE (1) DE2207756C3 (fr)
FR (1) FR2125471B1 (fr)
GB (1) GB1357282A (fr)
IT (1) IT947614B (fr)
SE (1) SE353954B (fr)

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US3995689A (en) * 1975-01-27 1976-12-07 The Marley Cooling Tower Company Air cooled atmospheric heat exchanger
FR2341119A1 (fr) * 1976-02-12 1977-09-09 Fischer Helmut Echangeur de chaleur constitue par des plaques de differents types
US4141412A (en) * 1977-01-27 1979-02-27 Culbertson Donald L Air-to-air heat recuperating unit
US4230179A (en) * 1979-07-09 1980-10-28 Haruo Uehara Plate type condensers
US4293033A (en) * 1979-06-29 1981-10-06 Linde Aktiengesellschaft Plate-type heat exchanger
US4470454A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
US4470453A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
US4586562A (en) * 1983-08-10 1986-05-06 Eltech Systems Corporation Plate and frame heat exchanger assembly with anodic protection
US4605060A (en) * 1981-11-26 1986-08-12 Alfa-Laval Ab Heat exchanger plate
US4758385A (en) * 1987-06-22 1988-07-19 Norsaire Systems Plate for evaporative heat exchanger and evaporative heat exchanger
US4815534A (en) * 1987-09-21 1989-03-28 Itt Standard, Itt Corporation Plate type heat exchanger
US4915165A (en) * 1987-04-21 1990-04-10 Alfa-Laval Thermal Ab Plate heat exchanger
WO1993025860A1 (fr) * 1992-06-12 1993-12-23 Alfa-Laval Thermal Ab Echangeur de chaleur a plaques pour liquides circulant a debits differents
US5398751A (en) * 1991-06-24 1995-03-21 Blomgren; Ralf Plate heat exchanger
US6267177B1 (en) * 1999-01-19 2001-07-31 Calsonic Kansei Corporation Flat tubes for use with heat exchanger and manufacturing method thereof
US6318456B1 (en) 1999-03-06 2001-11-20 Behr Gmbh & Co. Heat exchanger of the crosscurrent type
US6681846B2 (en) * 2001-11-02 2004-01-27 Behr Gmbh & Co. Heat exchanger
US20040069473A1 (en) * 2001-01-04 2004-04-15 Ralf Blomgren Heat transfer plate plate pack and plate heat exchanger
US20050039899A1 (en) * 2003-07-22 2005-02-24 Viktor Brost Turbulator for heat exchanger
CN100501241C (zh) * 2005-06-20 2009-06-17 张延丰 板式空气预热器
US20110139419A1 (en) * 2008-06-17 2011-06-16 Alfa Laval Corporate Ab Heat Exchanger
US20110174301A1 (en) * 2010-01-20 2011-07-21 Carrier Corporation Primary Heat Exchanger Design for Condensing Gas Furnace
US20120031595A1 (en) * 2009-01-12 2012-02-09 Alfa Laval Corporate Ab Reinforced heat exchanger plate
US20120168112A1 (en) * 2011-01-05 2012-07-05 Hamilton Sundstrand Corporation Laminated heat exchanger
EP2508831A1 (fr) * 2011-04-07 2012-10-10 Alfa Laval Corporate AB Echangeur thermique à plaque
CN102997742A (zh) * 2012-12-14 2013-03-27 新兴能源装备股份有限公司 一种全焊接板式换热器板片及使用该板片的换热器
US20140216687A1 (en) * 2013-02-07 2014-08-07 Jay Stephen Kaufman Corrugated Tube Regenerator for an Expansion Engine
EP2775247A2 (fr) * 2013-03-08 2014-09-10 Danfoss A/S Échangeur de chaleur à double motif d'alvéoles
US9739542B2 (en) 2012-10-30 2017-08-22 Alfa Laval Corporate Ab Heat transfer plate and plate heat exchanger comprising such a heat transfer plate
EP3115732A4 (fr) * 2014-03-04 2017-12-27 Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. Plaque d'échange thermique et échangeur de chaleur de type plaque
US10145625B2 (en) 2013-03-08 2018-12-04 Danfoss A/S Dimple pattern gasketed heat exchanger
US10443955B2 (en) * 2014-09-08 2019-10-15 Valeo Systemes Thermiques Tube with a reservoir of phase-change material for a heat exchanger
US10837717B2 (en) * 2013-12-10 2020-11-17 Swep International Ab Heat exchanger with improved flow
US11441854B2 (en) * 2016-04-25 2022-09-13 Novares France Heat exchanger made of plastic material and vehicle including this heat exchanger
US11486657B2 (en) 2018-07-17 2022-11-01 Tranter, Inc. Heat exchanger heat transfer plate
US20230400257A1 (en) * 2020-12-15 2023-12-14 Alfa Laval Corporate Ab Heat transfer plate

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DE4343399C2 (de) * 1993-12-18 1995-12-14 Balcke Duerr Ag Plattenwärmetauscher
DE4431413C2 (de) * 1994-08-24 2002-10-10 Rehberg Michael Plattenwärmetauscher für flüssige und gasförmige Medien
SE526831C2 (sv) * 2004-03-12 2005-11-08 Alfa Laval Corp Ab Värmeväxlarplatta och plattpaket
JP2011133166A (ja) * 2009-12-24 2011-07-07 Mitsubishi Electric Corp プレート式熱交換器
CN102230402B (zh) * 2011-05-25 2013-09-04 北京京海华诚能源科技有限公司 热交换板束组在低焓低沸点工质发电***中的应用
ES2947513T3 (es) 2020-12-15 2023-08-10 Alfa Laval Corp Ab Placa de transferencia de calor

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Cited By (53)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995689A (en) * 1975-01-27 1976-12-07 The Marley Cooling Tower Company Air cooled atmospheric heat exchanger
US4119140A (en) * 1975-01-27 1978-10-10 The Marley Cooling Tower Company Air cooled atmospheric heat exchanger
FR2341119A1 (fr) * 1976-02-12 1977-09-09 Fischer Helmut Echangeur de chaleur constitue par des plaques de differents types
US4176713A (en) * 1976-02-12 1979-12-04 Helmut Fisher Plate-type heat exchanger
US4141412A (en) * 1977-01-27 1979-02-27 Culbertson Donald L Air-to-air heat recuperating unit
US4293033A (en) * 1979-06-29 1981-10-06 Linde Aktiengesellschaft Plate-type heat exchanger
US4230179A (en) * 1979-07-09 1980-10-28 Haruo Uehara Plate type condensers
US4605060A (en) * 1981-11-26 1986-08-12 Alfa-Laval Ab Heat exchanger plate
US4470454A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
US4470453A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
US4586562A (en) * 1983-08-10 1986-05-06 Eltech Systems Corporation Plate and frame heat exchanger assembly with anodic protection
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US4758385A (en) * 1987-06-22 1988-07-19 Norsaire Systems Plate for evaporative heat exchanger and evaporative heat exchanger
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Also Published As

Publication number Publication date
JPS52271B1 (fr) 1977-01-06
IT947614B (it) 1973-05-30
DE2207756C3 (de) 1980-09-18
FR2125471B1 (fr) 1974-12-13
DE2207756A1 (de) 1972-09-21
SE353954B (fr) 1973-02-19
FR2125471A1 (fr) 1972-09-29
DE2207756B2 (de) 1980-01-10
GB1357282A (en) 1974-06-19

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