US3908758A - Heating or cooling radiator - Google Patents

Heating or cooling radiator Download PDF

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Publication number
US3908758A
US3908758A US311403A US31140372A US3908758A US 3908758 A US3908758 A US 3908758A US 311403 A US311403 A US 311403A US 31140372 A US31140372 A US 31140372A US 3908758 A US3908758 A US 3908758A
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US
United States
Prior art keywords
manifold
radiator
pipe
length
members
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 - Lifetime
Application number
US311403A
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English (en)
Inventor
Erich Armonies
Horst Keiner
Herbert Steup
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.)
MENK APPARATEBAU GmbH
Original Assignee
MENK APPARATEBAU GmbH
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
Priority claimed from DE19712160865 external-priority patent/DE2160865C3/de
Priority claimed from DE19722242159 external-priority patent/DE2242159C3/de
Application filed by MENK APPARATEBAU GmbH filed Critical MENK APPARATEBAU GmbH
Application granted granted Critical
Publication of US3908758A publication Critical patent/US3908758A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F27/00—Details of transformers or inductances, in general
    • H01F27/08—Cooling; Ventilating
    • H01F27/10—Liquid cooling
    • H01F27/12—Oil cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/088—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal for domestic or space-heating systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • F28F9/268—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators by permanent joints, e.g. by welding
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
    • Y10S165/471—Plural parallel conduits joined by manifold
    • Y10S165/483—Flow deflecting/retarding means in header for even distribution of fluid to plural tubes

Definitions

  • ABSTRACT A radiator with upper and lower manifolds and a series of radiator members extending therebetween, where at least the upper manifold chamber has in a first length portion an upper, flow channel through which the incoming fluid initially bypasses a first group of radiator member throats and reaches the latter after reversal, via a lower flow channel.
  • the present invention concerns a heating or cooling radiator, more particularly for cooling the oil of oilcooled transformers.
  • Radiators of this type comprise a predetermined number of radiator members arranged in parallel and provided at their upper and lower ends with throat portions serving for the connection of the members to each other and to the radiator manifolds which lead to the transformer vessel and the main flow system.
  • the compact manifold chambers thereby formed at the upper and lower ends of the radiator serve to distribute the heat transfer medium to the individual radiator members and to form a collecting outlet.
  • the manifold chambers are provided in part by the half-shells forming the radiator member throat portions which are formed with a semi-circular recess at the top and bottom. After the half-shells and members are joined to gether to form a radiator, a continuous half-pipegis mounted on the resultant throat profile.
  • the continuous half-pipe serves on the one hand for the closing of the radiator on the outside and, on the other hand, to provide mechanical strength.
  • a radiator for oil-filled transformer vessels wherein the throat portions are stamped and shaped from the body of the radiator half-shells as closed collars so that, when the half shells are joined together, they define closed members which are open only on the side where they adjoin other members.
  • the throat portions are stamped and shaped from the body of the radiator half-shells as closed collars so that, when the half shells are joined together, they define closed members which are open only on the side where they adjoin other members.
  • the radiator of the present invention is characterized by the feature that the upper and/or lower manifold chamber is provided with flow bypass means for the heating or cooling medium and is constructed and arranged to operate so as to distribute the medium to the radiator members in such a way that the temperature at the throats of the radiator members is the same or at least approximately the same over the entire length of the intake manifold.
  • the manifold may be formed by a series of upper member openings of elongated oval throat shape, which openings are closed to the outside by means'of a pipe having a diameter corresponding to the opening width of the throats, the pipe communicating with the manifold chamber in the region of the outer members remote from the manifold inlet through a longitudinal cut-away.
  • the entering coolant arrives in a compact flow in the center area of the radiator manifold, from where, under the suction exerted by the transformer vessel, it flows in reverse into the elongated oval space and, due to the deflection by, the upper manifold pipe, is distributed substantially uncooled to the individual members of the radiator.
  • a particularly uniform head temperature is achieved at the inlet into the radiator members which results in a more even surface heat load.
  • an improvement of the cooling efficiency of more than 10 percent, as compared with conventional radiators is obtained.
  • the same effect is obtained with a radiator inside whose manifold chamber is a continuous intake pipe having an opening into the chamber in the center of the manifold length.
  • the stepped members of the radiator are provided with elongate oval throats for forming the manifold chamber, and the resultant stepped manifold chamber is closed by means of a flat, arched, or ridged U-shaped profile, the side legs of the profile having a length approximately equal to the vertical distance between the edge line of the radiator throats and the top line of the members.
  • a stepped radiator designed in this manner has a much smaller lateral overhang, while retaining the necessary full flow cross-section for the coolant in the upper manifold, compared with conventional stepped radiators, so that the stepped portion of the radiator can begin further away, while obtaining an equivalent cooling surface.
  • the resultant improvement in the cooling efficiency makes it possible to construct smaller units or to choose a higher transformer power output with the same size vessel, a feature which, particularly in the case of series installations on railroad equipment, results in a considerable reduction in the number of required units for such a series installation for the same total power.
  • the upper or lower manifold chamber may be formed by a single pipe, or such a continuous manifold pipe may be provided inside an enlarged manifold chamber, said pipe connecting the radiator to the cooling vessel or heating system and having one or more openings in the region of each radiator member throat, the opening cross-section increasing progressively from the inlet end to the closed end of the manifold.
  • the openings are preferably formed on both sides of the inner manifold pipe, thus facilitating the transfer of any air bubbles from the radiator to the manifold pipe and the discharge thereof.
  • the openings in the pipe may all have an identical cross-section, and a longitudinal sector of tubing with a slanting edge may be inserted in the pipe, whereby the desired progression in the crosssection of the openings can be produced with only a few standardized parts.
  • the desired crosssectional progression it is then only necessary to insert the standardized pipe section to a greater or lesser depth into the manifold pipe and to cut it, if necessary, in the correct position, In this way, the necessary changes in cross-sectional progression may be readily adapted to change in the number of radiator members from radiator to radiator.
  • FIG. 1 is a side view of a radiator embodying the invention
  • FIG. 2 is an end elevation of the radiator of FIG. 1 or FIG. 9, as seen from the right-hand end;
  • FIG. 3 is a longitudinal section through a manifold pipe for a radiator of the invention.
  • FIGS. 4 and 5 are similar longitudinal sections through two modified manifold pipes
  • FIGS. 6, 7 and 8 are sections taken along the lines A B, C D, and E F, of FIGS. 5, 4, and 3, respectively;
  • FIG. 9 is a side view of a radiator of the invention, utilizing a manifold pipe like the one shown in FIG. 3;
  • FIG. 10 is a side view of another radiator embodying the invention.
  • FIGS. 11 and 12 are plan views of two modifications of the radiator manifold shown in FIG. 10;
  • FIG. 13 is a partial longitudinal section through a stepped radiator
  • FIG. 14 is a cross section taken along line A A of FIG. 13.
  • the individual radiator members are formed by joining together radiator half-shells la and lb.
  • the half shells and consequently the radiator members each have throat portions 2 formed at their ends with, in the case of the embodiment shown, an elongated oval cut-out 3 (FIG. 2) which defines the cross-sectional outline of the manifold chamber to the extent that the latter is defined by the radiator members.
  • the manifold chamber is closed externally by the upper portion of the pipe 4.
  • the free end 4a of the manifold pipe is welded to the connecting pipe socket of the main supply system, i.e., in the case of a heating radiator, to the heating medium supply line, or, in the case of a cooling radiator for a transformer vessel, to the vessel connecting sockets.
  • the manifold chamber serving to distribute the heating medium or coolant to the radiator members is defined between the member throats 3 and the half-pipe 4.
  • Pos itive flow guides are provided in the upper part of the manifold chamber for directing the heating or cooling medium to the radiator members in such a manner that the radiator temperature is the same or at least approximately the same over the entire length of the radiator manifold.
  • a continuous manifold pipe is provided in the upper portion of the manifold chamber 3, the latter being enlarged for an elongated oval cross-section so that the pipe 4 can be a continuous pipe, serving as the external chamber limitation. Facing each radiator member 1,
  • the manifold pipe 4 may have openings 50 through 51' (see FIG. 4) which openings increase in cross-section from the inlet end 4a to the opposite end 4b.
  • Two openings 5a are preferably provided in each member plane, as shown in FIG. 7, for example, so as to enable the pipe to communicate with the radiator throat chamber directly below the horizontal junction line with the external manifold closure, so as to allow rising air bubbles in the radiator to readily pass into the manifold pipe and to be discharged.
  • the openings are stamped out in the manifold pipe in the proposed progression of sizes.
  • the openings may also be formed in the manner shown in FIGS. 5 and 6, so that the pipe 4 itself is provided with openings 60, 6d 61', of identical cross-section, but the openings are partially covered by the insertion of a baffle 7 of arcuate crosssection with slanting edges to form openings of progressively increasing cross-section.
  • the manifold pipes may be standardized for radiators of various types and may have any number of members, and the graduation of the openings may be obtained by inserting a tube sector which is preferably stamped and shaped in one standardized size, sliding it into place and cutting-off projecting portions.
  • the manufacture of the novel radiators is greatly simplified in this manner. Due to the downward extension of the manifold chamber, which is longitudinally closed by a closure plate 8 (FIG. 1), the member throats are also communicating with each other. However, the members may also be closed-off from each other, as in the case of an embodiment where the radiator does not have a downwardly extended manifold chamber, in which case the member throats communicate with each other only through the openings in the manifold pipe and possibly through the lower manifold chamber.
  • FIGS. 3, 8, and 9 A preferred embodiment is shown in FIGS. 3, 8, and 9, which embodiment has its manifold chamber 9 (FIG. 9) partially defined by downwardly enlarged throats and the remaining upper manifold chamber portion is closed by means of a half-sectioned pipe 10 having a diameter corresponding to the transverse width of the member throats.
  • This design of the radiator throat junctions and of the manifold pipe while not complicating the manufacture of the radiator, affords a considerable reinforcement of the radiator structure.
  • it produces a more even distribution of the heat to be transferred to the cooling surface of the radiator, because the cooling or heating medium fed into the manifold chamber portion 9b reaches the radiator members approximately in the manner indicated by the arrows in FIG. 1, under the action of the suction exerted by the transformer vessel, in a flow which is guided by the manifold inlet pipe for an even distribution.
  • FIGS. 10 and 12 wherein, on the basis of downwardly extended or unextended (as shown) manifold chamber approximately at the level of the upper edge 11 of the radiator, a continuous baffle plate 12 is provided approximately in the center area of a comparatively large inlet opening 15 see FIG. 12, which plate divides the manifold chamber into an upper closed cooling medium inlet channel 13 and the lower chamber 14 connecting the individual radiator members together but closed on the outside.
  • a continuous baffle plate 12 is provided approximately in the center area of a comparatively large inlet opening 15 see FIG. 12, which plate divides the manifold chamber into an upper closed cooling medium inlet channel 13 and the lower chamber 14 connecting the individual radiator members together but closed on the outside.
  • baffle plate 12 (FIG. I l) is provided in the region of each radiator member with open ings 160 through 16f, the openings having a progressively increasing cross-section from the inlet end of the radiator, at 16a to the closed end of the radiator at 16f.
  • the step-free members are indicated by reference numeral 17 and the regularly stepped members by reference numeral 21.
  • the radiator members are assembled from half shells at and b and are provided at the upper and lower ends with throat recesses 22 open at the top and arranged opposite each other.
  • Thethroat recesses are formed by cut-outs at the top having an elongate oval form and are closed in the region of the step-free members by means of a manifold pipe 23 having a cut-away at its downstream end with a diameter corresponding to the throat width.
  • the manifold chamber is closed by means of a U-shaped profile 24 (see FIG. 2), the side legs 24a of which have a length approximately equal to the inner spacing 11' between the top line 25 of the throat edges and the top line 26 of the members.
  • the space gain corresponds approximately to the width of one radiator member so that, relative to conventional stepped radiators, the beginning of the stepping can be shifted outwardly by that one radiator member with a corresponding considerable gain in effective cooling surface area.
  • a radiator assembly for the circulation therethrough of a heat transfer fluid such as the cooling oil of a transformer for example, the assembly comprisa generally horizontally oriented inlet manifold having a closed end on one side and an inlet opening on its opposite side connectable to a fluid circulating system;
  • a generally similarly oriented outlet manifold spaced a distance below the inlet manifold and having likewise a closed end on one side and an outlet opening on the opposite side connectable to said fluid circulating system;
  • each radiator member including upper and lower openings for communication with both manifolds; and wherein at least the inlet manifold has its length subdivided into first and second length portions, the latter encompassing corresponding first and second groups of upper radiator member openings, respectively;
  • the first manifold length portion has its flow section longitudinally subdivided into an upper flow channel leading from the inlet opening of the manifold directly to its second length portion, and a lower flow channel leading from the second manifold length portion to said first group of radiator member openings, thereby forcing the entire incoming fluid flow to initially bypass the first group of radiator member openings, the latter being reachable only through reversal of a portion of said flow, via the lower flow channel;
  • At least said inlet manifold is constituted in its upper portion by a manifold pipe and in its lower portion by adjoining enlarged throat portions at the upper ends of the radiator members.
  • said manifold pipe has a full circumference in said first length portion of the manifold, thereby defining said upper flow channel, but has at least a major portion of the lower half of its circumference missing in said second manifold length portion;
  • the throat portions of the radiator members having adjoining collars, upwardly curved in a cradle shaped profile and connected to the manifold pipe at both ends of the cradle profile;
  • said axially adjoining collars define the lower flow channel in said first length portion of the manifold in cooperation with the lower half of the manifold pipe.
  • the manifold pipe is a round pipe, said missing lower circumferential portion being the lower half of the pipe;
  • the width of said cradle profile defined by the radiator member throat portions is substantially equal to the diameter of the manifold pipe.
  • the intake manifold has an angled longitudinal axis, its first length portion near its inlet opening being oriented substantially horizontally and its second length portion being slanting downwardly away from said first length portion;
  • the radiator members of said first group are of uniform length and the radiator members of said second group are progressively shorter so as to present a stepped line of collar joints with the slanting manifold length portion.
  • the first and second groups of radiator members are substantially equal in numbers.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Transformer Cooling (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US311403A 1971-12-08 1972-12-01 Heating or cooling radiator Expired - Lifetime US3908758A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19712160865 DE2160865C3 (de) 1971-12-08 Radiator zur Kühlung des Öls ölgefüllter Transformatorenkessel
DE19722242159 DE2242159C3 (de) 1972-08-26 1972-08-26 Radiator zur Kühlung des Öls ölgekühlter Transformatoren

Publications (1)

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US3908758A true US3908758A (en) 1975-09-30

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ID=25762144

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US311403A Expired - Lifetime US3908758A (en) 1971-12-08 1972-12-01 Heating or cooling radiator

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US (1) US3908758A (index.php)
BE (1) BE792396A (index.php)
CH (1) CH554063A (index.php)
CS (1) CS166663B2 (index.php)
DD (1) DD101751A5 (index.php)
FR (1) FR2162360B1 (index.php)
GB (1) GB1412748A (index.php)
IT (1) IT975759B (index.php)
NL (1) NL7214545A (index.php)
PL (1) PL78965B1 (index.php)
SE (1) SE383059B (index.php)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4227570A (en) * 1979-10-01 1980-10-14 Caterpillar Tractor Co. Heat exchange structure
WO1981001327A1 (en) * 1979-10-01 1981-05-14 D Crews Heat exchange structure
US4287945A (en) * 1979-07-03 1981-09-08 The A.P.V. Company Limited Plate heat exchanger
US4589480A (en) * 1981-12-10 1986-05-20 Alfa-Laval Ab Plate heat exchanger
US6179051B1 (en) * 1997-12-24 2001-01-30 Delaware Capital Formation, Inc. Distributor for plate heat exchangers
US6484797B2 (en) * 2000-10-20 2002-11-26 Mitsubishi Heavy Industries, Ltd. Laminated type heat exchanger
US20030155109A1 (en) * 2002-02-19 2003-08-21 Masaaki Kawakubo Heat exchanger
US7000690B2 (en) * 2001-10-06 2006-02-21 Behr Gmbh & Co. Heat exchanger for a motor vehicle
WO2006098677A1 (en) * 2005-03-15 2006-09-21 Scania Cv Ab (Publ) Cooler device
US20080135398A1 (en) * 2005-01-06 2008-06-12 Takeshi Azami Method For Manufacturing Carbonaceous Material
US20130199288A1 (en) * 2012-02-02 2013-08-08 Visteon Global Technologies, Inc. Fluid flow distribution device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4303124A (en) * 1979-06-04 1981-12-01 The A.P.V. Company Limited Plate heat exchanger
DE4327974C2 (de) * 1993-08-19 1996-11-07 Kermi Gmbh Heizkörper, insbesondere Röhrenheizkörper, sowie Verfahren und Vorrichtung zur Herstellung eines Heizkörpers
CN115164911A (zh) * 2021-02-03 2022-10-11 西华大学 基于图像识别的高精准度立交桥快速导航方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1208022A (en) * 1914-09-21 1916-12-12 Mccord Mfg Company Radiator head-sheet.
US2001663A (en) * 1932-10-17 1935-05-14 Erie City Iron Works Heater
US3153447A (en) * 1963-09-11 1964-10-20 Tranter Mfg Inc Oil cooling heat exchange unit
US3196943A (en) * 1963-07-18 1965-07-27 Carrier Corp Distributor for heat exchange apparatus
US3670812A (en) * 1969-04-10 1972-06-20 Ass Eng Ltd Heat exchangers

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR418331A (fr) * 1910-07-18 1910-12-06 Karl Schroeder Radiateur pour le chauffage des locaux
GB984910A (en) * 1963-01-09 1965-03-03 Hartwig Georg Binder Improvements in or relating to the manufacture of sectional heat-exchangers
FR1394501A (fr) * 1964-05-08 1965-04-02 Westinghouse Electric Corp Appareillage électrique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1208022A (en) * 1914-09-21 1916-12-12 Mccord Mfg Company Radiator head-sheet.
US2001663A (en) * 1932-10-17 1935-05-14 Erie City Iron Works Heater
US3196943A (en) * 1963-07-18 1965-07-27 Carrier Corp Distributor for heat exchange apparatus
US3153447A (en) * 1963-09-11 1964-10-20 Tranter Mfg Inc Oil cooling heat exchange unit
US3670812A (en) * 1969-04-10 1972-06-20 Ass Eng Ltd Heat exchangers

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4287945A (en) * 1979-07-03 1981-09-08 The A.P.V. Company Limited Plate heat exchanger
US4227570A (en) * 1979-10-01 1980-10-14 Caterpillar Tractor Co. Heat exchange structure
WO1981001327A1 (en) * 1979-10-01 1981-05-14 D Crews Heat exchange structure
US4589480A (en) * 1981-12-10 1986-05-20 Alfa-Laval Ab Plate heat exchanger
US6179051B1 (en) * 1997-12-24 2001-01-30 Delaware Capital Formation, Inc. Distributor for plate heat exchangers
US6484797B2 (en) * 2000-10-20 2002-11-26 Mitsubishi Heavy Industries, Ltd. Laminated type heat exchanger
US20060070729A1 (en) * 2001-10-06 2006-04-06 Behr Gmbh & Co. Heat exchanger for a motor vehicle
US7000690B2 (en) * 2001-10-06 2006-02-21 Behr Gmbh & Co. Heat exchanger for a motor vehicle
US7234515B2 (en) 2001-10-06 2007-06-26 Behr Gmbh & Co. Heat exchanger for a motor vehicle
US20030155109A1 (en) * 2002-02-19 2003-08-21 Masaaki Kawakubo Heat exchanger
US7044208B2 (en) * 2002-02-19 2006-05-16 Denso Corporation Heat exchanger
US20060151159A1 (en) * 2002-02-19 2006-07-13 Masaaki Kawakubo Heat exchanger
US7604044B2 (en) 2002-02-19 2009-10-20 Denso Corporation Heat exchanger
US20080135398A1 (en) * 2005-01-06 2008-06-12 Takeshi Azami Method For Manufacturing Carbonaceous Material
WO2006098677A1 (en) * 2005-03-15 2006-09-21 Scania Cv Ab (Publ) Cooler device
US7926558B2 (en) 2005-03-15 2011-04-19 Scania Cv Ab Cooler device
US20130199288A1 (en) * 2012-02-02 2013-08-08 Visteon Global Technologies, Inc. Fluid flow distribution device

Also Published As

Publication number Publication date
FR2162360A1 (index.php) 1973-07-20
NL7214545A (index.php) 1973-06-13
GB1412748A (en) 1975-11-05
CS166663B2 (index.php) 1976-03-29
CH554063A (de) 1974-09-13
IT975759B (it) 1974-08-10
BE792396A (fr) 1973-03-30
FR2162360B1 (index.php) 1976-01-30
SE383059B (sv) 1976-02-23
PL78965B1 (index.php) 1975-06-30
DD101751A5 (index.php) 1973-11-12

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