DK147381B - INJECTION VALVE FOR STAMP COMBUSTION ENGINES - Google Patents

INJECTION VALVE FOR STAMP COMBUSTION ENGINES Download PDF

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Publication number
DK147381B
DK147381B DK368478AA DK368478A DK147381B DK 147381 B DK147381 B DK 147381B DK 368478A A DK368478A A DK 368478AA DK 368478 A DK368478 A DK 368478A DK 147381 B DK147381 B DK 147381B
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DK
Denmark
Prior art keywords
fuel
valve
nozzle bores
needle
injection valve
Prior art date
Application number
DK368478AA
Other languages
Danish (da)
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DK368478A (en
DK147381C (en
Inventor
Peter Fuchs
Original Assignee
Sulzer Ag
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Publication of DK368478A publication Critical patent/DK368478A/en
Publication of DK147381B publication Critical patent/DK147381B/en
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Publication of DK147381C publication Critical patent/DK147381C/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/44—Valves, e.g. injectors, with valve bodies arranged side-by-side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

i 147381 5 Opfindelsen angår en indsprøjtnings'ventil til stempelforbrændingsmotorer og af den i krav l’s indledning angivne art.The invention relates to an injection valve for piston combustion engines and of the kind specified in the preamble of claim 1.

Fra tysk brugsmønster nr. 7.025.384 kendes en ind-10 sprøjtningsventil af den i krav l’s indledning angivne art, hvor den indre ventilnål styrer den neder-ste række dyseboringer, og hvor den cylindriske, yderste ventilnål styrer begge rækker dyseboringer. Under drift hæver brændstoftrykket til at begynde med den 15 inderste af de to ventilnåle fra sit ventilsæde, så brændstof gennem den hertil hørende række af dyseboringer sprøjtes ind i cylinderen. Når brændstoftrykket ikke vokser mere, vender den hævede ventilnål tilbage til sit ventilsæde med faldende brændstoftryk. Ind-20 sprøjtningstakten er til ende, hvis der er tale om delbelastning af motoren. Når motoren skal arbejde under fuld belastning åbnes først, som foran nævnt, den inderste ventilnål, men når brændstoftrykket øges yderligere, hæves også den yderste ventilnål, så der 25 også sprøjtes brændstof ud gennem den øverste række dyseboringer. Dvs at der under en del af indsprøjtningstakten sprøjtes brændstof gennem alle dyseboringer, men ved aftagende tryk lukker den yderste nål først, og lidt senere lukker den inderste.German application pattern No. 7,025,384 discloses an injection valve of the kind specified in the preamble of claim 1, wherein the inner valve needle controls the lower row of nozzle bores and where the cylindrical outer valve needle controls both rows of nozzle bores. In operation, the fuel pressure initially raises the 15 innermost of the two valve pins from its valve seat so that fuel is injected into the cylinder through the associated series of nozzle bores. When the fuel pressure no longer grows, the raised valve needle returns to its valve seat with decreasing fuel pressure. The injection rate is at an end in case of partial load on the engine. When operating the engine under full load, the inner valve needle is first opened, but as the fuel pressure increases further, the outer valve needle is also raised, so that fuel is also sprayed out through the upper row of nozzle bores. That is, during part of the injection rate, fuel is sprayed through all nozzle bores, but at decreasing pressure the outer needle closes first and a little later the inner one closes.

3030

En sådan konstruktion har flere ulemper. Yed fuldlast-drift af motoren vil den kegleformede udbredelse af forstøvet brændstof fra dyseboringerne i de to rækker krydse eller skære hinanden, og dette medfører ufuld- 2 147381 1 stændig. forbrænding. De sammenstødende, brændstofkegler medfører en· øget -brændstofkoncentration, hvori forbrændingsluften vanskeligt kan komme i tilstrækkelig tæt kontakt med brændstoffet. Dette medfører røgudvikling. Da 5 den indre ventilnål hæves ved et lavt brændstoftryk, og altså før den ydre overhovedet er begyndt at hæve sig, betyder det indskrænkninger i dimensioneringsmulighederne for den øverste række dyseboringer, eftersom forstøvningen bliver bedre jo højere brændstof-10 tryk der anvendes. Ved fuldlast anvendes alle dyseboringerne, hvorfor det heller ikke her er muligt at dimensionere optimalt. Dimensioneres dyseboringerne i den nederste række optimalt ved dellast, kan de jo ikke være optimale ved fuldlast, idet der ved fuldlast 15 anvendes et højere brændstoftryk.Such a construction has several disadvantages. During full-load operation of the engine, the cone-shaped propagation of atomized fuel from the nozzle bores in the two rows will intersect or intersect, resulting in incomplete. combustion. The clashing fuel cones result in an · increased fuel concentration, in which the combustion air can be difficult to come into sufficient close contact with the fuel. This causes smoke evolution. Since the inner valve needle is raised at a low fuel pressure, and that is, before the outer has started to rise at all, this means limitations in the sizing possibilities for the upper series of nozzle bores, since the atomization becomes better the higher the fuel pressure is used. At full load, all the nozzle bores are used, which is why it is not possible to dimension optimally here. If the nozzle bores in the lower row are optimally dimensioned at partial load, they may not be optimal at full load, since at full load 15 a higher fuel pressure is used.

Det er opfindelsen formål at forbedre den ovenfor nævnte indsprøjtningsventil på en sådan måde, at der både ved fuld belastning og ved delbelastning af mo-20 toren fås en i det væsentlige optimal forstøvning af brændstoffet.It is an object of the invention to improve the injection valve mentioned above in such a way that both at full load and at partial load of the engine a substantially optimum atomization of the fuel is obtained.

Dette opnås ved at udforme indsprøjtningsventilen i-følge opfindelsen som angivet i krav l's kendetegnen-25 de del. Ved denne udformning bliver det muligt at lade motoren gå med den ene dyserække under fuld belastning og med den anden dyserække ved delbelastning, idet dyseboringerne i hver række er dimensioneret til en brændstofmængde, der svarer til belastningen af 30 motoren. Derved får man ikke blot ved fuld belastning, men også ved delbelastning en god brændstofforstøvning med god, røgfri forbrænding, fordi der ikke kan opstå brændstofkoncentrationer, som ikke forbrændes fuldstændigt .This is achieved by designing the injection valve according to the invention as set forth in the characterizing part of claim 1. In this embodiment, it is possible to let the engine run with one nozzle row under full load and with the other nozzle row at partial load, the nozzle bores in each row being dimensioned for a fuel quantity corresponding to the load of the engine. In this way, not only at full load, but also at partial load, you get a good fuel spray with good, smoke-free combustion, because fuel concentrations that do not burn completely cannot be generated.

147381 3 1 Ved at udforme indsprøjtningsventilen ifølge opfin delsen som angivet i krav 2 får man en konstruktion, der er enkel at forarbejde og alligevel giver en sikker adskillelse mellem de to brændstofkredsløb ved 5 dyseboringerne.By designing the injection valve according to the invention as set forth in claim 2, a structure which is simple to process and yet provides a safe separation between the two fuel circuits at the nozzle bores is obtained.

Opfindelsen forklares nærmere under henvisning til tegningen, på hvilken, 10 fig. la viser et plant, aksialt snit gennem den nederste del af en udførelsesform for indsprøjtningsventilen ifølge opfindelsen, og fis. Ib viser et plant, aksialt snit gennem den 15 øverste del af samme udførelsesform.The invention is explained in more detail with reference to the drawing, in which: FIG. 1a shows a planar axial section through the lower part of an embodiment of the injection valve according to the invention, and figs. 1b shows a planar axial section through the top 15 of the same embodiment.

Ifølge fig. la og lb har indsprøjtningsventilen et ventillegeme l, der består af en øverste del 2 og en nederste del 3, der holdes sammen ved hjælp af enom-20 løbermøtrik 4. Ventillegemet 1 hviler med en ved dens øverste ende anbragt flange 5 på et ikke nærmere vist topstykke, der aflukker et forbrændingsrum i en cylinder i stempelforbrændingsmotoren opefter. Ventillegemet 1 er ført gennem topstykket og rager med den 25 nederste ende af legemets del 3 ind i forbrændingsrummet 7. I den nederste ende af delen 3 findes der aksialt forskudt for hinanden to rækker dyseboringer 8 og 9· Midterakserne for dyseboringerne i hver række ligger på en keglekappe, og keglevinklerne for de to kegler 30 afviger noget fra hinanden.According to FIG. 1a and 1b, the injection valve has a valve body 1 which consists of an upper part 2 and a lower part 3 held together by means of a single nut 4. The valve body 1 rests with a flange 5 arranged at its upper end on a no closer shown a cylinder head closing a combustion chamber in a cylinder in the piston combustion engine upwards. The valve body 1 is passed through the cylinder head and projects with the lower end of the body part 3 into the combustion chamber 7. At the lower end of the part 3 there are axially displaced for each other two rows of nozzle bores 8 and 9 · The central axes of the nozzle bores in each row lie on a cone sheath, and the cone angles of the two cones 30 differ slightly from each other.

De to rækker dyseboringer 8 og 9 er på brændstofsiden adskilt fra hinanden, idet der mellem de to rækker i delen 3 findes en kegleformet tætningsflade 10, på k 147381 1 hvilken der hviler et cylindrisk hult ventillegeme 11, der ved sin nederste ende har en kégleflade, der svarer til tætningsfladen 10, og som af en trykfjeder 12, fig. Ib, presses permanent mod tætningsfladen 10.The two rows of nozzle bores 8 and 9 are separated from each other on the fuel side, there being between the two rows of the part 3 a cone-shaped sealing surface 10, on k 147381 1, which rests on a cylindrical hollow valve body 11 having at its lower end a cone surface , which corresponds to the sealing surface 10, and that of a compression spring 12, fig. Ib, is permanently pressed against the sealing surface 10.

5 Trykkraften fra fjederen 12 bliver over en fjedertallerken 13 og et yderligere ventillegeme 14 overført til det hule ventillegeme 11. Fjederen 12 er dimensioneret således, at der under drift af indsprøjtnings-ventilen ikke sker nogen løftning af ventillegemet 11 10 fra tætningsfladen 10.5 The compressive force of the spring 12 is transferred over a spring plate 13 and a further valve body 14 to the hollow valve body 11. The spring 12 is dimensioned so that during operation of the injection valve there is no lifting of the valve body 11 10 from the sealing surface 10.

Foruden den med tætningsfladen 10 samvirkende ydre kegleflade har ventillegemet 11 på sin inderflade en kegleformet ventilsædeflade 15, der samvirker med en 15 tilsvarende udformet ventilsædeflade på en ventilnål 16, der er forskydelig i ventillegemet 11. Et nederste afsnit 17 på ventilnålen 16 har en formindsket diameter, så at der mellem ventillegemet 11 og afsnittet 17 dannes et ringrum 18. Den nederste række af dyse-20 boringerne 9 hører altså med hensyn til brændstoftilførsel til ventilnålen 16. Denne ventilnål presses af en trykfjeder 20, fig. Ib, mod ventilsædefladen 15, og fjederen er over en fjedertallerken 21 understøttet mod den øverste ende på ventilnålen 16.In addition to the outer cone surface cooperating with the sealing surface 10, the valve body 11 has on its inner surface a cone-shaped valve seat surface 15 which cooperates with a correspondingly shaped valve seat surface on a valve needle 16 which is displaceable in the valve body 11. A lower section 17 of the valve needle 16 has a reduced diameter. so that an annulus 18 is formed between the valve body 11 and the section 17. The lower row of the nozzle bores 9 thus belongs with respect to fuel supply to the valve needle 16. This valve needle is pressed by a compression spring 20, fig. 1b, towards the valve seat surface 15, and the spring is supported over a spring plate 21 against the upper end of the valve needle 16.

2525

Brændstoftilførslen til den øverste række af dyseboringerne 8 bliver påvirket af en anden ventilnål 22, der er hul, og som er forskydelig på ventillegemet 11, der adskiller de to dyseboringsrækker. Til den øverste ræk-30 ke af dyseboringerne 8 hører der i delen 3 en kegleformet ventilsædeflade 25, der samvirker med en til- , svarende udformet sædeflade på den nederste ende af den hule ventilnål 22. Denne hule ventilnål 22 presses af en trykfjeder 26 mod sædefladen 25· Fjederen 26 147381 5- 1 støtter sig over en fjedertallerkén 27 og et hylster 2$ på den øverste ende af den hule nål 22. Den øverste ende af fjederen 26 ligger an mod en fjedertallerken 29, der er fikseret i ventillegemet 1 over et af-5 standshylster 30 og en hul skrue 31» der er indskruet i flangen 5. Den hule skrue 31 omgiver de øverste ender på de koncentrisk i hinanden anbragte trykfjedre 12 og 20, der ligger an mod en yderligere hul skrue 32, som er indskruét i skruen 31. I skruen 32 er der 10 indskruet en skrue 33, der med sin nederste ende danner en centrering for den inderste trykfjeder 20, medens den hule skrue 32 til centrering af trykfjederen 12 har et trinformet nedsat afsnit 32*.The fuel supply to the upper row of the nozzle bores 8 is affected by a second hollow needle needle 22 which is slidable on the valve body 11 separating the two nozzle bore rows. To the upper row of the nozzle bores 8 there is in the part 3 a cone-shaped valve seat surface 25 which cooperates with a corresponding shaped seat surface on the lower end of the hollow valve needle 22. This hollow valve needle 22 is pressed by a compression spring 26 towards the seat surface 25 · The spring 26 147381 5- 1 rests over a spring plate 27 and a sleeve 2 $ on the upper end of the hollow needle 22. The upper end of the spring 26 abuts a spring plate 29 fixed in the valve body 1 above a hollow screw 31 'screwed into the flange 5. The hollow screw 31 surrounds the upper ends of the concentrically arranged compression springs 12 and 20 which abut an additional hollow screw 32 which is screwed in screw 31. In screw 32, a screw 33 is screwed in, which at its lower end forms a centering for the inner compression spring 20, while the hollow screw 32 for centering the compression spring 12 has a step-shaped reduced section 32 *.

15 Til brændstoftilførsel til de to rækker dyseboringer 8 og 9 findes der i dyselegemet 1 en brændstoftilførsel skanal for hver række, henholdsvis 35 og 45. Kanalen 35 begynder radialt i flangen 5 og strækker sig derefter i længderetning gennem delene 2 og 3 af ven-20 tillegemet. Den nederste ende af kanalen 35 udmunder i et ringrum 36» der i strømretning befinder sig oven over ventilsædefladen 25 og er udformet mellem den hule ventilnål 22 og delen 3. Kanalen 45 begynder ligeledes radialt i flangen 5 og strækker sig i længderetning 25 gennem delene 2 og 3 i ventillegemet 1. Den nederste ende af kanalen 45 udmunder i et ringrum 37, der er udformet i delen 3. Pra ringrummet 37 strækker der sig flere radiale huller 38 gennem den hule ventilnål 22,der omgiver ventillegemet 11. I området for ringrum-30 met 39 har ventillegemet 11 flere radiale huller 40, der danner en forbindelse med ringrummet 18. Neden under ringrummet 39 kan der findes et yderligere ringrum i den hule nål 22, til hvilket yderligere ringrum der er tilsluttet en opefter fra indsprøjtningsventilen 6 U7 381 1 førende afsugningskanal til at forhindre, at brændstof . fra ringrummet 39 langs de på hinanden glidende flader på den hule nål 22 og ventillegemet 11 når hen til rækken af dyseboringérne 8.15 For fuel supply to the two rows of nozzle bores 8 and 9, in the nozzle body 1 there is a fuel supply channel for each row, respectively 35 and 45. The channel 35 begins radially in the flange 5 and then extends longitudinally through the parts 2 and 3 of the valve 20. tillegemet. The lower end of the channel 35 opens into an annular space 36 which is in the direction of flow above the valve seat surface 25 and is formed between the hollow valve needle 22 and the part 3. The channel 45 also starts radially in the flange 5 and extends longitudinally 25 through the parts 2 and 3 in the valve body 1. The lower end of the duct 45 opens into an annulus 37 formed in the portion 3. In the annulus 37, several radial holes 38 extend through the hollow valve needle 22 surrounding the valve body 11. In the annulus region. At the 30 gauge 39, the valve body 11 has several radial holes 40 which form a connection with the annulus 18. Below the annulus 39 there is an additional annulus in the hollow needle 22 to which further annulus is connected upwardly from the injection valve 6 U7 381. 1 leading suction duct to prevent fuel. from the annulus 39 along the sliding surfaces of the hollow needle 22 and the valve body 11 reaching the row of the nozzle bores 8.

55

De to kanaler 35 og '45 er tilsluttet til en fælles, ikke vist brændstofpumpe, idet der mellem denne pumpe og de to kanaler findes en ligeledes ikke vist styreglider, der i afhængighed af belastningen forbinder 10 den ene af de to kanaler 35 og 45 med brændstofpumpens trykside.The two ducts 35 and '45 are connected to a common fuel pump, not shown, since there is also a control slider, not shown, which, depending on the load, connects one of the two ducts 35 and 45 to the two ducts. the pressure side of the fuel pump.

Ved fuld belastning af motoren er fx den nederste række på fx elleve dyseboringer 9 i drift. Brændstof, der 15 står under højt tryk, strømmer i dette tilfælde gennem kanalen 45 og når over ringrummet 37, hullerne 38, ringrummet 39 og hullerne 40 ind i ringrummet 18.At full load of the motor, for example, the bottom row of, for example, eleven nozzle bores 9 is in operation. In this case, fuel under high pressure 15 flows through channel 45 and reaches over annulus 37, holes 38, annulus 39 and holes 40 into annulus 18.

Trykket fra brændstoffet løfter ventilnålen 16 bort fra ventilsædefladen 15, så at brændstof derefter over 20 dyseboringerne 9 strømmer ud i forbrændingsrummet 7·The pressure from the fuel lifts the valve needle 16 away from the valve seat surface 15 so that fuel then flows over the nozzle bores 9 into the combustion chamber 7 ·

Ved delbelastning bliver brændstoftilførslen til kanalen 45 spærret, men samtidig hermed bliver brændstoftilførslen til kanalen 35 frigivet. Brændstof, der 25 står under højt tryk, når dermed ind i ringrummet 36, hvor brændstoffet løfter den hule ventilnål 22 op fra ventilsædefladen 25, så at gennemstrømningen til de fx seksten dyseboringer 8 bliver fri, og brændstof over disse boringer strømmer ind i forbrsndingsrummet 7· 50At partial load, the fuel supply to the duct 45 is blocked, but at the same time the fuel supply to the duct 35 is released. High-pressure fuel 25 thus enters the annulus 36, where the fuel lifts the hollow valve needle 22 up from the valve seat surface 25 so that the flow to the e.g. sixteen nozzle bores 8 becomes free and fuel over these bores flows into the combustion chamber 7 · 50

DK368478A 1977-09-01 1978-08-21 INJECTION VALVE FOR STAMP COMBUSTION ENGINES DK147381C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1065277A CH623114A5 (en) 1977-09-01 1977-09-01
CH1065277 1977-09-01

Publications (3)

Publication Number Publication Date
DK368478A DK368478A (en) 1979-03-02
DK147381B true DK147381B (en) 1984-07-09
DK147381C DK147381C (en) 1985-01-28

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ID=4365412

Family Applications (1)

Application Number Title Priority Date Filing Date
DK368478A DK147381C (en) 1977-09-01 1978-08-21 INJECTION VALVE FOR STAMP COMBUSTION ENGINES

Country Status (9)

Country Link
JP (1) JPS5848748B2 (en)
CH (1) CH623114A5 (en)
DE (2) DE2740880A1 (en)
DK (1) DK147381C (en)
FR (1) FR2402079B1 (en)
GB (1) GB2003550B (en)
IT (1) IT1098732B (en)
NL (1) NL183667C (en)
SE (1) SE430353B (en)

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JPS6123862A (en) * 1984-07-10 1986-02-01 Toyota Motor Corp Fuel injection controller
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US11885290B2 (en) 2020-09-08 2024-01-30 Caterpillar Inc. Fuel injector and nozzle assembly having dual concentric check assembly and ducted spray orifices
US11549474B2 (en) 2021-05-24 2023-01-10 Caterpillar Inc. Ducted fuel injector having nested checks with non-rotating outer check and method of operating same
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Also Published As

Publication number Publication date
SE7809201L (en) 1979-03-02
NL7808497A (en) 1979-03-05
FR2402079B1 (en) 1985-08-16
DK368478A (en) 1979-03-02
GB2003550A (en) 1979-03-14
FR2402079A1 (en) 1979-03-30
GB2003550B (en) 1982-10-20
NL183667B (en) 1988-07-18
JPS5447028A (en) 1979-04-13
SE430353B (en) 1983-11-07
JPS5848748B2 (en) 1983-10-31
IT7827194A0 (en) 1978-08-31
DE2759403C2 (en) 1988-09-29
IT1098732B (en) 1985-09-07
DK147381C (en) 1985-01-28
CH623114A5 (en) 1981-05-15
DE2740880A1 (en) 1979-03-15
NL183667C (en) 1988-12-16

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