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EP0166703B1 - Chaudière - Google Patents

Chaudière Download PDF

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Publication number
EP0166703B1
EP0166703B1 EP19850850114 EP85850114A EP0166703B1 EP 0166703 B1 EP0166703 B1 EP 0166703B1 EP 19850850114 EP19850850114 EP 19850850114 EP 85850114 A EP85850114 A EP 85850114A EP 0166703 B1 EP0166703 B1 EP 0166703B1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
flue gases
space
boiler
flue gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19850850114
Other languages
German (de)
English (en)
Other versions
EP0166703A3 (en
EP0166703A2 (fr
Inventor
Erick Arne Thuvander
Jan Evert Marten Johansson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ENERTECH VAERME AKTIEBOLAG
Original Assignee
Enertech Varme AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Enertech Varme AB filed Critical Enertech Varme AB
Priority to AT85850114T priority Critical patent/ATE37441T1/de
Priority to DK146485A priority patent/DK160584B/da
Publication of EP0166703A2 publication Critical patent/EP0166703A2/fr
Publication of EP0166703A3 publication Critical patent/EP0166703A3/de
Application granted granted Critical
Publication of EP0166703B1 publication Critical patent/EP0166703B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/263—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body with a dry-wall combustion chamber

Definitions

  • the present invention relates to a boiler which is primarily intended for single-family houses and smaller apartment buildings and is preferably heated with liquid or gaseous fuels.
  • the invention relates to an improvement of so-called low-temperature boilers with a combustion chamber of round cross-section, which is delimited by a first tubular jacket which extends inwards from the front wall of the boiler to a rear wall facing the front wall and delimiting the length of the combustion chamber, one Water storage device which surrounds the combustion chamber at its periphery and is delimited on the inside by a second tubular jacket which, together with the first-mentioned jacket, delimits a space which is annular in cross section and which is connected to the combustion chamber and a flue gas exhaust so that it is generated in the combustion chamber Flue gases flow through said space and thereby give off heat to the water storage tank before they leave the boiler through the flue gas outlet, the flue gases flowing along steering links provided in the space, which preferably comprise longitudinal profile elements of U-shaped cross-section, which are uniform around the Combustion chamber are distributed and connected to the water storage jacket to increase the area of this jacket absorbing the heat from the flue gases.
  • Boilers of this type have been available on the market for some time. In boiler designs where the flue gases flow in the above manner, the heat of the flue gases must be used as far as possible after they have left the combustion chamber and before they escape through the flue gas outlet. Experience has shown, however, that a desired reduction in the flue gas temperature during the flow through the boiler can cause certain condensation problems, especially in the lower, colder part of the boiler, and if this is not counteracted in a constructive manner, the boiler will not work properly. In addition, corrosion damage can occur on those jacket parts where acidic condensate is precipitated due to a too low boiler temperature.
  • DE-A-2 613 186 describes a boiler of the above-mentioned type.
  • U-profiles are provided to a certain extent, which form a plurality of longitudinal, parallel channels, all at their front ends are directly connected to the combustion chamber, while their rear ends open into an outlet chamber connected to the flue gas outlet behind the combustion chamber.
  • the flue gases from the combustion chamber can thus flow with uniform distribution, seen in the circumferential direction, in a single pass through the room to this outlet chamber, and since the flue gas flow running through the room has the same temperature as the flue gas flow running below, both above and below emitted an equal amount of heat below.
  • FR-A-1 316 206 shows a heater of a similar design. There are significant differences between this heater and the boiler of the type mentioned at the outset. It is a heater for the flow of a liquid or a gas, specifically through a container 20.
  • the combustion chamber also extends only partially along the container 20 , in direct contact with this. There is therefore no annular space arranged between the combustion chamber and the container. Therefore, no constructive measures have been taken to counteract uneven heat transfers at different boiler heights.
  • the flow through the individual Channels in the subject of this document means a completely uniform heat transfer to the container 20 in terms of vertical height. If, however, which is not the case, the container 20 would represent a water reservoir, it would be impossible with the device shown to avoid temperature differences at different boiler heights.
  • the invention is generally based on the object to provide a boiler of the type mentioned, which can work without difficulty with maximum utilization of the flue gas heat and thereby obtains a high boiler efficiency. More specifically, it is an object of the invention to provide a low-temperature boiler, in which a better thermal balance between the lower and upper parts of the boiler is achieved in operation, whereby the lower part of the water tank of the boiler receives a higher temperature than the boilers available on the market today , so that the condensation problems that occur especially with low-temperature boilers and the resulting corrosion phenomena are avoided.
  • 1 denotes the combustion chamber of the boiler, which is round, expediently circular cross section, which is delimited by a tubular jacket 2 made of refractory material.
  • the jacket extends from the front wall 3 of the boiler, which is formed with an insulated flap, which has a sheet metal cover 4 lying against the jacket end on the inside.
  • the burner 6 of the boiler extends through a hole 5 in the middle of the flap into the combustion chamber.
  • the combustion chamber jacket 2 is connected in the back of the boiler to a rear wall 7, which is also made of refractory material and delimits the entire space in which the flame and the flue gases from the burner 6 can spread.
  • a rear wall 7 which is also made of refractory material and delimits the entire space in which the flame and the flue gases from the burner 6 can spread.
  • the effective length of the combustion chamber is reduced by an end wall 8, which is detachably fastened to the jacket 2 shortly in front of the rear wall 7, for example with the aid of screw connections (at 9).
  • the effect of this detachable end wall on the heat absorption in the boiler is explained in more detail below.
  • the combustion chamber 1 is enclosed by the water reservoir 10 of the boiler, which is bounded on the inside by a second tubular jacket 11.
  • the casing 11 extends over the entire length of the combustion chamber casing 2 and is preferably concentric with it, such that the two casings leave a space 12 with an annular cross section between them.
  • the water reservoir is delimited radially outwards by an outer jacket 13, which is connected at its ends to the jacket 11 by means of annular end walls 14 and 15.
  • the end wall 15 is retracted a little from the front end of the jacket 11 in order to make room for insulation 16 on the front wall of the boiler.
  • the outer jacket 13 and the end wall 14 are also covered in a conventional manner with insulating material 17 which, as can be seen in FIG. 2, can fill the space inside the outer casing 18 of the boiler.
  • the space 12 between the jackets 2 and 11 should be in a known manner partly with the combustion chamber 1 and partly with a flue 19, which is located in the illustrated embodiment in the rear part of the boiler and connected to a chimney pipe 20, so that the space from the Flue gases can flow through the combustion chamber, and the flue gases can emit their heat to the water reservoir 10 before they escape through the chimney pipe.
  • the flue gas flow here runs axially along steering links that are inserted into the room and can consist in a known manner of longitudinal profile elements 21 U-shaped cross section. As can be seen from FIGS. 2-3, the profile elements can be distributed uniformly in the circumferential direction around the combustion chamber and have a radial extension which is the same or insignificantly shorter than the radial dimension between the jackets 2 and 11.
  • the outward-facing flanges of the profile members are preferably firmly connected to the water storage jacket 11 with the aid of longitudinal welding joints, so that the profile elements distribute and guide the flue gases axially and, in addition, significantly increase the heat-absorbing surface of this jacket and thus enable greatly improved heat transfer to the water storage device .
  • the profile elements 21 serve as a guide for the combustion chamber casing, so that it can easily be pulled out through the flap opening in the front wall 3 if necessary.
  • the connection between the combustion chamber 1 and the space 12 is designed according to the invention as a flue gas discharge opening 22 located at the bottom of the combustion chamber.
  • this is preferably formed as a recess in the open end 23 of the combustion chamber casing 2 closest to the front wall 3, but in another embodiment of the flue gas ducts one or more flue gas ducts can instead be drawn from the combustion chamber inside the boiler, on the Rear wall 7 or between this and the position of the opening 22 shown in FIG. 1 are executed.
  • each partition is preferably designed as an angle iron, which is connected with its one flange to the combustion chamber jacket, expediently welded, while the other flange follows the adjacent radial flange of one of the profile elements.
  • two such partitions 24 and 24 are provided, which extend along the lower boiler part and are drawn past the ends of the profile elements 21 to the front end 23 of the combustion chamber shell, ie to the sheet metal cover 4 of the front wall, as a result of which the these two partition walls formed channel A is separated both diagonally upwards to the sides and towards the front.
  • two upper partition walls 24 3 and 24 4 are provided, which are shorter than the first two partition walls and only extend to the ends of the profile elements 21, whereby a channel 25 is formed between each of these partition wall ends and the part of the sheet metal cover 4 in front of it . Together with the free spaces on both sides thereof around the combustion chamber jacket, these channels form a front deflection chamber 27 which comprises 2/3 of the jacket circumference.
  • the last two partition walls 24 3 and 24 4 are each connected to a radially directed plate 27 at the rear, so that the radially outer part 28 of each plate forms an extension of the partition wall to the rear.
  • the radially inner sheet metal parts 29 are connected at their edges to the back of the rear wall 7 of the combustion chamber and to one another, expediently to form a V, the tip of which is located at the height of the axis line of the combustion chamber.
  • the flue gas discharge 19 is arranged in the form of a pipe socket which is alternatively directed upwards, while a rear deflection chamber 31 for the flue gases is formed under the metal sheets.
  • this opening - as can best be seen in FIG. 2 - is given an extent in the circumferential direction which corresponds to that of the channel A, ie the side edges 32 of the opening can face the mutually facing edges 33 of the partitions 24 1 and 24 2 coincide.
  • Path 36 can take through the recesses 33 and between the profile elements 21 A in the channel A.
  • the more uniform temperature distribution in the boiler according to the invention is also facilitated in that the flue gases, after they have given off heat in channel A and continue to flow in channels B and B 2 of the two-part, second train, now have a lower temperature which corresponds to the heat requirement in the Side parts of the boiler is adapted, and that the flue gases, when they are at their lowest temperature, can flow in the third draft before the flue gas outlet along the uppermost part of the water reservoir, where the boiler water to be discharged through the riser 40 is naturally the hottest, and where than the heat requirement is the lowest.
  • the series connection of the flue gas channels ABC means that the problem of condensation in the lower parts of the flue gas space 12 is eliminated and that the boiler can therefore be operated at a temperature as low as 40 ° C. without risking corrosion in these parts .
  • the lower boiler temperature in turn leads to lower radiation losses to the environment.
  • the long flow path in the series-connected ducts means that the flue gas heat can be used to the maximum, which is reflected in the low flue gas temperature at the chimney and an efficiency of up to 96%.
  • the flue gas temperature may be below the lower limit critical for the chimney, due to the operating conditions, at which condensation occurs.
  • this disadvantage can be eliminated by the arrangement of the end wall 8 releasably inserted into the combustion chamber 1. If this wall is moved to the rear, that is closer to the fixed rear wall 7, or is removed so that the effective length of the combustion chamber becomes longer, flue gases from the burner 6, before they are deflected against the discharge opening 22, can produce more heat than before Release the upper rear part of the casing 2 to the colder gases which move to the chimney on the outside of the casing in the upper flue gas ducts. The latter flue gases are thus reheated to a higher temperature than if the wall 8 is inserted into the combustion chamber or is moved forward, since the part of the combustion chamber behind it cannot be reached by the flame and the flue gases by the burner.
  • the angle iron 24 1 - 4 which in the illustrated embodiment in the form of partitions divide the space 12 between the combustion chamber and the water reservoir into the four channels, can alternatively consist of the flanges on the four U-profiles 21, which are longitudinal in the embodiment extend the angle iron, the two lower U-profile flanges, which are to replace the angle iron 24 1 and 24 2 , must have the same length as the latter in order to To prevent flue gases from the combustion chamber from upstream to flow to the side channels B1 and B2. In order to avoid leakage between the channels, care must be taken to ensure that the U-profiles mentioned are as close as possible to the outside of the combustion chamber shell 2 and that a seal is also obtained on the front edge of the two sheets 28 provided at the rear.
  • the two channels B 1 and B 2 preferably enclose a circumferential angle with one another which has the same size as the circumferential angle of each of the remaining channels.
  • Channels A and C must therefore include an angle of 120 ° and each side channel an angle of 60 °.
  • the duct system comprises a duct C 'between the partition walls 41 and 41 3 which is connected in series with the duct B' and through which the flue gases flow again in the former direction along the shells 2 and 10, after which they go to the chimney.
  • the channels are to be designed with a circumferential angle of 120 ° so that the flow resistance in each channel is the same.
  • the invention is not limited to the arrangement shown here with four or three channels, which form three series-connected trains, but the number of channels and trains can also be larger. It is also possible to implement the invention and to take advantage of it by providing only two series ducts which cover the lower and upper part of the space between the combustion chamber and the water jacket.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Incineration Of Waste (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Oscillators With Electromechanical Resonators (AREA)

Claims (7)

1. Chaudière comportant une chambre de combustion (1) possédant une section transversale circulaire et limitée par une première enveloppe tubulaire (2) qui s'étend depuis la paroi avant (3) de la chaudière jusqu'à une paroi arrière (7) tournée vers la paroi avant et limitant la longueur de la chambre de combustion, un réservoir d'eau (10), qui entoure la chambre de combustion au niveau de son pourtour et est limité, vers l'intérieur, par une seconde enveloppe tubulaire (11) limitant, conjointement avec la première enveloppe, un espace (12) possédant une section transversale annulaire et relié à la chambre de combustion et à un conduit (19) d'évacuation des gaz de fumées, afin que les gaz de fumées produits dans la chambre de combustion traversent ledit espace et que de la chaleur soit délivrée au réservoir d'eau, avant que les gaz de fumées s'échappent de la chaudière par le conduit d'évacuation des gaz de fumées, les gaz de fumées circulant dans ledit espace le long de chicanes qui comportent de préférence des éléments profilés longitudinaux (21) possédant une section transversale en forme de U et répartis en cercle uniformément autour de la chambre de combustion et reliés à l'enveloppe (11) du réservoir d'eau, de manière à augmenter la surface de cette enveloppe, recevant la chaleur produite par les gaz de fumées, caractérisée en ce que ledit espace (12) est subdivisé par des cloisons de séparation (24) qui s'étendent dans la direction transversale depuis l'enveloppe (2) de la chambre de combustion jusqu'à l'enveloppe (11) du réservoir d'eau et s'étendent dans la direction longitudinale depuis une extrémité de l'espace jusqu'à son autre extrémité en formant, entre la chambre de combustion (1) et le réservoir d'eau (10), des canaux longitudinaux d'écoulement (A, B, C), qui sont séparés par les cloisons de séparation (24) et contiennent lesdites chicanes, de préférence sous la forme d'un groupe, disposé dans chaque canal, d'éléments profilés (21), en ce que les canaux sont reliés entre eux en série en s'étendant à partir d'une ouverture (22) de dérivation de sortie des gaz de fumées, située à la partie inférieure de la chambre de combustion, et en débouchant dans le conduit (19) d'évacuation des gaz de fumées, auquel cas les gaz de fumées chauds arrivant sde la chambre de combustion (1) délivrent, lors d'un premier parcours (dans A), exclusivement de la chaleur à une partie inférieure du réservoir d'eau (10), à la suite de quoi les gaz de fumées refroidis de cette manière délivrent, lors de parcours suivants (dans B - C), une quantité de chaleur supplémentaire aux autres éléments du réservoir d'eau.
2. Chaudière selon la revendication 1, caractérisée en ce que les canaux (A, B, C) dirigent les gaz de fumées arrivant depuis la chambre de combustion (1) en empruntant l'ouverture (22) de dérivation de sortie, tout d'abord vers l'arrière à proximité de la paroi arrière (7) et, à partir de là, dans la direction opposée vers la paroi avant (3) et ensuite finalement à nouveau vers l'arrière jusqu'à un espace (30) se raccordant au conduit (19) d'évacuation des gaz de fumées.
3. Chaudière suivant la revendication 1 ou 2, caractérisée par le fait que l'espace (12) est subdivisé en quatre canaux d'écoulement, à savoir un canal inférieur (A) pour le premier parcours, qui englobe de préférence 1/3 de la surface en coupe transversale de l'espace, deux canaux latéraux (B), qui sont situés de chaque côté de la chambre de combustion (1) au-dessus du canal inférieur (A) et se raccordent chacun au canal inférieur par l'intermédiaire d'une première chambre de renvoi (26), au niveau de l'extrémité (7) de la chambre de combustion, qui est la plus éloignée de l'ouverture (20) de la conduite d'évacuation, de manière à diriger les gaz de fumées sur un second parcours comportant deux éléments en direction de l'autre extrémité (23) de la chambre de combustion, où se trouve prévue une seconde chambre de renvoi (31), chaque canal latéral (B) occupant de préférence 1/6-ème de la surface en coupe transversale de l'espace, ainsi qu'un canal supérieur (C) disposé entre et au-dessus des deux canaux latéraux (B) et est raccordé à ces derniers au moyen de la seconde chambre de renvoi (31), de manière à diriger les gaz de fumées le long d'un troisième parcours en les renvoyant à ladite première extrémité (7) de la chambre de combustion, à partir de laquelle ils s'évacuent oar le conduit (191 d'évacuation des gaz de fumées, le canal supérieur (C) englobant de préférence le 1/3 restant de la surface en coupe transversale de l'espace.
4. Chaudière suivant la revendication 2 ou 3, caractérisée par le fait que l'ouverture (22) de dérivation de sortie est disposée dans la partie de l'enveloppe (2) de la chambre de combustion, qui est la plus proche de la paroi avant (3), de sorte que les gaz de fumées, qui sont produits dans la chambre de combustion sont contraints, avant d'être évacués de cette chambre, de revenir vers la paroi avant circulant le long de la face intérieure de l'enveloppe de la chambre de combustion et de délivrer une chaleur aux gaz de fumées circulant sur la face extérieure, et en ce qu'il est prévu une paroi frontale (8) pouvant être insérée en avant de la paroi arrière (7) dans la chambre de combustion (1) ou pouvant en être retirée de manière à réduire ou accroître la température des gaz de fumées dans le dernier parcours, grâce à un raccourcissement ou un allongement de la face intérieure de la chambre de combustion (1), balayée par les gaz de fumées.
5. Chaudière suivant l'une des revendications 1 - 4, caractérisée en ce que l'ouverture (22) de dérivation de sortie est formée par un évidement prévu dans une extrémité (23) de l'enveloppe (2) de la chambre de combustion et dont la largeur est sensiblement égale à la distance entre les deux cloisons de séparation (241, z) qui limitent le canal (A) raccordé à l'ouverture de dérivation de sortie et qui sont voisines de ladite extrémité de l'enveloppe de la chambre de combustion.
6. Chaudière suivant l'une des revendications 1 - 4, caractérisée en ce que les cloisons de séparation (243, 4), qui limitent le canal (C) dans lequel les gaz de fumées pénètrent lors du dernier parcours en direction du conduit (19) d'évacuation des gaz de fumées, se terminent, dans la direction opposée, à une distance telle de l'extrémité (23) de l'enveloppe de la chambre de combustion que l'on obtient en cet endroit la formation d'un passage libre (25) à travers lequel les gaz de fumées sont renvoyés à partir du parcours précédent et sont introduits dans le canal.
7. Chaudière selon la revendication 2 ou 3, caractérisée en ce que ledit espace (30), qui se raccorde au conduit (19) d'évacuation des gaz de fumées, est disposé en arrière de la paroi arrière (7) et est limité, vers le bas, par deux tôles radiales (27), dont les parties (28), extérieures du point de vue radial, se prolongent par les deux cloisons de séparation (24g 4), entre lesquelles les gaz de fumées sont dirigés vers l'arrière en direction de l'espace (30), tandis que les parties (29), intérieures du point de vue radial, des tôles sont reliées entre elles en forme de V et sont fixées de chant à la partie arrière (7).
EP19850850114 1984-03-30 1985-03-29 Chaudière Expired EP0166703B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT85850114T ATE37441T1 (de) 1984-03-30 1985-03-29 Heizkessel.
DK146485A DK160584B (da) 1984-03-30 1985-04-01 Varmekedel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8401755A SE441778B (sv) 1984-03-30 1984-03-30 Vermepanna med ett cylindriskt vattenmagasin
SE8401755 1984-03-30

Publications (3)

Publication Number Publication Date
EP0166703A2 EP0166703A2 (fr) 1986-01-02
EP0166703A3 EP0166703A3 (en) 1986-06-11
EP0166703B1 true EP0166703B1 (fr) 1988-09-21

Family

ID=20355357

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850850114 Expired EP0166703B1 (fr) 1984-03-30 1985-03-29 Chaudière

Country Status (6)

Country Link
EP (1) EP0166703B1 (fr)
DE (2) DE3508936A1 (fr)
DK (1) DK140785A (fr)
FR (1) FR2562215A1 (fr)
NO (2) NO851300L (fr)
SE (1) SE441778B (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3546265A1 (de) * 1985-12-28 1987-07-02 Viessmann Hans Heizungskessel
DE3933680A1 (de) * 1989-10-09 1991-04-11 Werner Mueller Heizkessel fuer hausheizungen
DE3938090C1 (fr) * 1989-11-16 1991-04-18 Viessmann Werke Gmbh & Co, 3559 Allendorf, De
EP0591563B1 (fr) * 1991-04-04 1997-07-09 CAPITO GmbH & Co Verwaltungsgesellschaft Chaudière
SE500326C2 (sv) * 1992-11-18 1994-06-06 Ctc Parca Ab Värmepanna med rökgasåterföring samt brännkammarenhet för sådan värmepanna
DE4418495C1 (de) * 1994-05-27 1995-05-11 Viessmann Werke Kg Dreizug-Heizkessel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1316206A (fr) * 1962-02-26 1963-01-25 Webasto Werk Baier Kg W Radiateur pour chauffage à circulation de combustible
SE341060B (fr) * 1967-06-17 1971-12-13 Belleli & C S A S
DE2613186C3 (de) * 1976-03-27 1979-03-22 Hans 3559 Battenberg Viessmann Heizungskessel für flussige oder gasformige Brennstoffe
DE2852135A1 (de) * 1978-12-01 1980-06-12 Alfred Eisenschink Heizkessel-vorrichtung

Also Published As

Publication number Publication date
DE3565173D1 (en) 1988-10-27
EP0166703A3 (en) 1986-06-11
NO851299L (no) 1985-10-01
DK140785A (da) 1985-10-01
DE3508936A1 (de) 1985-10-10
EP0166703A2 (fr) 1986-01-02
SE8401755L (fr) 1985-10-01
DK140785D0 (da) 1985-03-28
SE8401755D0 (sv) 1984-03-30
NO851300L (no) 1985-10-01
SE441778B (sv) 1985-11-04
FR2562215A1 (fr) 1985-10-04

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