EP3161281A1 - Camshaft for the valve drive of an internal combustion engine with a variable valve opening duration - Google Patents

Camshaft for the valve drive of an internal combustion engine with a variable valve opening duration

Info

Publication number
EP3161281A1
EP3161281A1 EP15729484.4A EP15729484A EP3161281A1 EP 3161281 A1 EP3161281 A1 EP 3161281A1 EP 15729484 A EP15729484 A EP 15729484A EP 3161281 A1 EP3161281 A1 EP 3161281A1
Authority
EP
European Patent Office
Prior art keywords
cam
partial
outer shaft
shaft
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.)
Granted
Application number
EP15729484.4A
Other languages
German (de)
French (fr)
Other versions
EP3161281B1 (en
Inventor
Uwe Dietel
Bernd Mann
Michael Kunz
Martin Lehmann
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.)
Thyssenkrupp Dynamic Components Teccenter AG
Original Assignee
ThyssenKrupp Presta TecCenter AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ThyssenKrupp Presta TecCenter AG filed Critical ThyssenKrupp Presta TecCenter AG
Publication of EP3161281A1 publication Critical patent/EP3161281A1/en
Application granted granted Critical
Publication of EP3161281B1 publication Critical patent/EP3161281B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F01L1/34413—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 using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L13/0057—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 by splittable or deformable cams
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings

Definitions

  • the invention relates to a camshaft for an internal combustion engine according to the preamble of claim 1.
  • a camshaft comprises a hollow outer shaft and an inner shaft rotatably disposed concentrically within the outer shaft.
  • a first part cam of a cam is rotationally fixed on the outer shaft and a second part cam of the cam is rotatably connected to the inner shaft and rotatably mounted on the outer shaft.
  • Each sub-cam requires a minimum axial space, which is substantially as large as the space required by a cam of a non-adjustable camshaft. Since, however, at least two such partial cams are to be provided per valve, the total axial space required by the cams increases overall.
  • camshafts treated here are basically to be distinguished from those camshafts which exclusively include those cams whose contour can not be changed. Although such cams can also be held variably on the camshaft; However, this only allows the opening period to be changed but not changed in its duration.
  • the camshaft comprises an outer shaft and an inner shaft extending through the outer shaft.
  • the inner shaft is rotatably held to the outer shaft.
  • a cam is designed in several parts and has a first part cam and at least one second part cam. Either the first part cam or the at least one second part cam is connected rotationally fixed to the outer shaft; the other part cam, so the at least one second part cam or the first part cam, is rotationally connected to the inner shaft. It therefore does not matter which of the part cam with the outer shaft and which part of the cam is connected to the inner shaft.
  • a bearing inner ring of a shaft bearing is held on the outer shaft. Sliding bearings and rolling bearings come into consideration in particular as shaft bearings.
  • one of the at least one second partial cam now has an axial projection which forms at least part of the bearing inner ring.
  • the part of the bearing inner ring is in particular formed integrally with the second part cam.
  • a separate attachment of the bearing inner ring on the outer shaft can be omitted.
  • the bearing inner ring is designed in several parts; a further part of the bearing inner ring can be formed by a second part cam of an adjacent cam. It may result in a symmetrical arrangement.
  • This division results in short joining paths, which simplifies assembly.
  • the further part of the bearing inner ring can be formed by a one-piece, non-rotatably held on the outer shaft cam or bearing ring.
  • an axial gap which results between the two, in each case jointly forming a bearing inner ring part cam, axially aligned with a radial bore in the outer shaft.
  • the gap and the radial bore can serve as a radial lubricant channel between the inner region of the outer shaft and the bearing, in particular in the case of a sliding bearing.
  • the cam has a first part cam and two second part cam, wherein the first part cam is arranged axially between the two second part cam and one of the two second part cam forms the part of the bearing inner ring. It is particularly preferred if in this embodiment, the first Telnocken is rotatably connected to the inner shaft and the second part cam are rotatably connected to the outer shaft. In this case, only a partial cam must be rotatably connected in particular via a complex bolt construction with the inner shaft.
  • the middle part cam increases radially inwards, viewed in cross section, so that the contact surfaces of the outer part cam must "move” axially outward
  • the middle part cam increases radially inwards, viewed in cross section, so that the contact surfaces of the outer part cam must "move” axially outward
  • the cam has exactly one first part cam and exactly one second part cam.
  • the first part cam is arranged axially adjacent to the second part cam, the second part cam forms the part of the bearing inner ring.
  • FIG. 1 shows a cross section through a camshaft according to the invention of the first
  • Figure 2 shows a cross section through a camshaft according to the invention of the second
  • FIG. 3 shows a cross section through an alternative camshaft according to the invention of the second embodiment.
  • FIG. 4 shows a cross section through an alternative camshaft according to the invention of the first embodiment
  • FIG. 6 shows a cross section through a further unclaimed camshaft.
  • a camshaft 1 according to the invention for an internal combustion engine is shown in fragmentary cross-section.
  • the camshaft 1 comprises a hollow outer shaft 2 and a concentric within the outer shaft 2 by a twist angle of at most 35 °, preferably 20 ° to 30 °, rotatably mounted inner shaft 3.
  • the camshaft 1 comprises two cams 6 ', 6 ", the In this case, the first part cam 4 is rotatably connected to the inner shaft 4 and arranged rotatably on the outer shaft 2, while the second part cam 5 are held against rotation and displacement on the outer shaft 2.
  • Die Dreh- and displacement-resistant arrangement of the first partial cam 4 can be realized by conventional methods by means of a frictional and / or a positive and / or material-locking connection
  • the second partial cam 5 is connected in a rotationally fixed manner to the inner shaft 3 via a bolt 12.
  • This bolt 12 is shown in the sectional view Figure 1 is not visible, but this is in one of the following Fi still visible.
  • the two partial cams 4, 5 may have identical or different outer contours. Based on the relative rotational position between the inner shaft 3 and outer shaft 2, the relative orientation of the outer contours of the two partial cams 4, 5 can be adjusted to each other. If the radially highlighted regions of the outer contours of both partial cams are superimposed with one another in the circumferential direction of the camshaft, the opening duration of the associated valve is reduced. If the radially highlighted regions of the outer contours of both partial cams are offset relative to one another in the circumferential direction of the camshaft, the opening duration of the associated valve is increased.
  • the camshaft 1 is held by means of a sliding bearing 9 in a housing, not shown.
  • the plain bearing has a bearing outer ring 8 and a (in the case of Figure 1 multi-part) bearing inner ring 7.
  • a drag lever 13 is indicated by dashed lines.
  • the rocker arm 13 For interaction of the rocker arm 13 with the cam 6, the rocker arm must always rest on a predetermined minimum contact length (measured parallel to the camshaft axis A) on the cam 6 in order to increase the surface pressure to a permissible maximum value restrict.
  • Due to the multi-part design of the cam it is possible that the drag lever 13 is only in contact with one of the partial cams 4, 5.
  • This operating state is shown in FIG. 1, in which case only the first part cam 4 is in contact with the drag lever 13. Even in such a case, the maximum permissible surface pressure must not be exceeded. Consequently, both the first part cam and the second part cam 5 must each have a minimum length on the outer contour.
  • the multi-part cam 6 of such a variable camshaft basically requires significantly more axial space than a one-piece cam.
  • the dimension x in the figure 1 stands for the axial clearance between the cams.
  • each sub-cam requires a minimal abutment surface on the outer shaft and / or requires a certain axial length for receiving the bolt 12.
  • each partial cam requires a certain connection length l 2 on the outer shaft 2, wherein l 2 in this case is greater than. Therefore, the areas of the outer part cam 5, which are in contact with the outer shaft 2, move axially outward.
  • the sliding bearing claimed a predetermined slide bearing l 3 .
  • one of the two second partial cams 5 is now formed in one piece with the bearing inner ring 7 of the sliding bearing 9. It can be seen in the figure 1 that overlap so the areas of the required system l 2 of the partial cam on the outer shaft 2 with the length l 3 of the sliding bearing 9.
  • the invention results in a space-saving arrangement in the axial direction.
  • the first part cam 4 may also be the fixed part cam instead of the second part cam 5.
  • the second part cam 5 rotatably connected to the inner shaft 4 and rotatably arranged on the outer shaft 2, while the first part cam 4 is rotationally and non-displaceably connected to the outer shaft 2.
  • the camshaft is then mounted via one of the adjustable part cam 5.
  • a radial bore 10 is provided in the outer shaft 2, which is axially aligned with a gap 1 1, which results between two adjacently arranged part cam 5 and bearing inner ring parts 7. Through the bore 10 and the gap 1 1, a lubricant channel between the sliding bearing 8 and the gap is formed radially between the outer shaft 2 and the inner shaft 3.
  • Figure 2 shows an alternative embodiment, which is largely the embodiment of FIG
  • the second part cam 5 are fixedly connected to the outer shaft 2; the first part cam 4 are rotationally connected to the inner shaft 3.
  • the already mentioned bolt construction for the rotationally fixed connection of one of the partial cams with the inner shaft can be seen in FIG.
  • a bolt 12 is guided in each case by a slot-shaped, running transversely to the camshaft axis of rotation
  • the bolt 12 also engages positively in those partial cams, which is rotatably connected to the inner shaft, in this case the partial cam. 4
  • Figure 3 shows an alternative embodiment, which is largely the embodiment of FIG
  • the first part cam 4 are firmly connected to the outer shaft 2; the second part cam 5 are rotationally connected via a respective bolt 12 with the inner shaft 3 in the manner described above.
  • FIG. 3 a separate bearing bush 15 with one or more lubricant bores is provided radially between the inner shaft 3 and the outer shaft 2.
  • a separate bearing bush 15 with one or more lubricant bores is provided radially between the inner shaft 3 and the outer shaft 2.
  • Figure 4 shows an alternative embodiment, which largely corresponds to the embodiment of Figure 2.
  • the bearing inner ring 7 is on the one hand, as in Figure 1, formed by a Telnocken 5.
  • the inner ring is formed by a partial cam 5 separate bearing ring 17, which is not part of a cam.
  • the gap 1 1 is formed between the partial cam 5 and the bearing ring 17.
  • FIG. 5 shows an alternative not claimed. Shown are two one-piece cam 6 ', 6 ", which are always in all operating conditions in interaction with a respective rocker arm 13', 13". Both cams 6 form parts of the bearing inner ring 7.
  • the right cam 6 " is an adjusting cam which is non-rotatably connected to the inner shaft 3 through the bolt 12 and is rotatably held to the outer shaft 2.
  • the left cam 6 ' is a fixed cam which is non-rotatably connected to the outer shaft 2.
  • FIG. 6 shows an alternative not claimed. Shown are two one-piece cam 6 ', 6 ", which are always in all operating conditions in interaction with a respective rocker arm 13', 13".
  • the right cam 6 " is an adjusting cam
  • the left cam 6 ' is a fixed cam which is non-rotatably connected to the outer shaft 2 and assumes no function of the bearing 8.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a camshaft (1) for the valve drive of an internal combustion engine with a variable valve opening duration, comprising an outer shaft (2) and an inner shaft (3) which extends through the outer shaft (2). The inner shaft (3) is held in a rotatable manner relative to the outer shaft (2). A cam (6) is designed in multiple parts and has a first sub-cam (4) and at least one second sub-cam (5). Either the first sub-cam (4) or the at least one second sub-cam (5) is rotationally fixed to the outer shaft (2), and the respective other sub-cam (5, 4) is rotationally fixed to the inner shaft (3). An inner bearing ring (7) of a shaft bearing (9) is held on the outer shaft (2), and one of the second sub-cams (5) has an axial projection which forms at least one part of the inner bearing ring (7).

Description

Nockenwelle für den Ventiltrieb einer Brennkraftmaschine mit  Camshaft for the valve train of an internal combustion engine with
variierbarer Ventilöffnungsdauer  variable valve opening duration
B e s c h r e i b u n g Description
Die Erfindung betrifft eine Nockenwelle für eine Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1. The invention relates to a camshaft for an internal combustion engine according to the preamble of claim 1.
STAND DER TECHNIK STATE OF THE ART
Um eine Brennkraftmaschine unter verschiedenen Betriebsbedingungen stets möglichst optimal betreiben zu können sind aus dem Stand der Technik bereits verschiedenste Methoden bekannt. So ist die Variation der Ventilöffnungsdauer in der WO 201 1/032632 A1 beschrieben. Eine Nockenwelle umfasst eine hohle Außenwelle und eine konzentrisch innerhalb der Außenwelle verdrehbar angeordnete Innenwelle. Ein erster Teilnocken eines Nockens ist drehfest auf der Außenwelle und ein zweiter Teilnocken des Nockens ist drehfest mit der Innenwelle verbunden und drehbar auf der Außenwelle gelagert. Durch Verdrehung der beiden Teilnocken zueinander, bewirkt durch eine Verdrehung von Innen- und Außenwelle zueinander, ist die Nockenkontur des Nockens und damit die Ventilöffnungszeit entsprechend veränderbar. In order to operate an internal combustion engine always optimally under different operating conditions are already known from the prior art various methods. Thus, the variation of the valve opening duration is described in WO 201 1/032632 A1. A camshaft comprises a hollow outer shaft and an inner shaft rotatably disposed concentrically within the outer shaft. A first part cam of a cam is rotationally fixed on the outer shaft and a second part cam of the cam is rotatably connected to the inner shaft and rotatably mounted on the outer shaft. By rotation of the two partial cam to each other, caused by a rotation of the inner and outer shaft to each other, the cam contour of the cam and thus the valve opening time is changed accordingly.
Jeder Teilnocken erfordert einen minimalen axialen Bauraum, der im Wesentlichen so groß ist wie der Bauraum, den ein Nocken einer nicht verstellbaren Nockenwelle benötigt. Da aber pro Ventil nun zumindest zwei solcher Teilnocken vorzuhalten sind, erhöht sich insgesamt der von den Nocken benötigte axiale Bauraum. Each sub-cam requires a minimum axial space, which is substantially as large as the space required by a cam of a non-adjustable camshaft. Since, however, at least two such partial cams are to be provided per valve, the total axial space required by the cams increases overall.
Zu unterscheiden sind die hier behandelten Nockenwellen grundsätzlich von solchen Nockenwellen, die ausschließlich solche Nocken, umfassen, deren Kontur nicht veränderbar sind. Solche Nocken können zwar auch variabel an der Nockenwelle gehalten sein; hiermit lässt sich jedoch nur die Öffnungsperiode verschieben, aber nicht in ihrer Dauer verändern. OFFENBARUNG DER ERFINDUNG The camshafts treated here are basically to be distinguished from those camshafts which exclusively include those cams whose contour can not be changed. Although such cams can also be held variably on the camshaft; However, this only allows the opening period to be changed but not changed in its duration. DISCLOSURE OF THE INVENTION
Es ist daher die Aufgabe der vorliegenden Erfindung, eine verbesserte Nockenwelle der eingangs genannten Art zu schaffen, die sich insbesondere durch eine platzsparende Bauweise auszeichnet. It is therefore an object of the present invention to provide an improved camshaft of the type mentioned, which is characterized in particular by a space-saving design.
Diese Aufgabe wird ausgehend von einer Nockenwelle für den Ventiltrieb einer Brennkraftmaschine mit variierbarer Ventilöffnungsdauer gemäß dem Oberbegriff des Anspruchs 1 in Verbindung mit dem kennzeichnenden Merkmalen gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben. This object is achieved on the basis of a camshaft for the valve train of an internal combustion engine with variable valve duration according to the preamble of claim 1 in conjunction with the characterizing features. Advantageous developments of the invention are specified in the dependent claims.
Die erfindungsgemäße Nockenwelle umfasst eine Außenwelle und eine sich durch die Außenwelle erstreckenden Innenwelle. Die Innenwelle ist drehbar zur Außenwelle gehalten. Ein Nocken ist mehrteilig ausgebildet und weist einen ersten Teilnocken und zumindest einen zweiten Teilnocken auf. Entweder der erste Teilnocken oder der zumindest eine zweite Teilnocken ist mit der Außenwelle verdrehfest verbunden; der jeweils andere Teilnocken, also der zumindest eine zweite Teilnocken bzw. der erste Teilnocken, ist verdrehfest mit der Innenwelle verbunden. Es kommt folglich nicht darauf an, welcher der Teilnocken mit der Außenwelle und welcher der Teilnocken mit der Innenwelle verbunden ist. Auf der Außenwelle ist ein Lagerinnenring eines Wellenlagers gehalten. Als Wellenlager kommen insbesondere Gleitlager und Wälzlager in Betracht. Erfindungsgemäß weist nun einer der zumindest einen zweiten Teilnocken einen axialen Ansatz auf, der zumindest einen Teil des Lagerinnenrings ausbildet. The camshaft according to the invention comprises an outer shaft and an inner shaft extending through the outer shaft. The inner shaft is rotatably held to the outer shaft. A cam is designed in several parts and has a first part cam and at least one second part cam. Either the first part cam or the at least one second part cam is connected rotationally fixed to the outer shaft; the other part cam, so the at least one second part cam or the first part cam, is rotationally connected to the inner shaft. It therefore does not matter which of the part cam with the outer shaft and which part of the cam is connected to the inner shaft. On the outer shaft, a bearing inner ring of a shaft bearing is held. Sliding bearings and rolling bearings come into consideration in particular as shaft bearings. According to the invention, one of the at least one second partial cam now has an axial projection which forms at least part of the bearing inner ring.
Für die Verbindung des Teilnockens als auch des Lagerinnenrings mit der Außenwelle dient nun der Teilnocken. Aufgrund dieser Funktionsintegration lässt sich axialer Bauraum einsparen. Dies ist insbesondere bei den gattungsgemäßen Verstellnocken von Vorteil, da diese per se einen recht großen axialen Bauraum erfordern, wie anhand des Ausführungsbeispiels noch näher erläutert wird. Der Teil des Lagerinnenrings ist dabei insbesondere einstückig mit dem zweiten Teilnocken ausgebildet. Eine separate Befestigung des Lagerinnenrings an der Außenwelle kann entfallen. Vorzugsweise ist der Lagerinnenring mehrteilig ausgebildet; ein weiterer Teil des Lagerinnenrings ist kann durch einen zweiten Teilnocken eines benachbarten Nockens ausgebildet. Es kann sich so eine symmetrische Anordnung ergeben. Die zwei axial benachbarten Teilnocken, jeweils unterschiedlicher Nocken, bilden so gemeinsam den Lagerinnenring aus. Durch diese Teilung ergeben sich kurze Fügewege, was die Montage vereinfacht. Alternativ kann der weitere Teil des Lagerinnenrings durch einen einteiligen, drehfest auf der Außenwelle gehaltenen Nocken oder Lagerring ausgebildet werden. For the connection of the part cam and the bearing inner ring with the outer shaft is now the part cam. Due to this functional integration, axial space can be saved. This is particularly advantageous in the case of the generic adjusting cams, since they require a rather large axial installation space per se, as will be explained in more detail with reference to the exemplary embodiment. The part of the bearing inner ring is in particular formed integrally with the second part cam. A separate attachment of the bearing inner ring on the outer shaft can be omitted. Preferably, the bearing inner ring is designed in several parts; a further part of the bearing inner ring can be formed by a second part cam of an adjacent cam. It may result in a symmetrical arrangement. The two axially adjacent partial cams, each different cams, so together form the bearing inner ring. This division results in short joining paths, which simplifies assembly. Alternatively, the further part of the bearing inner ring can be formed by a one-piece, non-rotatably held on the outer shaft cam or bearing ring.
Vorzugsweise ist ein axialer Spalt, der sich zwischen den beiden, jeweils gemeinsam einen Lagerinnenring bildenden Teilnocken ergibt, axial ausgerichtet mit einer Radialbohrung in der Außenwelle. Gemeinsam können der Spalt und die Radialbohrung als radialer Schmiermittelkanal zwischen dem Innenbereich der Außenwelle und der Lager, insbesondere im Falle eines Gleitlagers, dienen. Gleiches gilt für die im vorigen Absatz angesprochenen Alternativen, so dass sich der Spalt zwischen einem Teilnocken und dem Festnocken bzw. dem Lagerring ergibt. Preferably, an axial gap, which results between the two, in each case jointly forming a bearing inner ring part cam, axially aligned with a radial bore in the outer shaft. Together, the gap and the radial bore can serve as a radial lubricant channel between the inner region of the outer shaft and the bearing, in particular in the case of a sliding bearing. The same applies to the alternatives mentioned in the previous paragraph, so that the gap between a partial cam and the fixed cam or the bearing ring results.
In einer ersten bevorzugten Ausgestaltung weist der Nocken einen ersten Teilnocken und zwei zweite Teilnocken auf, wobei der erste Teilnocken axial zwischen den beiden zweiten Teilnocken angeordnet ist und einer der beiden zweiten Teilnocken den Teil des Lagerinnenrings ausbildet. Besonders bevorzugt ist es, wenn in dieser Ausgestaltung der erste Telnocken mit der Innenwelle drehfest verbunden ist und die zweiten Teilnocken mit der Außenwelle drehfest verbunden sind. In diesem Fall muss nur ein Teilnocken insbesondere über eine aufwendige Bolzenkonstruktion mit der Innenwelle drehfest verbunden werden. In a first preferred embodiment, the cam has a first part cam and two second part cam, wherein the first part cam is arranged axially between the two second part cam and one of the two second part cam forms the part of the bearing inner ring. It is particularly preferred if in this embodiment, the first Telnocken is rotatably connected to the inner shaft and the second part cam are rotatably connected to the outer shaft. In this case, only a partial cam must be rotatably connected in particular via a complex bolt construction with the inner shaft.
Grundsätzlich ist eine solche Aufteilung in drei Teilnocken bevorzugt, da so ein Mitnehmer, insbesondere ein Schlepp- oder Kipphebel, stets zentriert auf dem Nocken anliegt, nämlich entweder an dem innenliegenden ersten Teilnocken alleine, an den beiden außenliegenden Teilnocken gemeinsam oder an allen drei Teilnocken gemeinsam. Bei allen drei Betriebszuständen können die Kräfte axial zentral auf den Mitnehmer übertragen werden. Allerdings zeichnet sich diese Ausgestaltung durch einen großen axialen Bauraumbedarf der drei Teilnocken aus, da diese allesamt auf der Außenwelle angebracht werden. Dabei erfordert jeder Teilnocken eine gewisse Mindestauflagefläche an der Außenfläche. Insbesondere der mittlere Teilnocken vergrößert sich dabei radial nach innen, im Querschnitt betrachtet, so dass auch die Anlageflächen der äußeren Teilnocken axial nach außen„wandern" müssen. Zudem erfordert die Bolzenkonstruktion zur drehfesten Verbindung mit der Innenwelle eine gewisse Mindestbreite. Daher muss die Schulter des Teilnockens stets um ein gewisses Maß axial betrachtet länger sein, als der Durchmesser des Bolzens. Dass nun einer der äußeren Teilnocken zugleich den Lagerinnenring, zumindest teilweise, ausbildet, reduziert den Platzbedarf, der von diesem Teilnocken und dem Lagerinnenring gemeinsam auf der Außenwelle beansprucht wird. Basically, such a division into three sub-cams is preferred, since such a driver, in particular a towing or rocker arm, always centered on the cam is applied, either on the inner first part cam alone, on the two outer part cam together or on all three sub-cams together , In all three operating conditions, the forces can be transferred axially centrally on the driver. However, this configuration is characterized by a large axial space requirement of the three sub-cams, since they are all mounted on the outer shaft. Each partial cam requires a certain minimum contact surface on the outside surface. In particular, the middle part cam increases radially inwards, viewed in cross section, so that the contact surfaces of the outer part cam must "move" axially outward The fact that one of the outer partial cams at the same time forms the bearing inner ring, at least partially, reduces the space required by this partial cam and the bearing inner ring together on the outer shaft.
In einer zweiten bevorzugten Ausgestaltung weist der Nocken genau einen ersten Teilnocken und genau einen zweiten Teilnocken auf. Der erste Teilnocken ist axial benachbart zum zweiten Teilnocken angeordnet, der zweite Teilnocken bildet den Teil des Lagerinnenrings aus. Zwar kann diese Ausgestaltung mit Kippmomenten auf den Schlepphebel einhergehen; andererseits kann aufgrund der geringeren Anzahl an Teilnocken insgesamt der durch die Teilnocken benötigte axiale Bauraum nochmals verringert werden. In a second preferred embodiment, the cam has exactly one first part cam and exactly one second part cam. The first part cam is arranged axially adjacent to the second part cam, the second part cam forms the part of the bearing inner ring. Although this design can go along with tilting moments on the drag lever; On the other hand, due to the smaller number of partial cams in total, the axial space required by the partial cams can be further reduced.
BEVORZUGTES AUSFÜHRUNGSBEISPIEL DER ERFINDUNG PREFERRED EMBODIMENT OF THE INVENTION
Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt: Further, measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS. It shows:
Figur 1 einen Querschnitt durch eine erfindungsgemäße Nockenwelle der ersten 1 shows a cross section through a camshaft according to the invention of the first
Ausgestaltung;  design;
Figur 2 einen Querschnitt durch eine erfindungsgemäße Nockenwelle der zweiten  Figure 2 shows a cross section through a camshaft according to the invention of the second
Ausgestaltung;  design;
Figur 3 einen Querschnitt durch eine alternative erfindungsgemäße Nockenwelle der zweiten Ausgestaltung.  3 shows a cross section through an alternative camshaft according to the invention of the second embodiment.
Figur 4 einen Querschnitt durch eine alternative erfindungsgemäße Nockenwelle der ersten Ausgestaltung;  FIG. 4 shows a cross section through an alternative camshaft according to the invention of the first embodiment;
Figur 5 einen Querschnitt durch eine nicht beanspruchte Nockenwelle,  5 shows a cross section through an unclaimed camshaft,
Figur 6 einen Querschnitt durch eine weitere nicht beanspruchte Nockenwelle. In der Figur 1 ist eine erfindungsgemäße Nockenwelle 1 für eine Brennkraftmaschine ausschnittsweise im Querschnitt gezeigt. Die Nockenwelle 1 umfasst eine hohle Außenwelle 2 sowie eine konzentrisch innerhalb der Außenwelle 2 um einen Verdrehwinkel von insbesondere maximal 35°, vorzugsweise 20° bis 30°, verdrehbar gelagert angeordnete Innenwelle 3. Die Nockenwelle 1 umfasst zwei Nocken 6', 6", die mehrere gegeneinander verdrehbare Teilnocken 4, 5 aufweisen. Dabei ist der erste Teilnocken 4 drehfest mit der Innenwelle 4 verbunden und verdrehbar auf der Außenwelle 2 angeordnet, während die zweiten Teilnocken 5 verdreh- und verschiebefest auf der Außenwelle 2 gehalten sind. Dabei kann die dreh- und verschiebefeste Anordnung des ersten Teilnockens 4 über herkömmliche Verfahren mittels einer kraftschlüssigen und/oder einer formschlüssigen und/oder stoffschlüssigen Verbindung realisiert sein. Der zweite Teilnocken 5 ist über einen Bolzen 12 drehfest mit der Innenwelle 3 verbunden. Dieser Bolzen 12 ist in der Schnittdarstellung nach Figur 1 nicht erkennbar; dies wird aber in einer der nachfolgenden Figuren noch ersichtlich. 6 shows a cross section through a further unclaimed camshaft. In the figure 1, a camshaft 1 according to the invention for an internal combustion engine is shown in fragmentary cross-section. The camshaft 1 comprises a hollow outer shaft 2 and a concentric within the outer shaft 2 by a twist angle of at most 35 °, preferably 20 ° to 30 °, rotatably mounted inner shaft 3. The camshaft 1 comprises two cams 6 ', 6 ", the In this case, the first part cam 4 is rotatably connected to the inner shaft 4 and arranged rotatably on the outer shaft 2, while the second part cam 5 are held against rotation and displacement on the outer shaft 2. Die Dreh- and displacement-resistant arrangement of the first partial cam 4 can be realized by conventional methods by means of a frictional and / or a positive and / or material-locking connection The second partial cam 5 is connected in a rotationally fixed manner to the inner shaft 3 via a bolt 12. This bolt 12 is shown in the sectional view Figure 1 is not visible, but this is in one of the following Fi still visible.
Die beiden Teilnocken 4, 5 können identische oder zueinander abweichende Außenkonturen aufweisen. Anhand der relativen Verdrehstellung zwischen Innenwelle 3 und Außenwelle 2 kann die relative Ausrichtung der Außenkonturen der beiden Teilnocken 4, 5 zueinander gezielt eingestellt werden. Werden die radial hervorgehobenen Bereiche der Außenkonturen beider Teilnocken in Umfangsrichtung der Nockwelle miteinander überlagert, so wird die Öffnungsdauer des zugehörigen Ventils reduziert. Werden die radial hervorgehobenen Bereiche der Außenkonturen beider Teilnocken in Umfangsrichtung der Nockwelle versetzt zueinander angeordnet, so wird die Öffnungsdauer des zugehörigen Ventils erhöht.  The two partial cams 4, 5 may have identical or different outer contours. Based on the relative rotational position between the inner shaft 3 and outer shaft 2, the relative orientation of the outer contours of the two partial cams 4, 5 can be adjusted to each other. If the radially highlighted regions of the outer contours of both partial cams are superimposed with one another in the circumferential direction of the camshaft, the opening duration of the associated valve is reduced. If the radially highlighted regions of the outer contours of both partial cams are offset relative to one another in the circumferential direction of the camshaft, the opening duration of the associated valve is increased.
Die Nockenwelle 1 wird mittels eines Gleitlagers 9 in einem nicht dargestellten Gehäuse gehalten. Das Gleitlager weist einen Lageraußenring 8 sowie einen (im Fall der Figur 1 mehrteiligen) Lagerinnenring 7 auf. The camshaft 1 is held by means of a sliding bearing 9 in a housing, not shown. The plain bearing has a bearing outer ring 8 and a (in the case of Figure 1 multi-part) bearing inner ring 7.
In Figur 1 ist ein Schlepphebel 13 gestrichelt angedeutet. Zur Interaktion des Schlepphebels 13 mit dem Nocken 6 muss der Schlepphebel stets auf einer vorgegebenen Mindestkontaktlänge (gemessen parallel zur Nockwellenachse A) am Nocken 6 anliegen, um die Flächenpressung auf ein zulässigen Maximalwert zu beschränken. Aufgrund der mehrteiligen Ausgestaltung des Nockens ist es aber möglich, dass der Schlepphebel 13 nur mit einem der Teilnocken 4, 5 in Kontakt ist. Dieser Betriebszustand ist Figur 1 gezeigt, wobei hier nur der erste Teilnocken 4 mit dem Schlepphebel 13 in Kontakt ist. Auch in einem solchen Fall darf die maximal zulässige Flächenpressung nicht überschritten werden. Folglich müssen sowohl der erste Teilnocken als auch die zweiten Teilnocken 5 zusammen jeweils eine Mindestlänge an der Außenkontur aufweisen. Somit beansprucht der mehrteilige Nocken 6 einer solchen variablen Nockenwelle grundsätzlich deutlich mehr axialen Bauraum als ein einteiliger Nocken. Die Dimension x in der Figur 1 steht für den axialen Freigang zwischen den Nocken. In Figure 1, a drag lever 13 is indicated by dashed lines. For interaction of the rocker arm 13 with the cam 6, the rocker arm must always rest on a predetermined minimum contact length (measured parallel to the camshaft axis A) on the cam 6 in order to increase the surface pressure to a permissible maximum value restrict. Due to the multi-part design of the cam, it is possible that the drag lever 13 is only in contact with one of the partial cams 4, 5. This operating state is shown in FIG. 1, in which case only the first part cam 4 is in contact with the drag lever 13. Even in such a case, the maximum permissible surface pressure must not be exceeded. Consequently, both the first part cam and the second part cam 5 must each have a minimum length on the outer contour. Thus, the multi-part cam 6 of such a variable camshaft basically requires significantly more axial space than a one-piece cam. The dimension x in the figure 1 stands for the axial clearance between the cams.
Ferner ist zu erkennen, dass sich der Querschnitt des ersten Teilnockens 4 radial nach innen konisch vergrößert, also eine Art Schulter 16 ausbildet. Dies ist erforderlich, da jeder Teilnocken eine minimale Anlagefläche auf der Außenwelle erfordert und/oder eine gewisse axiale Länge zur Aufnahme des Bolzens 12 erfordert. Durch jeden Teilnocken vergrößert sich folglich der Platzbedarf an der Außenwelle zur Anlage der Teilnocken. So bedarf jeder Teilnocken einer bestimmten Verbindungslänge l2 auf der Außenwelle 2, wobei l2 in diesem Fall größer ist als . Daher wandern auch die Bereiche der äußeren Teilnocken 5, die in Anlage mit der Außenwelle 2 sind, axial nach außen. Zudem beansprucht das Gleitlager eine vorgegebene Gleitlagerlänge l3. It can also be seen that the cross section of the first part cam 4 increases conically radially inwardly, that is, forms a kind of shoulder 16. This is necessary because each sub-cam requires a minimal abutment surface on the outer shaft and / or requires a certain axial length for receiving the bolt 12. As a result of each partial cam, the space requirement on the outer shaft for the attachment of the partial cams increases. Thus, each partial cam requires a certain connection length l 2 on the outer shaft 2, wherein l 2 in this case is greater than. Therefore, the areas of the outer part cam 5, which are in contact with the outer shaft 2, move axially outward. In addition, the sliding bearing claimed a predetermined slide bearing l 3 .
Erfindungsgemäß ist nun einer der beiden zweiten Teilnocken 5 einstückig mit dem Lagerinnenring 7 des Gleitlagers 9 ausgebildet. Es ist in der Figur 1 ersichtlich, dass sich so die Bereiche der erforderlichen Anlage l2 des Teilnockens auf der Außenwelle 2 mit der Länge l3 des Gleitlager 9 überlappen. So ergibt sich erfindungsgemäß eine bauraumsparende Anordnung in axialer Richtung. According to the invention, one of the two second partial cams 5 is now formed in one piece with the bearing inner ring 7 of the sliding bearing 9. It can be seen in the figure 1 that overlap so the areas of the required system l 2 of the partial cam on the outer shaft 2 with the length l 3 of the sliding bearing 9. Thus, the invention results in a space-saving arrangement in the axial direction.
In einer Variante kann auch der erste Teilnocken 4 der feste Teilnocken anstelle der zweiten Teilnocken 5 sein. Dann sind die zweiten Teilnocken 5 drehfest mit der Innenwelle 4 verbunden und verdrehbar auf der Außenwelle 2 angeordnet, während der erste Teilnocken 4 verdreh- und verschiebefest mit der Außenwelle 2 verbunden ist. Die Nockenwelle wird dann über einen der verstellbaren Teilnocken 5 gelagert. Ferner ist in der Außenwelle 2 eine Radialbohrung 10 vorgesehen, die axial ausgerichtet ist mit einem Spalt 1 1 , der sich zwischen zwei benachbart angeordneten Teilnocken 5 bzw. Lagerinnenringteilen 7 ergibt. Durch die Bohrung 10 und den Spalt 1 1 ist ein Schmiermittelkanal zwischen dem Gleitlager 8 und dem Zwischenraum radial zwischen der Außenwelle 2 und der Innenwelle 3 gebildet. In a variant, the first part cam 4 may also be the fixed part cam instead of the second part cam 5. Then, the second part cam 5 rotatably connected to the inner shaft 4 and rotatably arranged on the outer shaft 2, while the first part cam 4 is rotationally and non-displaceably connected to the outer shaft 2. The camshaft is then mounted via one of the adjustable part cam 5. Furthermore, a radial bore 10 is provided in the outer shaft 2, which is axially aligned with a gap 1 1, which results between two adjacently arranged part cam 5 and bearing inner ring parts 7. Through the bore 10 and the gap 1 1, a lubricant channel between the sliding bearing 8 and the gap is formed radially between the outer shaft 2 and the inner shaft 3.
Figur 2 zeigt eine alternative Ausgestaltung, die weitgehend der Ausgestaltung nach FigurFigure 2 shows an alternative embodiment, which is largely the embodiment of FIG
1 entspricht. Im Folgenden wird daher nur auf die Unterschiede eingegangen. Die Nocken 6 weisen lediglich einen zweiten Teilnocken 5 auf. Liegt der Schlepphebel 13 allerdings nur an einem der beiden Teilnocken 4, 5 an, so können sich Kippmomente nachteilig auf den Schlepphebel 13 auswirken. Daher ist eine Ausgestaltung nach Figur 1 bevorzugt, da dort der Schlepphebel 13 stets zentriert von dem Nocken 6 beaufschlagt wird. 1 corresponds. In the following, therefore, only the differences will be discussed. The cams 6 have only a second part cam 5. However, if the drag lever 13 only on one of the two partial cams 4, 5, so tilting moments can adversely affect the drag lever 13. Therefore, an embodiment of Figure 1 is preferred because there the cam follower 13 is always centered by the cam 6 is applied.
Die zweiten Teilnocken 5 sind fest mit der Außenwelle 2 verbunden; die ersten Teilnocken 4 sind verdrehfest mit der Innenwelle 3 verbunden. Zur drehfesten Verbindung der Innenwelle 3 mit dem entsprechenden Teilnocken 4 ist in Figur 2 die bereits angesprochene Bolzenkonstruktion zur drehfesten Verbindung eines der Teilnocken mit der Innenwelle zu erkennen. Ein Bolzen 12 ist jeweils durch eine schlitzförmige, quer zur Nockenwellendrehachse A verlaufende Ausnehmung 14 in der hohlen Außenwelle 2 geführt und insbesondere kraft- oder formschlüssig mit der Innenwelle 3 fest verbunden. Der Bolzen 12 greift ferner formschlüssig in denjenigen Teilnocken ein, der mit der Innenwelle drehfest verbunden ist, in diesem Fall der Teilnocken 4. The second part cam 5 are fixedly connected to the outer shaft 2; the first part cam 4 are rotationally connected to the inner shaft 3. For the rotationally fixed connection of the inner shaft 3 with the corresponding part cam 4, the already mentioned bolt construction for the rotationally fixed connection of one of the partial cams with the inner shaft can be seen in FIG. A bolt 12 is guided in each case by a slot-shaped, running transversely to the camshaft axis of rotation A recess 14 in the hollow outer shaft 2 and in particular non-positively or positively connected to the inner shaft 3. The bolt 12 also engages positively in those partial cams, which is rotatably connected to the inner shaft, in this case the partial cam. 4
Figur 3 zeigt eine alternative Ausgestaltung, die weitgehend der Ausgestaltung nach FigurFigure 3 shows an alternative embodiment, which is largely the embodiment of FIG
2 entspricht. Im Folgenden wird daher nur auf die Unterschiede eingegangen. Die ersten Teilnocken 4 sind fest mit der Außenwelle 2 verbunden; die zweiten Teilnocken 5 sind verdrehfest über jeweils eine Bolzen 12 mit der Innenwelle 3 auf die zuvor beschriebene Weise verbunden. 2 corresponds. In the following, therefore, only the differences will be discussed. The first part cam 4 are firmly connected to the outer shaft 2; the second part cam 5 are rotationally connected via a respective bolt 12 with the inner shaft 3 in the manner described above.
In der Ausgestaltung der Figur 3 ist radial zwischen der Innenwelle 3 und der Außenwelle 2 eine separate Lagerbuchse 15 mit ein oder mehreren Schmiermittelbohrungen vorgesehen. Eine solche Lagerbuchse 15 kann ohne weiters auch bei den Ausgestaltungen entsprechend der anderen Figuren Anwendung finden. Figur 4 zeigt eine alternative Ausgestaltung, die weitgehend der Ausgestaltung nach Figur 2 entspricht. Der Lagerinnenring 7 wird zum einen, wie auch in Figur 1 , durch einen Telnocken 5 gebildet. Zum anderen wird der Innenring durch einen zum Teilnocken 5 separaten Lagerring 17 gebildet, der nicht Bestandteil eines Nockens ist. Der Spalt 1 1 ist zwischen dem Teilnocken 5 und dem Lagerring 17 gebildet. In the embodiment of FIG. 3, a separate bearing bush 15 with one or more lubricant bores is provided radially between the inner shaft 3 and the outer shaft 2. Such a bushing 15 can be found without further use in the embodiments according to the other figures application. Figure 4 shows an alternative embodiment, which largely corresponds to the embodiment of Figure 2. The bearing inner ring 7 is on the one hand, as in Figure 1, formed by a Telnocken 5. On the other hand, the inner ring is formed by a partial cam 5 separate bearing ring 17, which is not part of a cam. The gap 1 1 is formed between the partial cam 5 and the bearing ring 17.
Figur 5 zeigt eine nicht beanspruchte Alternative. Gezeigt sind zwei einteilige Nocken 6', 6", die in allen Betriebszuständen stets in Wechselwirkung mit jeweils einem Schlepphebel 13', 13" sind. Beide Nocken 6 bilden Teile des Lagerinnenrings 7 aus. Der rechte Nocken 6" ist ein Verstellnocken, der mit der Innenwelle 3 durch den Bolzen 12 drehfest verbunden ist und verdrehbar zur Außenwelle 2 gehalten ist. Der linke Nocken 6' ist ein Festnocken, der drehfest mit der Außenwelle 2 verbunden ist. FIG. 5 shows an alternative not claimed. Shown are two one-piece cam 6 ', 6 ", which are always in all operating conditions in interaction with a respective rocker arm 13', 13". Both cams 6 form parts of the bearing inner ring 7. The right cam 6 "is an adjusting cam which is non-rotatably connected to the inner shaft 3 through the bolt 12 and is rotatably held to the outer shaft 2. The left cam 6 'is a fixed cam which is non-rotatably connected to the outer shaft 2.
Figur 6 zeigt eine nicht beanspruchte Alternative. Gezeigt sind zwei einteilige Nocken 6', 6", die in allen Betriebszuständen stets in Wechselwirkung mit jeweils einem Schlepphebel 13', 13" sind. Der rechte Nocken 6" ist ein Verstellnocken, der FIG. 6 shows an alternative not claimed. Shown are two one-piece cam 6 ', 6 ", which are always in all operating conditions in interaction with a respective rocker arm 13', 13". The right cam 6 "is an adjusting cam, the
mit der Innenwelle 3 durch den Bolzen 12 drehfest verbunden ist und verdrehbar zur Außenwelle 2 gehalten ist. Dieser Nocken bildet den Lagerinnenring 7 vollständig aus. Der linke Nocken 6' ist ein Festnocken, der drehfest mit der Außenwelle 2 verbunden ist und keinerlei Funktion des Lagers 8 übernimmt. is rotatably connected to the inner shaft 3 by the bolt 12 and is rotatably held to the outer shaft 2. This cam forms the bearing inner ring 7 completely. The left cam 6 'is a fixed cam which is non-rotatably connected to the outer shaft 2 and assumes no function of the bearing 8.
In den Ausführungsbeispielen wurde als Lager ausschließlich ein Gleitlager gezeigt. Die Erfindung ist bei Wälzlagern ebenfalls anwendbar. Bei den erfindungsgemäßen Ausführungsformen nach den Figuren 1 bis 4 bildete ein Teilnocken jeweils nur einen Teil des Lagerinnenrings aus. Es ist aber auch möglich, dass ein Teilnocken den Lagerinnenring vollständig ausbildet. Bez u g s ze i c h e n l i s te In the embodiments, only a plain bearing was shown as a bearing. The invention is also applicable to rolling bearings. In the embodiments according to the invention according to Figures 1 to 4 formed a partial cam each only a part of the bearing inner ring. But it is also possible that a partial cam fully forms the bearing inner ring. Bez ies zeenlis te
1 Nockenwelle 1 camshaft
2 Außenwelle  2 outer shaft
3 Innenwelle  3 inner shaft
4 erster Teilnocken  4 first part cams
5 zweiter Teilnocken  5 second part cams
6 Nocken  6 cams
7 Lagerinnenring  7 bearing inner ring
8 Lageraußenring  8 bearing outer ring
9 Gleitlager  9 plain bearings
10 Radialbohrung in Außenwelle  10 Radial bore in outer shaft
11 Spalt im Lagerinnenring  11 gap in the bearing inner ring
12 Bolzen  12 bolts
13 Schlepphebel  13 rocker arms
14 schlitzförmige Ausnehmung  14 slot-shaped recess
15 Lagerhülse  15 bearing sleeve
16 Schulter  16 shoulder
17 Lagerring l-i Kontaktlänge zwischen Schlepphebel und Nocken 17 Bearing ring l-i contact length between rocker arm and cam
12 Verbindungslänge zwischen Teilnocken und Außenwelle1 2 Connection length between partial cam and outer shaft
13 Gleitlagerlänge 1 3 plain bearing length

Claims

P a t e n t a n s p r ü c h e P a t e n t a n s r ü c h e
Nockenwelle (1 ) für den Ventiltrieb einer Brennkraftmaschine mit variierbarer Ventilöffnungsdauer, Camshaft (1) for the valve train of an internal combustion engine with variable valve opening duration,
mit einer Außenwelle (2) und mit einer sich durch die Außenwelle with an outer shaft (2) and with a through the outer shaft
(2) erstreckenden(2) extending
Innenwelle (3), wobei die Innenwelle Inner shaft (3), where the inner shaft
(3) drehbar zur Außenwelle (2) gehalten ist, wobei wenigsten ein Nocken (6") mehrteilig ausgebildet ist und einen ersten(3) is rotatably held relative to the outer shaft (2), with at least one cam (6 " ) being formed in several parts and a first
Teilnocken (4) und zumindest einen zweiten Teilnocken (5) aufweist, Has partial cams (4) and at least one second partial cam (5),
wobei entweder der erste Teilnocken (4) oder der zumindest eine zweite Teilnockenwherein either the first partial cam (4) or the at least one second partial cam
(5) mit der Außenwelle (2) verdrehfest verbunden ist und der jeweils andere(5) is connected to the outer shaft (2) in a rotationally fixed manner and the other
Teilnocken (5, partial cam (5,
4) verdrehfest mit der Innenwelle (3) verbunden ist, 4) is connected to the inner shaft (3) in a torsion-proof manner,
wobei auf der Außenwelle (2) ein Lagerinnenring (7) eines Wellenlagers (9) gehalten ist, wherein an inner bearing ring (7) of a shaft bearing (9) is held on the outer shaft (2),
dadurch gekennzeichnet, characterized,
dass der zweite Teilnocken (5) einen axialen Ansatz aufweist, der zumindest einen Teil des Lagerinnenrings (7) ausbildet. that the second partial cam (5) has an axial extension which forms at least part of the bearing inner ring (7).
Verstellbare Nockenwelle (1 ) nach Anspruch 1 , Adjustable camshaft (1) according to claim 1,
dadurch gekennzeichnet, characterized,
dass der Lagerinnenring (7) mehrteilig ausgebildet ist und ein weiterer Teil des Lagerinnenrings (7) durch einen zweiten Teilnocken (5) eines zum Nocken (6") benachbarten weiteren Nockens (6") ausgebildet ist. that the bearing inner ring (7) is designed in several parts and a further part of the bearing inner ring (7) is formed by a second partial cam (5) of a further cam (6 " ) adjacent to the cam (6").
Verstellbare Nockenwelle (1 ) nach Anspruch 2, Adjustable camshaft (1) according to claim 2,
dadurch gekennzeichnet, characterized,
dass ein Spalt (1 1 ) zwischen den beiden zweiten Teilnocken (5), die gemeinsam den Lagerinnenring (7) ausbilden, gebildet ist, der axial mit einer Radialbohrung (10) in der Außenwelle (2) ausgerichtet ist. that a gap (1 1) is formed between the two second partial cams (5), which together form the bearing inner ring (7), which is axially aligned with a radial bore (10) in the outer shaft (2).
Verstellbare Nockenwelle (1 ) nach einem der vorherigen Ansprüche, Adjustable camshaft (1) according to one of the preceding claims,
dadurch gekennzeichnet, characterized,
dass der Nocken (6") einen ersten Teilnocken (4) und zwei zweite Teilnocken (5) aufweist, wobei der erste Teilnocken (4) axial zwischen den beiden zweiten Teilnocken (5) angeordnet ist und einer der beiden zweiten Teilnocken (5) den Teil des Lagerinnenrings (7) ausbildet. that the cam (6 " ) has a first partial cam (4) and two second partial cams (5), the first partial cam (4) being arranged axially between the two second partial cams (5) and one of the two second partial cams (5). Part of the bearing inner ring (7) forms.
5. Verstellbare Nockenwelle (1 ) nach einem der Ansprüche 1 bis 3, 5. Adjustable camshaft (1) according to one of claims 1 to 3,
dadurch gekennzeichnet, characterized,
dass der Nocken (6") genau einen ersten Teilnocken (4) und genau einen zweiten Teilnocken (5) aufweist, wobei der erste Teilnocken (4) axial neben dem zweiten Teilnocken (5) angeordnet ist und der zweite Teilnocken (5) den Teil des Lagerinnenrings (7) ausbildet. that the cam (6 " ) has exactly one first partial cam (4) and exactly one second partial cam (5), the first partial cam (4) being arranged axially next to the second partial cam (5) and the second partial cam (5) the part of the bearing inner ring (7).
EP15729484.4A 2014-06-30 2015-06-17 Camshaft for the valve drive of an internal combustion engine with a variable valve opening duration Active EP3161281B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014109103.5A DE102014109103A1 (en) 2014-06-30 2014-06-30 Camshaft for the valve train of an internal combustion engine with variable valve duration
PCT/EP2015/063601 WO2016000965A1 (en) 2014-06-30 2015-06-17 Camshaft for the valve drive of an internal combustion engine with a variable valve opening duration

Publications (2)

Publication Number Publication Date
EP3161281A1 true EP3161281A1 (en) 2017-05-03
EP3161281B1 EP3161281B1 (en) 2018-08-15

Family

ID=53404572

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15729484.4A Active EP3161281B1 (en) 2014-06-30 2015-06-17 Camshaft for the valve drive of an internal combustion engine with a variable valve opening duration

Country Status (7)

Country Link
US (1) US10316705B2 (en)
EP (1) EP3161281B1 (en)
JP (1) JP2017519940A (en)
KR (1) KR20170021262A (en)
CN (1) CN106661967B (en)
DE (1) DE102014109103A1 (en)
WO (1) WO2016000965A1 (en)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2888837A (en) * 1957-02-28 1959-06-02 Carl S Hellmann Adjustable cam mechanism
US5090366A (en) * 1990-03-23 1992-02-25 Gondek John T Hydraulically operated engine valve system
US5253546A (en) * 1990-05-29 1993-10-19 Clemson University Variable valve actuating apparatus
JPH07102914A (en) 1993-03-03 1995-04-18 Peter Amborn Camshaft structure with mutually positioned shaft element and manufacture thereof
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
DE19908286B4 (en) * 1999-02-26 2007-03-01 Dr.Ing.H.C. F. Porsche Ag Variable valve control for internal combustion engines
WO2003014535A1 (en) * 2001-08-06 2003-02-20 Stefan Battlogg Device for transforming a rotational movement into a backwards and forward movement
DE102004056191B4 (en) * 2004-11-20 2008-08-28 Mahle Ventiltrieb Gmbh Camshaft for in particular motor vehicle engines
DE102005040934A1 (en) 2005-02-03 2006-08-17 Mahle International Gmbh Adjustable camshaft, in particular for internal combustion engines of motor vehicles, with a hydraulic adjusting device
DE102007010156A1 (en) 2007-03-02 2008-09-04 Audi Ag Valve drive unit for a combustion engine comprises an adjusting unit having interacting elements which interact alternately with a curved connecting part
DE102009041426A1 (en) 2009-09-16 2011-05-19 Thyssenkrupp Presta Teccenter Ag Camshaft with variable valve opening duration
DE102009056224B4 (en) 2009-11-28 2019-08-22 Audi Ag Valve gear of an internal combustion engine and internal combustion engine
JP2013019362A (en) * 2011-07-12 2013-01-31 Mitsubishi Motors Corp Variable valve device

Also Published As

Publication number Publication date
US10316705B2 (en) 2019-06-11
KR20170021262A (en) 2017-02-27
EP3161281B1 (en) 2018-08-15
DE102014109103A1 (en) 2015-12-31
CN106661967B (en) 2019-12-20
WO2016000965A1 (en) 2016-01-07
US20170122142A1 (en) 2017-05-04
JP2017519940A (en) 2017-07-20
CN106661967A (en) 2017-05-10

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