EP1288451B1 - Zylinderkopf für eine Hubkolben-Brennkraftmaschine mit einer hubvariablen Ventilsteuerung - Google Patents
Zylinderkopf für eine Hubkolben-Brennkraftmaschine mit einer hubvariablen Ventilsteuerung Download PDFInfo
- Publication number
- EP1288451B1 EP1288451B1 EP02014670A EP02014670A EP1288451B1 EP 1288451 B1 EP1288451 B1 EP 1288451B1 EP 02014670 A EP02014670 A EP 02014670A EP 02014670 A EP02014670 A EP 02014670A EP 1288451 B1 EP1288451 B1 EP 1288451B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- cylinder head
- teeth
- adjusting element
- head according
- 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
Links
Images
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
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
-
- 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
- F01L1/10—Valve drive by means of crank-or eccentric-driven rods
-
- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating valves
-
- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
-
- 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
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- the invention relates to a cylinder head for a reciprocating piston internal combustion engine a stroke-variable valve control according to the features in the preamble of the claim 1.
- the swing arm is mounted on another swivel axis, which in turn is pivotally arranged about the pivot axis of the rocker arm.
- the control shaft rotates at half the crankshaft speed, while the rocker arm is pivoted at half the crankshaft speed becomes.
- the cam surface of the rocker arm presses the rocker arm wedge towards the gas exchange valve, which opens it periodically.
- the gas exchange valve is closed again by a valve spring.
- the pivot axis of the rocker arm pivoted about the rocking axis of the rocker arm.
- a disadvantage of this configuration is the relatively large space required for the Rocker arm with its pivot axis, which is from the rocking axis of the rocker arm must be spaced.
- the object of the invention is the installation space for such a variable stroke valve control to minimize.
- the curved surface of the actuating element advantageously lies directly on the valve stem or on a roller tappet or a play compensation element.
- the arrangement according to the invention makes it possible to dispense with an intermediate element, such as a movable wedge, between the pivot lever and valve stem or roller tappet or play compensation element for stroke variation.
- an intermediate element such as a movable wedge
- the drive of the intermediate element necessary for the adjustment is also eliminated.
- a further advantage is the significantly lower moving masses, which means that the internal combustion engine can be designed for a higher speed range.
- the elimination of components compared to the prior art advantageously also reduces the overall weight of the valve train. When using an adjustment system per cylinder of the internal combustion engine, it is also possible to implement a single cylinder shutdown, which enables considerable fuel savings.
- the configuration according to the invention according to claims 2 to 5 enables one extremely small and compact construction.
- the stroke adjustment is very simple Way by axial displacement of the output shaft.
- no further adjusting elements are required for the axial adjustment of the output shaft.
- the Stroke adjustment reinforced with the same axial displacement of the output shaft In the configuration of the variable stroke valve train according to claim 6, the Stroke adjustment reinforced with the same axial displacement of the output shaft.
- the pitch of the helical gearing can be used for almost any gear ratio between the axial displacement of the output shaft and the Stroke adjustment for the gas exchange valve can be adjusted. Translations can be done can be realized either with a large axial displacement the output shaft a small change in the valve stroke or by a small axial displacement the output shaft causes a very large valve lift adjustment. By simply changing the slope, you can either position it very precisely or very fast adjustment systems can be implemented.
- backlash-free valve trains also fully variable valve trains, can be realized.
- the configuration according to claim 8 reduces the friction in the valve train, which has a positive effect on fuel consumption.
- FIG. 1 shows the perspective illustration of a stroke-variable valve control 1, consisting of a drive shaft 2 with a drive shaft 2a and a crank pin 3, which has an articulated connection 4, consisting of a connecting rod 12 and an output element 13, with an output shaft 5, with an output axis 5a is articulated.
- the connecting rod 12 is on the one hand rotatable with the crank pin 3 and on the other hand via a pivot axis 14 with the output element 13 rotatably connected.
- the output element 13 is on the, the pivot axis 14 facing away, pivotally mounted about the output axis 5.
- the direction of the output axis 5a is on both sides of the output element 13 an actuating element 6, 6 'arranged radially around the output shaft 5.
- Every actuator 6, 6 ' has a curved surface arranged radially on the outer circumference.
- the actuating element 6, 6 ' is a cam with a base circle 7, 7' and a raised one Area 8, 8 '.
- the actuating elements 6, 6 ' are with the output shaft 5 via a first teeth 9, 9 'in operative connection.
- the output element 13 stands with the Output shaft 5 via a second toothing 10, shown in Fig. 2, in operative connection.
- Each control element 6, 6 ' presses with its curved surface on a roller tappet 11, 11 '.
- the drive shaft 2 When the internal combustion engine is operating, the drive shaft 2 is not activated by one here Drive shown driven, which rotates about its drive axis 2a.
- the Crank pin 3 and the connecting rod 13 rotate accordingly about the drive axis 2a.
- the rotational movement of one end of the connecting rod 12 is via the output element 13 in connection with the pivot axis 14 in a pivoting movement of the Output shaft 5 converted around the output axis 5a.
- the control elements 6, 6 ' swivel once around the output axis during a full rotation of the drive shaft 2 5a.
- the output shaft 5 has three inclined toothed areas radially on their outer circumference, two areas with a first Gearing 9, 9 ', between which an area with a second gearing 10 is arranged.
- the pitch of the first toothing 9, 9 'and the second toothing 10 are designed in opposite directions to each other.
- the first toothing 9, 9 ' meshes with an internal toothing in the actuating element 6, 6 '.
- the second toothing 10 meshes with an internal toothing in the output element 13. Because of the opposite toothing between the first toothing 9, 9 'and the second toothing 10 is the angular adjustment of the cam surface 6, 6 'reinforced with respect to an axial displacement of the output shaft 5.
- the second toothing 10 can also be designed as a straight toothing, however In this case there is no need to increase the adjustment angle with the same axial Displacement of the output shaft 5.
- the greater the pitch of the gears the smaller the adjustment angle with respect to an axial displacement of the output shaft 5. It follows that with a large incline, large adjustment paths of the Output shaft 5 leads to small changes in the angle of the actuating element 6, 6 '. A In contrast, a small pitch of the toothing leads to a large angle adjustment of the control element 6, 6 '.
- the Adjustment speed and the accuracy of the adjustment system on the corresponding stroke variable valve train can be adjusted.
- the bearings between the crank pin 3 and the connecting rod 12, and the Pivot axis 14 and the output element 13 can optionally be used as a sliding or Roll bearings are run.
- the usual valve train materials can be used as materials be used. As is common in valve train today, there can be between the adjusting element and the valve also arranged valve clearance compensation element become.
- the output shaft 5 actuates the gas exchange valves of a cylinder.
- a single cylinder shutdown is also in this configuration possible.
- an output shaft 5 actuates the gas exchange valves of several cylinders or an entire cylinder bank.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
In vorteilhafter Weise liegt die Kurvenfläche des Stellelementes direkt auf dem Ventilschaft oder auf einem Rollenstößel bzw. einem Spielausgleichselement auf. Durch die erfindungsgemäße Anordnung kann auf ein Zwischenelement, wie beispielsweise einem beweglichen Keil, zwischen Schwenkhebel und Ventilschaft bzw. Rollenstößel oder Spielausgleichselement zur Hubvariation verzichtet werden. Durch den Entfall des Zwischenelements entfällt somit auch der für die Verstellung notwendige Antrieb des Zwischenelements. Als weiterer Vorteil sind die deutlich geringeren bewegten Massen anzusehen, wodurch die Brennkraftmaschine für einen höheren Drehzahlbereich ausgelegt werden kann. Durch den Entfall von Bauteilen gegenüber dem Stand der Technik reduziert sich in vorteilhafter Weise auch das Gesamtgewicht des Ventiltriebs. Beim Einsatz eines Verstellsystems pro Zylinder der Brennkraftmaschine ist es darüber hinaus auch möglich, eine Einzelzylinderabschaltung zu realisieren, wodurch erhebliche Kraftstoffeinsparungen möglich sind.
- Fig. 1
- zeigt die Aufsicht auf eine hubvariable Ventilsteuerung,
- Fig. 2
- zeigt die Ausgestaltung einer Abtriebswelle.
- 1
- Hubvariable Ventilsteuerung
- 2
- Antriebswelle
- 2a
- Antriebsachse
- 3
- Hubzapfen
- 4
- Gelenkige Verbindung
- 5
- Abtriebswelle
- 5a
- Abtriebsachse
- 6, 6'
- Stellelement
- 7, 7'
- Grundkreis
- 8, 8'
- Erhabener Bereich
- 9, 9'
- Erste Verzahnung
- 10
- Zweite Verzahnung
- 11, 11'
- Rollenstößel
- 12
- Pleuel
- 13
- Abtriebselement
- 14
- Schwenkachse
Claims (7)
- Zylinderkopf für eine Hubkolben-Brennkraftmaschine mit einer hubvariablen Ventilsteuerung mit zumindest einem Gaswechselventil und mit einer Antriebswelle mit zumindest einem Hubzapfen der über eine gelenkige Verbindung mit einer zur Antriebswelle parallel angeordneten Abtriebswelle mit zumindest einem Stellelement mit zumindest einer radial angeordneten Kurvenfläche verbunden ist, wobei eine Drehung der Antriebswelle um eine Antriebsachse über die gelenkige Verbindung in eine Schwenkbewegung der Abtriebswelle um eine Abtriebsachse transformiert wird, wobei der Ventilhub durch Schwenken des Stellelementes um die Abtriebsachse einstellbar ist,
dadurch gekennzeichnet, dass das Stellelement (6, 6') durch Verschieben der Abtriebswelle (5) in Richtung der Abtriebsachse um die Abtriebsachse (5a) schwenkbar ist. - Zylinderkopf nach Anspruch 1,
dadurch gekennzeichnet, dass das Stellelement (6, 6') ein Nocken mit einem Grundkreis (7, 7') und zumindest einem erhabenen Bereich (8, 8') ist. - Zylinderkopf nach Anspruch 1 oder 2,
dadurch gekennzeichnet, dass das Stellelement (6, 6') mit der Abtriebswelle (5) über eine erste Verzahnung (9, 9') und die gelenkige Verbindung (4) mit der Abtriebswelle über eine zweite Verzahnung (10) in Wirkverbindung steht. - Zylinderkopf nach Anspruch 3,
dadurch gekennzeichnet, dass die erste Verzahnung (9, 9') eine Schrägverzahnung und die zweite Verzahnung (10) eine Geradverzahnung oder eine Schrägverzahnung ist. - Zylinderkopf nach Anspruch 4, wobei die erste und die zweite Verzahnung eine Schrägverzahnung ist,
dadurch gekennzeichnet, dass die Schrägverzahnungen zueinander gegenläufig sind. - Zylinderkopf nach einem der zuvor genannten Ansprüche, wobei die Kurvenfläche mit dem Gaswechselventil indirekt in Wirkverbindung steht,
dadurch gekennzeichnet, dass zwischen dem Ventil und dem Stellelement (6, 6') ein Ventilspielausgleichselement angeordnet ist. - Zylinderkopf nach einem der zuvor genannten Ansprüche, wobei die Kurvenfläche mit dem Gaswechselventil indirekt in Wirkverbindung steht,
dadurch gekennzeichnet, dass zwischen dem Ventil und dem Stellelement (6, 6') ein Rollenstößel angeordnet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10139043 | 2001-08-08 | ||
DE10139043A DE10139043A1 (de) | 2001-08-08 | 2001-08-08 | Zylinderkopf für eine Hubkolben-Brennkraftmaschine mit einer hubvariablen Ventilsteuerung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1288451A1 EP1288451A1 (de) | 2003-03-05 |
EP1288451B1 true EP1288451B1 (de) | 2004-02-18 |
Family
ID=7694854
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02014670A Expired - Lifetime EP1288451B1 (de) | 2001-08-08 | 2002-07-03 | Zylinderkopf für eine Hubkolben-Brennkraftmaschine mit einer hubvariablen Ventilsteuerung |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1288451B1 (de) |
DE (2) | DE10139043A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5604240B2 (ja) * | 2010-09-22 | 2014-10-08 | 株式会社オティックス | 可変動弁機構 |
CN105604634B (zh) | 2015-12-24 | 2018-04-20 | 广州汽车集团股份有限公司 | 连续可变气门升程***及汽车 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE727987C (de) * | 1941-01-07 | 1942-11-16 | Messer & Co G M B H | Waehrend des Umlaufens verstellbare Steuernocken |
GB798135A (en) * | 1956-04-25 | 1958-07-16 | Nsu Werke Ag | An internal combustion engine with an oscillating overhead camshaft |
DE2950565C2 (de) * | 1979-12-13 | 1984-02-02 | Mannesmann AG, 4000 Düsseldorf | Verfahren zum Herstellen eines Leichtradsatzes für Schienenfahrzeuge |
JP3268827B2 (ja) * | 1992-07-03 | 2002-03-25 | マツダ株式会社 | エンジンのバルブタイミング制御装置 |
DE19629349A1 (de) * | 1996-07-20 | 1998-01-22 | Dieter Dipl Ing Reitz | Ventiltrieb und Zylinderkopf einer Brennkraftmaschine |
JP3982917B2 (ja) * | 1997-08-08 | 2007-09-26 | 株式会社日立製作所 | 内燃機関の可変動弁装置 |
US6019076A (en) * | 1998-08-05 | 2000-02-01 | General Motors Corporation | Variable valve timing mechanism |
AU9362798A (en) * | 1998-08-10 | 2000-03-06 | Ruben Helmin | Variable lift and timing system for valves |
US6295958B2 (en) * | 2000-01-19 | 2001-10-02 | Delphi Technologies, Inc. | Linkless variable valve actuation mechanism |
JP3799944B2 (ja) * | 2000-03-21 | 2006-07-19 | トヨタ自動車株式会社 | 内燃機関の可変動弁機構および吸気量制御装置 |
-
2001
- 2001-08-08 DE DE10139043A patent/DE10139043A1/de not_active Withdrawn
-
2002
- 2002-07-03 DE DE50200248T patent/DE50200248D1/de not_active Expired - Lifetime
- 2002-07-03 EP EP02014670A patent/EP1288451B1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP1288451A1 (de) | 2003-03-05 |
DE50200248D1 (de) | 2004-03-25 |
DE10139043A1 (de) | 2003-02-20 |
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