DE3521539A1 - Device for a cam-controlled reciprocating piston engine - Google Patents
Device for a cam-controlled reciprocating piston engineInfo
- Publication number
- DE3521539A1 DE3521539A1 DE19853521539 DE3521539A DE3521539A1 DE 3521539 A1 DE3521539 A1 DE 3521539A1 DE 19853521539 DE19853521539 DE 19853521539 DE 3521539 A DE3521539 A DE 3521539A DE 3521539 A1 DE3521539 A1 DE 3521539A1
- Authority
- DE
- Germany
- Prior art keywords
- rocker arm
- compensating part
- cams
- cam
- camshaft
- 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.)
- Withdrawn
Links
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
- 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
- F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
- F01L13/0047—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other
-
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Die Erfindung betrifft eine Nockenwellenanordnung gemäß dem Oberbegriff des Patentanspruches 1..The invention relates to a camshaft arrangement according to the preamble of claim 1 ..
Betrachtet man eine Viertakt-Brennkraftmaschine, so bestimmt bekanntlich die Form der Ein- und Auslaßnocken in starkem Maße den Drehmomentverlauf, die Nenndrehzahl, den Leerlauf, den Kraftstoffverbrauch und die Abgasemission der Maschine. Maßgebend für diese Punkte sind die Öffnungszeiten der Ein- und Auslaßventile in Bezug auf die Totpunkte der Bewegungen der Kolben der Maschine, woraus sich die durch die Nocken zu verwirklichenden Steuerzeiten der Ventile ergeben. Allgemein kann gesagt werden, daß mit engen Einlaßnocken Steuerzeiten realisiert werden können, die einen guten Liefergrad bei kleinen Drehzahlen (elastischer Motor) gewährleisten. Mit einem breiten Nocken erzielt man jedoch höhere Leistungen bei hohen Drehzahlen, muß dann allerdings einen Drehmomentverlust bei niedrigen Drehzahlen in Kauf nehmen. Schon aus diesen Darlegungen folgt anschaulich, daß Ein- und Auslaßnocken konstanter Breite und konstanter Spreizung nur einen Kompromiß für die verschiedenen Drehzahlen und Lasten der Maschine darstellen können.If a four-stroke internal combustion engine is considered, then it is determined is well known, the shape of the inlet and outlet cams to a large extent the torque curve, the rated speed, the idling, the Fuel consumption and the exhaust emissions of the machine. The opening times of entry and exit are decisive for these points Exhaust valves in relation to the dead centers of the movements of the pistons of the machine, which gives rise to those to be realized by the cams Control times of the valves result. In general it can be said that control times are achieved with narrow intake cams that ensure a good degree of delivery at low speeds (elastic motor). With a broad However, cams are used to achieve higher performance at high speeds, but then there is a loss of torque at low speeds Accept speeds. Already from these explanations it clearly follows that inlet and outlet cams of constant width and constant spread only a compromise for the different Can represent speeds and loads of the machine.
Daher ist, um einen optimalen Motor mit hohem Drehmoment bei niedrigen und hohen Drehzahlen, sowie niedrigem Leerlauf, Kraftstoffverbrauch und geringe Abgasemission zu erhalten, eine variable Nockenwelle erforderlich, welche die Steuerzeiten über ein elektronisches Steuergerät und z.B. ein elektrohydraulisches Stellglied oder Regelmotor regelt.Therefore, in order to have an optimal engine with high torque at low and high speeds, as well as low idle, To obtain fuel consumption and low exhaust emissions, a variable camshaft is required, which controls the valve timing an electronic control unit and, for example, an electro-hydraulic actuator or regulating motor.
Um variable Steuerzeiten mit einer Nockenwelle zu erzielen, ist bei dieser Erfindung eine Konstruktion mit zwei nebeneinanderliegenden Nocken erforderlich, welche in der An- und Abstiegsflanke verschieden sind. Zwischen den beiden Nocken (2a und 2b) In order to achieve variable timing with one camshaft, this invention is a construction with two adjacent one another Cams are required, which are different in the rising and falling edge. Between the two cams (2a and 2b)
- 4 - Erich Schmid, 14.6.1985- 4 - Erich Schmid, June 14, 1985
und dem Ventilstößel (4) Fig. 1 und 2 oder dem Kipphebel (3) Fig. 5, 6 und 7 ist ein Ausgleichsteil (5), welches axial verschoben werden kann, somit kann je nach Position des Ausgleichsteils (5) der Ventilstößel (4) Fig. 1 und 2 oder der Kipphebel (3) Fig. 5, 6 und 7 von den Nocken (2a und 2b) beeinflußt werden. Bei Figur 1 und 2 zum Beispiel ist der Ventilstößel (4) stark von der Nocke (2b) beeinflußt, verschiebt man das Ausgleichsteil (5) zum Beispiel in die Mitte der zwei Nocken (2a und 2b), so wird der Ventilstößel (4) von beiden Nocken (2a und 2b) beeinflußt, oder schiebt es auf die Gegenposition, so beeinflußt die Nocke (2a) mehr den Ventilstößel (4) Fig. 1 und 2 oder den Kipphebel (3) Fig. 5, 6 und 7, somit kann man die Steuerzeiten beeinflußen zwischen dem breiten Nocken (2b) und dem engen Nocken (2a).and the valve tappet (4) Fig. 1 and 2 or the rocker arm (3) Fig. 5, 6 and 7 is a compensating part (5), which axially can be moved, thus depending on the position of the compensating part (5) of the valve stem (4) Fig. 1 and 2 or the Rocker arm (3) Fig. 5, 6 and 7 can be influenced by the cams (2a and 2b). In Figures 1 and 2, for example, is the valve stem (4) strongly influenced by the cam (2b), one moves the compensating part (5), for example, in the middle of the two Cams (2a and 2b), the valve tappet (4) is influenced by both cams (2a and 2b), or pushes it to the opposite position, so the cam (2a) affects more the valve tappet (4) Fig. 1 and 2 or the rocker arm (3) Fig. 5, 6 and 7, thus you can influence the timing between the wide cam (2b) and the narrow cam (2a).
Das Ausgleichsteil (5), welches im Nockengrundkreis parallel zur Längsrichtung der Nockenwelle steht, verändert seine Lage diagonal, wenn es in die Nockenan- und -Abstiegskurve kommt; um hierbei eine formschlüssige Auflage der Anlaufkuppen (7) an der Nockenfläche (2a und 2b) zu bekommen, sind die Anlaufkuppen (7) mit den Schwenklagern (6) verbunden, welche in dem Ausgleichsteil (5) gelagert sind.(Die Anlaufkuppe (7) und das Schwenklager (6) ist ein Teil.)The compensation part (5), which is parallel to the longitudinal direction of the camshaft in the cam base circle, changes its position diagonally when it comes into the cam rise and fall curve; in order to achieve a form-fitting support of the start-up tips (7) To get on the cam surface (2a and 2b), the start-up tips (7) are connected to the pivot bearings (6), which are in the Compensating part (5) are stored (the start-up dome (7) and the swivel bearing (6) are one part.)
Die Übertragung der Bewegungen von der Nockenwelle (2) über das Ausgleichsteil (5) auf den Ventilstößel (4) bei Fig. 1 und 2 zum Beispiel über eine längere Anlaufkuppe (11) und bei Fig. 5, 6 und 7 erfolgen die Bewegungen von der Nockenwelle (2) über das Ausgleichsteil (5) zum Kipphebel (3) zum Beispiel von einer Gleitfläche (20) auf dem Ausgleichsteil (5) auf die Halbkugel (19), welche in einer Pfanne im Kipphebel (3) gelagert ist. Die Halbkugel (19) gleicht die diagonalen Bewegungen des Ausgleichsteils (5) im Bereich der An- und Abstiegsflanke der Nockenwelle (2) zum Kipphebel (3) aus.The transmission of the movements from the camshaft (2) via the compensating part (5) to the valve tappet (4) in Fig. 1 and 2, for example, via a longer start-up dome (11) and in Figs. 5, 6 and 7 the movements are made by the camshaft (2) Via the compensating part (5) to the rocker arm (3), for example from a sliding surface (20) on the compensating part (5) to the hemisphere (19), which is mounted in a pan in the rocker arm (3). The hemisphere (19) resembles the diagonal movements of the Compensating part (5) in the area of the rising and falling flank of the camshaft (2) to the rocker arm (3).
- 5 - Erich Schmid, 14.6.1985- 5 - Erich Schmid, June 14, 1985
Bei Fig. 1, 2, 3 und 4 erfolgt die Verschiebung des Ausgleichsteils (5) über den Lagerzapfen (10) des Schlepphebels (8), welcher auf der Schlepphebelwelle (9) gelagert und zum Beispiel durch Seegeringe (21) und Anlaufscheiben (22) axial fixiert ist, so daß der Schlepphebel (8) den axialen Verschiebungen folgen muß. Das Ausgleichsteil (5) kann die diagonalen Bewegungen während dem Ablauf auf den An- und Abstiegsflanken der Nockenwelle (2) durch die Lagerung im Ausgleichszapfen (10) am Schlepphebel (8) ausführen. Die Schlepphebelwelle (9) wird zum Beispiel über eine elektronische Steuerung und einem elektro-hydraulischen Stellglied oder einem Regelmotor in die jeweilige gewünschte Position gebracht.In Fig. 1, 2, 3 and 4, the displacement of the compensation part takes place (5) over the bearing pin (10) of the rocker arm (8), which is mounted on the rocker arm shaft (9) and to Example by circlips (21) and thrust washers (22) is axially fixed so that the rocker arm (8) the axial displacements must follow. The compensation part (5) can control the diagonal movements during the sequence on the rising and falling flanks the camshaft (2) through the bearing in the compensation pin (10) on the rocker arm (8). The rocker arm shaft (9) is for example via an electronic control and an electro-hydraulic actuator or brought into the respective desired position by a control motor.
Bei Fig. 5, 6, 7 und 8 wird das Ausgleichsteil (5) durch eine Welle (14) in der Kipphebelhohlwelle (13) in die jeweilige gewünschte Position gebracht, indem die Welle· (14) in der Kipphebelhohlwelle (13) axial verschoben werden kann und die beiden Verschiebelager (12) durch die Mitnehmer (15), welche durch einen Durchtritt (16) in der Kipphebelhohlwelle (13) in einer Nut (17) im Verschiebelager (12) diese zu führen. Die Verschiebelager 12 sitzen axial und radial freilaufend auf der Kipphebelhohlwelle (13) und sind mit dem Ausgleichsteil (5) durch zum Beispiel mit einer Art Federblätter (18) mit den Verschiebelagern (12) verbunden, so daß das Ausgleichsteil (5) den Verschiebelagern (12) axial folgt und die radialen Schwingbewegungen ausführen kann.In Fig. 5, 6, 7 and 8, the compensation part (5) is through a The shaft (14) is brought into the desired position in the rocker arm hollow shaft (13) by sliding the shaft (14) in the Rocker arm hollow shaft (13) can be moved axially and the two sliding bearings (12) by the driver (15), which to guide them through a passage (16) in the rocker arm hollow shaft (13) in a groove (17) in the sliding bearing (12). the Sliding bearings 12 sit axially and radially free-running the rocker arm hollow shaft (13) and are connected to the compensating part (5) by for example with a kind of spring leaves (18) with the sliding bearings (12), so that the compensating part (5) the Displacement bearings (12) axially follows and the radial oscillating movements can perform.
Die Federblätter (18) gleichen auch die diagonalen Bewegungen des Ausgleichsteils (5) während dem Ablauf auf den An- und Ablaufflanken der Nockenwelle (2) aus. Der Kipphebel (3) ist auf der Kipphebelwelle (13) zum Beispiel mit Seegeringen und Anlaufscheiben axial fixiert.The spring leaves (18) also equal the diagonal movements of the compensating part (5) during the process on the leading and trailing edges the camshaft (2). The rocker arm (3) is on the rocker arm shaft (13), for example with circlips and thrust washers axially fixed.
Die Welle (14) wird z.B. über eine elektronische Steuerung und einem elektro-hydraulischen Stellglied oder einen Regelmotor in die jeweilige gewünschte Position gebracht.The shaft (14) is e.g. via an electronic control and an electro-hydraulic actuator or a regulating motor brought into the respective desired position.
Claims (6)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19853521539 DE3521539A1 (en) | 1985-06-15 | 1985-06-15 | Device for a cam-controlled reciprocating piston engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19853521539 DE3521539A1 (en) | 1985-06-15 | 1985-06-15 | Device for a cam-controlled reciprocating piston engine |
Publications (1)
Publication Number | Publication Date |
---|---|
DE3521539A1 true DE3521539A1 (en) | 1986-12-18 |
Family
ID=6273392
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DE19853521539 Withdrawn DE3521539A1 (en) | 1985-06-15 | 1985-06-15 | Device for a cam-controlled reciprocating piston engine |
Country Status (1)
Country | Link |
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DE (1) | DE3521539A1 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0352580A1 (en) * | 1988-07-28 | 1990-01-31 | Krupp MaK Maschinenbau GmbH | Operating system of internal-combustion engine valves |
DE4124305A1 (en) * | 1991-07-23 | 1993-01-28 | Audi Ag | Valve drive, esp. intake valve, for IC engine - has cams, positioned mirror-fashion on camshaft and levers, moved together in opposite direction by pressure medium |
FR2694786A1 (en) * | 1992-08-12 | 1994-02-18 | Renault | Variable distribution device for modifying distribution of IC motor - has two cams of differing profiles on one shaft with rocker sliding counter spring loaded on control shaft to operate valve |
EP0750098A1 (en) * | 1995-06-22 | 1996-12-27 | Yamaha Hatsudoki Kabushiki Kaisha | Internal combustion engine and method for controlling the valve actuation |
US5785017A (en) * | 1995-04-12 | 1998-07-28 | Yamaha Hatsudoki Kabushiki Kaisha | Variable valve timing mechanism |
DE102006047293A1 (en) * | 2006-10-06 | 2008-04-10 | Schaeffler Kg | Valve drive for an internal combustion engine with displaceable space cam |
DE102014220385A1 (en) * | 2014-10-08 | 2015-10-29 | Schaeffler Technologies AG & Co. KG | Switchable valve drive of a reciprocating internal combustion engine |
DE102015204041A1 (en) * | 2015-03-06 | 2016-04-14 | Schaeffler Technologies AG & Co. KG | Sliding axle valve drive of an internal combustion engine |
-
1985
- 1985-06-15 DE DE19853521539 patent/DE3521539A1/en not_active Withdrawn
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0352580A1 (en) * | 1988-07-28 | 1990-01-31 | Krupp MaK Maschinenbau GmbH | Operating system of internal-combustion engine valves |
DE4124305A1 (en) * | 1991-07-23 | 1993-01-28 | Audi Ag | Valve drive, esp. intake valve, for IC engine - has cams, positioned mirror-fashion on camshaft and levers, moved together in opposite direction by pressure medium |
FR2694786A1 (en) * | 1992-08-12 | 1994-02-18 | Renault | Variable distribution device for modifying distribution of IC motor - has two cams of differing profiles on one shaft with rocker sliding counter spring loaded on control shaft to operate valve |
US5785017A (en) * | 1995-04-12 | 1998-07-28 | Yamaha Hatsudoki Kabushiki Kaisha | Variable valve timing mechanism |
US5809953A (en) * | 1995-04-12 | 1998-09-22 | Yamaha Hatsudoki Kabushiki Kaisha | Variable valve timing mechanism |
US5836274A (en) * | 1995-04-12 | 1998-11-17 | Yamaha Hatsudoki Kabushiki Kaisha | Multi valve engine with variable valve operation |
EP0750098A1 (en) * | 1995-06-22 | 1996-12-27 | Yamaha Hatsudoki Kabushiki Kaisha | Internal combustion engine and method for controlling the valve actuation |
DE102006047293A1 (en) * | 2006-10-06 | 2008-04-10 | Schaeffler Kg | Valve drive for an internal combustion engine with displaceable space cam |
DE102014220385A1 (en) * | 2014-10-08 | 2015-10-29 | Schaeffler Technologies AG & Co. KG | Switchable valve drive of a reciprocating internal combustion engine |
DE102015204041A1 (en) * | 2015-03-06 | 2016-04-14 | Schaeffler Technologies AG & Co. KG | Sliding axle valve drive of an internal combustion engine |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
8139 | Disposal/non-payment of the annual fee |