EP0280774B1 - Camshaft drive for an internal-combustion piston engine - Google Patents

Camshaft drive for an internal-combustion piston engine Download PDF

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Publication number
EP0280774B1
EP0280774B1 EP19870117531 EP87117531A EP0280774B1 EP 0280774 B1 EP0280774 B1 EP 0280774B1 EP 19870117531 EP19870117531 EP 19870117531 EP 87117531 A EP87117531 A EP 87117531A EP 0280774 B1 EP0280774 B1 EP 0280774B1
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EP
European Patent Office
Prior art keywords
flange
crankshaft
receiving
gear
output flange
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
EP19870117531
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German (de)
French (fr)
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EP0280774A1 (en
Inventor
Hans Scherrer
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.)
Sulzer AG
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Gebrueder Sulzer AG
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Publication date
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Publication of EP0280774A1 publication Critical patent/EP0280774A1/en
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Publication of EP0280774B1 publication Critical patent/EP0280774B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/026—Gear drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear

Definitions

  • the invention relates to a control shaft drive with the features of the preamble of claim 1.
  • the ring gear In a known control shaft drive of this type, the ring gear consists of two ring halves, which are supported with one end face on an undercut shoulder of the crankshaft and which rest with their other end face on a two-part clamping ring which also surrounds the crankshaft and is clamped together by two screws.
  • This construction has the advantage that disassembly and reassembly of the ring gear in the motor is possible, i.e. without having to remove the crankshaft.
  • Disadvantages of the known construction can be seen in the fact that because of the two-part design of the ring gear and the clamping ring, it is complex both in terms of construction and in terms of assembly and is therefore expensive.
  • Difficulties in the assembly of the ring gear also cause its two-part construction because deviations from the tooth pitch can occur at the separation point of the ring halves. Furthermore, there are problems in the production of the ring gear when it has to be hardened because the ring halves can warp.
  • the invention has for its object to improve a control shaft drive of the type mentioned so that the design effort for the ring gear and its attachment is significantly reduced and that the manufacture and assembly of the ring gear is simplified.
  • this object is achieved by the features of the characterizing part of claim 1.
  • the one-piece design of the toothed ring simplifies its manufacture and also makes it less expensive, because during hardening, because of the closed ring shape, there is less tendency to warp than with ring halves.
  • shrinking the ring gear onto the mounting flange its assembly is considerably simplified. This simplification is supported by the somewhat larger dimensioning of the diameter of the mounting flange compared to the diameter of the output flange.
  • a control shaft drive is known from DE-OS 2 228 635, in which a separate output flange is fastened on an elongated section of the crankshaft bearing journal with a diameter.
  • a flywheel is attached to this flange, whereas the one-piece gearwheel for driving the control shaft is arranged on the extended section between the bearing journal and the output flange. If the gearwheel is to be removed in this control shaft drive, the output flange must first be removed from the extended section because the outer diameter of the flange is larger than the inner diameter of the gearwheel.
  • crankshaft has at one end an integral output flange and a shaft section located between this flange and the crankshaft bearing journal is surrounded by a two-part sleeve-like molded part.
  • This molded part is provided at its end adjacent to the output flange with a flange which is attached to the output flange together with a flywheel.
  • the other end of the two-part shaped piece is designed as a ring gear for driving the control shaft.
  • the outside diameter of the ring gear is smaller than that of the output flange.
  • a crankshaft 2 is mounted in a housing 1 of a reciprocating piston internal combustion engine, which works according to the four-stroke diesel method, of which a main bearing journal 3, a crank journal 4, a flange 5 serving to receive a ring gear 6 and a driven flange 7 forming the crankshaft end are shown are.
  • the ring gear 6 serving to drive a control shaft 8 is in engagement with an intermediate gear 9, which is rotatably mounted on a pin 11 together with a further intermediate gear 10.
  • the intermediate gears 9 and 10 are rotatably connected to each other, and the bearing pin 11 is fixed to the housing 1. With the intermediate gear 10, which has a smaller diameter than the intermediate gear 9, a gear 12 is engaged, which is fixed on the control shaft 8.
  • the gear transmission consisting of the parts 6, 9, 10 and 12 is shielded from the outside by a cover plate 13 fastened to the housing 1.
  • the receiving flange 5 has an outer diameter D F , which is slightly larger than the outer diameter D A of the output flange 7.
  • the output flange 7 as well as the receiving flange 5 are made in one piece with the crankshaft 2.
  • the somewhat larger diameter D F makes it possible to move this thermally widened ring gear over the driven flange 7 to the receiving flange 5, which is provided with a collar 5 ′ to limit this movement, when the ring gear 6 to be shrunk onto the flange 5.
  • the widened ring gear 6 lies against this collar 5 ', it is fastened to the flange 5 by cooling, it being irrelevant which relative angular position the ring gear assumes to the crankshaft.
  • the intermediate gears 9 and 10 are interconnected by thermal shrinking.
  • the gear wheel 12 fastened on the control shaft 8, on the other hand, is shrunk on hydraulically, for which purpose an axial blind bore 14 and radial bores 15 branching therefrom are provided.
  • the exact angular position between the crankshaft 2 and the control shaft 8 is achieved in that hydraulic pressure medium is supplied via the bores 14 and 15 under a pressure of, for example, 1000 bar, under which Influence the gear 12 is expanded somewhat.
  • the control shaft 8 can then be rotated relative to the gear 12 and thus to the crankshaft 2 until the desired angular position is reached. Then the pressure medium is discharged from the bores 14 and 15, so that the gear 12 is stuck on the control shaft 8.
  • the ring gear 6 on the receiving flange 5 If the ring gear 6 on the receiving flange 5 has to be replaced, it is cut open by means of cut-off grinding and pulled off the flange 5. Then a new ring gear 6 is thermally shrunk onto the flange 5.
  • the ring gear 6 could also be connected to the receiving flange 5 by a hydraulic pressure bandage, as is provided for the gear wheel 12 and the control shaft 8.
  • the cylindrical section 3 ′ of the crankshaft 2 located between the receiving flange 5 and the driven flange 7 is normally surrounded by a shaft seal arrangement, not shown here, which is detachably fastened to the cover plate 13.
  • the first crankshaft bearing (journal 3) is provided behind the receiving flange 5, as seen from the output flange 7.
  • this bearing arrangement is sufficient for the smooth running of the ring gear 6.

Description

Die Erfindung betriffl einen Steuerwellenantrieb mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a control shaft drive with the features of the preamble of claim 1.

Bei einem bekannten Steuerwellenantrieb dieser Art besteht der Zahnkranz aus zwei Ringhälften, die sich mit der einen Stirnfläche an einer hinterschnittenen Schulter der Kurbelwelle abstützen und die mit ihrer anderen Stirnfläche an einem zweiteiligen Klemmring anliegen, der ebenfalls die Kurbelwelle umgibt und durch zwei Schrauben zusammengespannt wird. Diese Konstruktion hat den Vorteil, dass eine Demontage sowie Wiedermontage des Zahnkranzes im Motor möglich ist, d.h. ohne dass die Kurbelwelle dazu ausgebaut werden müsste. Nachteile der bekannten Konstruktion sind darin zu sehen, dass sie wegen der Zweiteiligkeit des Zahnkranzes und des Spannringes sowohl konstruktiv wie auch montagemässig aufwendig und damit teuer ist. Schwierigkeiten bei der Montage des Zahnkranzes bereitet dessen Zweiteiligkeit auch deshalb, weil an der Trennstelle der Ringhälften Abweichungen von der Zahnteilung auftreten können. Ferner ergeben sich Probleme bei der Herstellung des Zahnkranzes, wenn dieser gehärtet werden muss, weil sich die Ringhälften verziehen können.In a known control shaft drive of this type, the ring gear consists of two ring halves, which are supported with one end face on an undercut shoulder of the crankshaft and which rest with their other end face on a two-part clamping ring which also surrounds the crankshaft and is clamped together by two screws. This construction has the advantage that disassembly and reassembly of the ring gear in the motor is possible, i.e. without having to remove the crankshaft. Disadvantages of the known construction can be seen in the fact that because of the two-part design of the ring gear and the clamping ring, it is complex both in terms of construction and in terms of assembly and is therefore expensive. Difficulties in the assembly of the ring gear also cause its two-part construction because deviations from the tooth pitch can occur at the separation point of the ring halves. Furthermore, there are problems in the production of the ring gear when it has to be hardened because the ring halves can warp.

. Der Erfindung liegt die Aufgabe zugrunde, einen Steuerwellenantrieb der eingangs genannten Art so zu verbessern, dass der konstruktive Aufwand für den Zahnkranz und seine Befestigung wesentlich verringert wird und dass die Herstellung und Montage des Zahnkranzes vereinfacht wird.. The invention has for its object to improve a control shaft drive of the type mentioned so that the design effort for the ring gear and its attachment is significantly reduced and that the manufacture and assembly of the ring gear is simplified.

Diese Aufgabe wird erfindungsgemäss durch die Merkmale des Kennzeichens des Anspruchs 1 gelöst. Durch die Einstückigkeit des Zahnkranzes wird seine Herstellung vereinfacht und auch verbilligt, weil beim Härten wegen der geschlossenen Ringform eine geringere Neigung zum Verziehen besteht als bei Ringhälften. Durch das Aufschrumpfen des Zahnkranzes auf den Aufnahmeflansch wird seine Montage wesentlich vereinfacht. Unterstützt wird diese Vereinfachung durch die etwas grössere Bemessung des Durchmessers des Aufnahmeflansches gegenüber dem Durchmesser des Abtriebsflansches.According to the invention, this object is achieved by the features of the characterizing part of claim 1. The one-piece design of the toothed ring simplifies its manufacture and also makes it less expensive, because during hardening, because of the closed ring shape, there is less tendency to warp than with ring halves. By shrinking the ring gear onto the mounting flange, its assembly is considerably simplified. This simplification is supported by the somewhat larger dimensioning of the diameter of the mounting flange compared to the diameter of the output flange.

Aus der DE-OS 2 228 635 ist ein Steuerwellenantrieb bekannt, bei dem auf einem verlängerten, im Durchmesser abgesetzten Abschnitt des Lagerzapfens der Kurbelwelle ein separater Abtriebsflansch befestigt ist. An diesem Flansch ist ein Schwungrad befestigt, wogegen das einstückige Zahnrad für den Antrieb der Steuerwelle auf dem verlängerten Abschnitt zwischen dem Lagerzapfen und dem Abtriebsflansch angeordnet ist. Wenn bei diesem Steuerwellenantrieb das Zahnrad entfernt werden soll, so muss zuvor der Abtriebsflansch vom verlängerten Abschnitt abgezogen werden, weil der Aussendurchmesser des Flansches grösser ist als der Innendurchmesser des Zahnrades.A control shaft drive is known from DE-OS 2 228 635, in which a separate output flange is fastened on an elongated section of the crankshaft bearing journal with a diameter. A flywheel is attached to this flange, whereas the one-piece gearwheel for driving the control shaft is arranged on the extended section between the bearing journal and the output flange. If the gearwheel is to be removed in this control shaft drive, the output flange must first be removed from the extended section because the outer diameter of the flange is larger than the inner diameter of the gearwheel.

Aus der Zeitschrift «Machine Design» 38, vom 6.1.1966, S. 139 bis 143 ist die Befestigungsart des Aufschrumpfens eines Zahnrades auf eine Welle bekannt.From the magazine "Machine Design" 38, from 6.1.1966, pp. 139 to 143, the method of fastening the shrinking of a gear wheel onto a shaft is known.

Aus der GB-PS 279 627 ist ein Steuerwellenantrieb bekannt, bei dem die Kurbelwelle an ihrem einen Ende einen mit ihr einstückigen Abtriebsflansch aufweist und ein zwischen diesem Flansch und dem Kurbelwellenlagerzapfen befindlicher Wellenabschnitt von einem zweiteiligen hülsenartigen Formteil umgeben ist. Dieser Formteil ist an seinem dem Abtriebsflansch benachbarten Ende mit einem Flansch versehen, der zusammen mit einem Schwungrad am Abtriebsflansch befestigt ist. Das andere Ende des zweiteiligen Formstückes ist als Zahnkranz für den Antrieb der Steuerwelle ausgebildet. Der Aussendurchmesser des Zahnkranzes ist kleiner als der des Abtriebsflansches.From GB-PS 279 627 a control shaft drive is known in which the crankshaft has at one end an integral output flange and a shaft section located between this flange and the crankshaft bearing journal is surrounded by a two-part sleeve-like molded part. This molded part is provided at its end adjacent to the output flange with a flange which is attached to the output flange together with a flywheel. The other end of the two-part shaped piece is designed as a ring gear for driving the control shaft. The outside diameter of the ring gear is smaller than that of the output flange.

Ein Ausführungsbeispiel der Erfindung wird in der folgenden Beschreibung anhand der Zeichnung näher erläutert, die einen Schnitt durch den Steuerwellenantrieb nach der Erfindung zeigt.An embodiment of the invention is explained in more detail in the following description with reference to the drawing, which shows a section through the control shaft drive according to the invention.

In einem Gehäuse 1 einer Hubkolbenbrennkraftmaschine, die nach dem Viertakt-Diesel-Verfahren arbeitet, ist eine Kurbelwelle 2 gelagert, von der ein Hauptlagerzapfen 3, ein Kurbelzapfen 4, ein zur Aufnahme eines Zahnkranzes 6 dienender Flansch 5 und ein das Kurbelwellenende bildender Abtriebsflansch 7 gezeigt sind. Der dem Antrieb einer Steuerwelle 8 dienende Zahnkranz 6 ist im Eingriff mit einem Zwischenzahnrad 9, das zusammen mit einem weiteren Zwischenzahnrad 10 auf einem Zapfen 11 drehbar gelagert ist. Die Zwischenzahnräder 9 und 10 sind gegeneinander drehfest verbunden, und der Lagerzapfen 11 ist am Gehäuse 1 befestigt. Mit dem Zwischenzahnrad 10, das einen kleineren Durchmesser aufweist als das Zwischenzahnrad 9, steht ein Zahnrad 12 im Eingriff, das auf der Steuerwelle 8 befestigt ist. Das aus den Teilen 6,9,10 und 12 bestehende Zahnradgetriebe ist nach aussen durch eine am Gehäuse 1 befestigte Deckplatte 13 abgeschirmt.A crankshaft 2 is mounted in a housing 1 of a reciprocating piston internal combustion engine, which works according to the four-stroke diesel method, of which a main bearing journal 3, a crank journal 4, a flange 5 serving to receive a ring gear 6 and a driven flange 7 forming the crankshaft end are shown are. The ring gear 6 serving to drive a control shaft 8 is in engagement with an intermediate gear 9, which is rotatably mounted on a pin 11 together with a further intermediate gear 10. The intermediate gears 9 and 10 are rotatably connected to each other, and the bearing pin 11 is fixed to the housing 1. With the intermediate gear 10, which has a smaller diameter than the intermediate gear 9, a gear 12 is engaged, which is fixed on the control shaft 8. The gear transmission consisting of the parts 6, 9, 10 and 12 is shielded from the outside by a cover plate 13 fastened to the housing 1.

Der Aufnahmeflansch 5 hat einen Aussendurchmesser DF, der etwas grösser ist als der Aussendurchmesser DA des Abtriebsflansches 7. Der Abtriebsflansch 7 wie auch der Aufnahmeflansch 5 sind einstückig mit der Kurbelwelle 2 hergestellt. Durch den etwas grösseren Durchmesser DF wird es möglich, beim Montieren des auf den Flansch 5 aufzuschrumpfenden Zahnkranzes 6 diesen thermisch aufgeweiteten Zahnkranz über den Abtriebsflansch 7 hinweg zum Aufnahmeflansch 5 zu bewegen, der zum Begrenzen dieser Bewegung mit enem Bund 5' versehen ist. Wenn der aufgeweitete Zahnkranz 6 an diesem Bund 5' anliegt, wird er durch Abkühlen auf dem Flansch 5 befestigt, wobei es keine Rolle spielt, welche relative Winkellage der Zahnkranz zur Kurbelwelle einnimmt. In gleicher Wiese sind die Zwischenzahnräder 9 und 10 durch thermisches Schrumpfen miteinander verbunden. Das auf der Steuerwelle 8 befestigte Zahnrad 12 ist dagegen auf hydraulischem Wege aufgeschrumpft, wozu in der Welle eine axiale Sackbohrung 14 und von dieser abzweigende radiale Bohrungen 15 vorgesehen sind. Die exakte Winkelstellung zwischen der Kurbelwelle 2 und der Steuerwelle 8 wird dadurch erreicht, dass über die Bohrungen 14 und 15 hydraulisches Druckmittel unter einem Druck von beispielsweise 1000 bar zugeführt wird, unter dessem Einfluss das Zahnrad 12 etwas aufgeweitet wird. Die Steuerwelle 8 kann dann relativ zum Zahnrad 12 und damit zur Kurbelwelle 2 verdreht werden, bis die gewünschte Winkelstellung erreicht ist. Dann wird das Druckmittel aus den Bohrungen 14 und 15 abgelassen, so dass das Zahnrad 12 auf der Steuerwelle 8 festsitzt.The receiving flange 5 has an outer diameter D F , which is slightly larger than the outer diameter D A of the output flange 7. The output flange 7 as well as the receiving flange 5 are made in one piece with the crankshaft 2. The somewhat larger diameter D F makes it possible to move this thermally widened ring gear over the driven flange 7 to the receiving flange 5, which is provided with a collar 5 ′ to limit this movement, when the ring gear 6 to be shrunk onto the flange 5. When the widened ring gear 6 lies against this collar 5 ', it is fastened to the flange 5 by cooling, it being irrelevant which relative angular position the ring gear assumes to the crankshaft. In the same field, the intermediate gears 9 and 10 are interconnected by thermal shrinking. The gear wheel 12 fastened on the control shaft 8, on the other hand, is shrunk on hydraulically, for which purpose an axial blind bore 14 and radial bores 15 branching therefrom are provided. The exact angular position between the crankshaft 2 and the control shaft 8 is achieved in that hydraulic pressure medium is supplied via the bores 14 and 15 under a pressure of, for example, 1000 bar, under which Influence the gear 12 is expanded somewhat. The control shaft 8 can then be rotated relative to the gear 12 and thus to the crankshaft 2 until the desired angular position is reached. Then the pressure medium is discharged from the bores 14 and 15, so that the gear 12 is stuck on the control shaft 8.

Wenn der Zahnkranz 6 auf dem Aufnahmeflansch 5 ausgewechselt werden muss, so wird dieser durch Trennschleifen aufgeschnitten und vom Flansch 5 abgezogen. Daraufhin wird ein neuer Zahnkranz 6 thermisch auf den Flansch 5 aufgeschrumpft.If the ring gear 6 on the receiving flange 5 has to be replaced, it is cut open by means of cut-off grinding and pulled off the flange 5. Then a new ring gear 6 is thermally shrunk onto the flange 5.

Abweichend von dem beschriebenen Beispiel könnte auch der Zahnkranz 6 durch einen hydraulischen Druckverband mit dem Aufnahmeflansch 5 verbunden sein, wie dies für das Zahnrad 12 und die Steuerwelle 8 vorgesehen ist.In a departure from the example described, the ring gear 6 could also be connected to the receiving flange 5 by a hydraulic pressure bandage, as is provided for the gear wheel 12 and the control shaft 8.

Der zwischen dem Aufnahmeflansch 5 und dem Abtriebsflansch 7 befindliche zylindrische Abschnitt 3' der Kurbelwelle 2 ist normalerweise mit einer hier nicht dargestellten Wellendichtungsanordnung umgeben, die an der Deckplatte 13 lösbar befestigt ist.The cylindrical section 3 ′ of the crankshaft 2 located between the receiving flange 5 and the driven flange 7 is normally surrounded by a shaft seal arrangement, not shown here, which is detachably fastened to the cover plate 13.

In dem gezeichneten Ausführungsbeispiel ist - vom Abtriebsflansch 7 her gesehen - das erste Kurbelwellenlager (Zapfen 3) hinter dem Aufnahmeflansch 5 vorgesehen. Im allgemeinen genügt diese Lageranordnung für den ruhigen Lauf des Zahnkranzes 6. Es ist jedoch auch möglich, auch den zylindrischen Wellenabschnitt 3' als Lagerstelle auszubilden, und zwar zusätzlich zu der erwähnten Wellendichtungsanordnung.In the exemplary embodiment shown, the first crankshaft bearing (journal 3) is provided behind the receiving flange 5, as seen from the output flange 7. In general, this bearing arrangement is sufficient for the smooth running of the ring gear 6. However, it is also possible to design the cylindrical shaft section 3 'as a bearing point, in addition to the shaft seal arrangement mentioned.

Claims (3)

1. A camshaft drive for a reciprocating piston internal combustion engine, comprising a crankshaft (2) integrally formed at one end with an output flange (7), a gear rim (6) for driving the camshaft (8) being secured on the crankshaft (2) near the flange (7), characterised in that the crankshaft (2) has a flange (5) for receiving the gear. rim (6), the diameter (DF) of the receiving flange being somewhat greater than the diameter (DA) of the output flange (7), and a portion (3') of the crankshaft (3) is disposed between the receiving flange (5) and the output flange (7) and has a smaller diameter than the output flange (7), and the gear rim (6) is in one piece and during assembly is movable over the output flange (7) and is shrunk on to the receiving flange (5).
2. A camshaft drive according to claim 1, characterised in that the receiving flange (5), on the side remote from the output flange (7), is provided with a radially projecting collar (5'), serving as an abutment for the gear rim (6).
3. A camshaft drive according to claim 1 or 2, characterised in that the first crankshaft bearing (3), as seen from the output flange (7), is disposed behind the receiving flange (5).
EP19870117531 1987-02-26 1987-11-27 Camshaft drive for an internal-combustion piston engine Expired - Lifetime EP0280774B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH735/87 1987-02-26
CH73587A CH673681A5 (en) 1987-02-26 1987-02-26

Publications (2)

Publication Number Publication Date
EP0280774A1 EP0280774A1 (en) 1988-09-07
EP0280774B1 true EP0280774B1 (en) 1990-11-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870117531 Expired - Lifetime EP0280774B1 (en) 1987-02-26 1987-11-27 Camshaft drive for an internal-combustion piston engine

Country Status (9)

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EP (1) EP0280774B1 (en)
JP (1) JP2798211B2 (en)
CH (1) CH673681A5 (en)
DE (1) DE3766360D1 (en)
DK (1) DK8588A (en)
ES (1) ES2019923B3 (en)
FI (1) FI89976C (en)
NO (1) NO880836L (en)
PL (1) PL158264B1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI92855C (en) * 1993-02-16 1995-01-10 Waertsilae Diesel Int Adjustable camshaft arrangement for camshaft on a large diesel engine
GB2346670B (en) * 1999-02-11 2003-07-16 United Eng Forgings Ltd Crankshaft construction
CN102121520A (en) * 2010-12-27 2011-07-13 中国北车集团大连机车车辆有限公司 Gear transmission device

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB104493A (en) * 1917-01-02 1917-03-08 Rolls Royce Improvements in or relating to Camshaft Driving Gear of Internal Combustion Engines
GB279627A (en) * 1926-10-21 1927-11-03 Rover Co Ltd Improvements in or relating to means for driving the camshafts of internal combustion engines
DE2228635A1 (en) * 1972-06-13 1974-01-03 Kloeckner Humboldt Deutz Ag PISTON MACHINE WITH A CRANKSHAFT
JPS5377213U (en) * 1976-11-29 1978-06-27
JPS6059818U (en) * 1983-09-30 1985-04-25 日産ディーゼル工業株式会社 crankshaft
JPS60139968A (en) * 1983-12-28 1985-07-24 Nippon Piston Ring Co Ltd Preparation of assembly cam shaft
JPS6283556A (en) * 1985-10-09 1987-04-17 Honda Motor Co Ltd Damper device of gear train

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Publication number Publication date
FI89976B (en) 1993-08-31
ES2019923B3 (en) 1991-07-16
DK8588A (en) 1988-08-27
NO880836L (en) 1988-08-29
JP2798211B2 (en) 1998-09-17
DE3766360D1 (en) 1991-01-03
JPS63235608A (en) 1988-09-30
FI880003A (en) 1988-08-27
NO880836D0 (en) 1988-02-25
FI880003A0 (en) 1988-01-04
FI89976C (en) 1996-12-23
CH673681A5 (en) 1990-03-30
PL270836A1 (en) 1988-12-08
PL158264B1 (en) 1992-08-31
EP0280774A1 (en) 1988-09-07
DK8588D0 (en) 1988-01-08

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