EP0280774A1 - 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
EP0280774A1
EP0280774A1 EP87117531A EP87117531A EP0280774A1 EP 0280774 A1 EP0280774 A1 EP 0280774A1 EP 87117531 A EP87117531 A EP 87117531A EP 87117531 A EP87117531 A EP 87117531A EP 0280774 A1 EP0280774 A1 EP 0280774A1
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EP
European Patent Office
Prior art keywords
flange
crankshaft
control shaft
receiving
ring gear
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.)
Granted
Application number
EP87117531A
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German (de)
French (fr)
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EP0280774B1 (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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Sulzer AG
Gebrueder Sulzer AG
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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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Classifications

    • 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 for a reciprocating piston internal combustion engine, with a crankshaft which has an output flange at one end and, in addition to this flange, a toothed ring fixed on the shaft for driving the control shaft.
  • 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 engine is possible, ie without the crankshaft having to be removed.
  • 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.
  • 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.
  • crankshaft for receiving the ring gear has a flange, the diameter of which is slightly larger than the diameter of the output flange integral with the crankshaft, and in that the ring gear is formed in one piece, which can be moved over the output flange during its assembly and shrunk onto the mounting flange. Due to the one-piece design of the ring gear, its manufacture is simplified and also reduced in cost, because during hardening there is less tendency to warp due to the closed ring shape than with ring halves. The assembly of the toothed ring on the mounting flange 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 housing 1 of a reciprocating piston internal combustion engine which works according to the four-stroke diesel method, there is one Mounted crankshaft 2, 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.
  • 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 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 somewhat 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 expanded 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 rests against this collar 5 ', it is fastened to the flange 5 by cooling, it being irrelevant what the angular position of the ring gear relative to the crankshaft is.
  • 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 there is an axial blind bore 14 in the shaft and a radial one branching off from it Holes 15 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 whose influence the gear wheel 12 is widened 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 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 located between the receiving flange 5 and the output flange 7 cylindrical portion 3ef of the crankshaft 2 is normally surrounded by a shaft seal arrangement, not shown here, which is releasably attached 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Gears, Cams (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The camshaft drive has a crankshaft (2) which is provided on its one end with an output drive flange (7) and with a retaining flange (5) next to this flange. On this flange (5) there is mounted a single-piece toothed rim (6), as the drive for the camshaft (8). The diameter (DF) of the retaining flange (5) is somewhat greater than the diameter (DA) of the output drive flange (7) forming a single piece with the crankshaft (2). The single-piece toothed rim (6) can be moved away over the output drive flange (7) during its installation, and is shrunk onto the retaining flange (5). <IMAGE>

Description

Die Erfindung betrifft einen Steuerwellenantrieb für eine Hubkolbenbrennkraftmaschine, mit einer Kurbelwelle, die an ihrem einen Ende einen Abtriebsflansch und neben diesem Flansch einen auf der Welle befestigten Zahnkranz für den Antrieb der Steuerwelle aufweist.The invention relates to a control shaft drive for a reciprocating piston internal combustion engine, with a crankshaft which has an output flange at one end and, in addition to this flange, a toothed ring fixed on the shaft for driving the control shaft.

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 Konstrukton 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 engine is possible, ie without the crankshaft having to be removed. 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 arise Problems with the production of the ring gear if 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 dadurch gelöst, dass die Kurbelwelle zur Aufnahme des Zahnkranzes einen Flansch aufweist, dessen Durchmesser etwas grösser als der Durchmesser des mit der Kurbelwelle einstückigen Abtriebsflansches ist, und dass der Zahnkranz einstückig ausgebildet ist, der bei seiner Montage über den Ab­triebsflansch hinweg bewegbar und auf dem Aufnahmeflansch aufgeschrumpft ist. 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 Aufschrupfen 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.This object is achieved according to the invention in that the crankshaft for receiving the ring gear has a flange, the diameter of which is slightly larger than the diameter of the output flange integral with the crankshaft, and in that the ring gear is formed in one piece, which can be moved over the output flange during its assembly and shrunk onto the mounting flange. Due to the one-piece design of the ring gear, its manufacture is simplified and also reduced in cost, because during hardening there is less tendency to warp due to the closed ring shape than with ring halves. The assembly of the toothed ring on the mounting flange 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.

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.In a housing 1 of a reciprocating piston internal combustion engine, which works according to the four-stroke diesel method, there is one Mounted crankshaft 2, 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. 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 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 5ʹ versehen ist. Wenn der aufgeweitete Zahnkranz 6 an diesem Bund 5ʹ 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 somewhat 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 expanded 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 rests against this collar 5 ', it is fastened to the flange 5 by cooling, it being irrelevant what the angular position of the ring gear relative to the crankshaft is. 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 there is an axial blind bore 14 in the shaft and a radial one branching off from it Holes 15 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 whose influence the gear wheel 12 is widened 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 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 3ʹ der Kurbelwelle 2 ist normalerweise mit einer hier nicht dargestellten Wellendichtungsanordnung umgeben, die an der Deckplatte 13 lösbar befestigt ist.The located between the receiving flange 5 and the output flange 7 cylindrical portion 3ef of the crankshaft 2 is normally surrounded by a shaft seal arrangement, not shown here, which is releasably attached 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 3ʹ 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 use the cylindrical shaft section 3ʹ as a bearing to train, in addition to the shaft seal arrangement mentioned.

Claims (3)

1. Steuerwellenantrieb für eine Hubkolbenbrennkraft­maschine, mit einer Kurbelwelle, die an ihrem einen Ende einen Abtriebsflansch und neben diesem Flansch einen auf der Welle befestigten Zahnkranz für den Antrieb der Steuerwelle aufweist, dadurch geken nzeichnet, dass die Kurbelwelle zur Aufnahme des Zahnkranzes einen Flansch aufweist, dessen Durchmesser etwas grösser als der Durchmesser des mit der Kurbelwelle einstückigen Abtriebsflansches ist, und dass der Zahnkranz einstückig ausgebildet ist, der bei seiner Montage über den Abtriebsflansch hinweg bewegbar und auf dem Aufnahmeflansch auf­geschrumpft ist.1. Control shaft drive for a reciprocating piston internal combustion engine, with a crankshaft, which has an output flange at one end and, in addition to this flange, a toothed ring attached to the shaft for driving the control shaft, characterized in that the crankshaft has a flange for receiving the toothed ring. whose diameter is slightly larger than the diameter of the output flange integral with the crankshaft, and that the toothed ring is formed in one piece, which can be moved over the output flange during assembly and shrunk onto the receiving flange. 2. Steuerwellenantrieb nach Anspruch 1, dadruch gekenn­zeichnet, dass der Aufnahmeflansch auf seiner dem Abtriebsflansch abgewendeten Seite mit einem radial vorstehenden Bund versehen ist, der als Anschlag für den Zahnkranz dient.2. Control shaft drive according to claim 1, characterized in that the receiving flange is provided on its side facing away from the output flange with a radially projecting collar which serves as a stop for the ring gear. 3. Steuerwellenantrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das erste Kurbelwellenlager - ­vom Abtriebsflansch her gesehen - hinter dem Aufnah­meflansch vorgesehen ist.3. Control shaft drive according to claim 1 or 2, characterized in that the first crankshaft bearing - seen from the output flange - is provided behind the receiving flange.
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 true EP0280774A1 (en) 1988-09-07
EP0280774B1 EP0280774B1 (en) 1990-11-22

Family

ID=4193975

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)

Country Link
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)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0622527A1 (en) * 1993-02-16 1994-11-02 Oy Wärtsilä Diesel International Ltd. An adjustable force transmission arrangement for a camshaft of a large diesel engine
GB2346670A (en) * 1999-02-11 2000-08-16 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

Citations (3)

* 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

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Patent Citations (3)

* 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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
MACHINE DESIGN, Band 38, Nr. 1, 6. Januar 1966, Seiten 139-143, Cleveland, US; G.W. MICHALEC: "Fastening gears" *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0622527A1 (en) * 1993-02-16 1994-11-02 Oy Wärtsilä Diesel International Ltd. An adjustable force transmission arrangement for a camshaft of a large diesel engine
GB2346670A (en) * 1999-02-11 2000-08-16 United Eng Forgings Ltd Crankshaft construction
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

Also Published As

Publication number Publication date
JP2798211B2 (en) 1998-09-17
DK8588D0 (en) 1988-01-08
FI880003A (en) 1988-08-27
JPS63235608A (en) 1988-09-30
FI89976C (en) 1996-12-23
DK8588A (en) 1988-08-27
NO880836D0 (en) 1988-02-25
EP0280774B1 (en) 1990-11-22
DE3766360D1 (en) 1991-01-03
FI880003A0 (en) 1988-01-04
PL158264B1 (en) 1992-08-31
CH673681A5 (en) 1990-03-30
PL270836A1 (en) 1988-12-08
FI89976B (en) 1993-08-31
ES2019923B3 (en) 1991-07-16
NO880836L (en) 1988-08-29

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