EP3819481A1 - Agencement d'arbre à cames - Google Patents

Agencement d'arbre à cames Download PDF

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Publication number
EP3819481A1
EP3819481A1 EP20202817.1A EP20202817A EP3819481A1 EP 3819481 A1 EP3819481 A1 EP 3819481A1 EP 20202817 A EP20202817 A EP 20202817A EP 3819481 A1 EP3819481 A1 EP 3819481A1
Authority
EP
European Patent Office
Prior art keywords
outer shaft
camshaft
shaft
rotor
camshaft arrangement
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Withdrawn
Application number
EP20202817.1A
Other languages
German (de)
English (en)
Inventor
André Seidenschwann
André Selke
Dietmar Schulze
Justus Himstedt
Stefan Steichele
Christoph Steinmetz
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.)
Mahle International GmbH
Eco Holding 1 GmbH
Original Assignee
Mahle International GmbH
Eco Holding 1 GmbH
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 Mahle International GmbH, Eco Holding 1 GmbH filed Critical Mahle International GmbH
Publication of EP3819481A1 publication Critical patent/EP3819481A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/34—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
    • 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
    • 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
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices

Definitions

  • the present invention relates to a camshaft arrangement with an adjustable camshaft and an adjuster for adjusting the camshaft.
  • the invention also relates to an internal combustion engine system with an internal combustion engine and such a camshaft arrangement.
  • a camshaft is usually used to actuate the valves of an internal combustion engine.
  • the camshaft has cams which are arranged non-rotatably on a shaft and which respectively actuate associated valves.
  • adjustable camshafts also called phase-adjustable camshafts, for example from the DE 10 2015 224 012 A1 , known.
  • Such a camshaft has an outer shaft and an inner shaft which is arranged in the outer shaft and which is rotatable relative to the outer shaft.
  • the respective shaft is connected to associated cams, so that a relative rotation between the inner shaft and the outer shaft leads to a phase shift between the cams of the outer shaft and the cams of the inner shaft.
  • adjusters are usually used which are connected to the outer shaft in a rotationally fixed manner by means of a stator and to the inner shaft by means of a rotor in a rotationally fixed manner.
  • Such a camshaft arrangement with an adjustable camshaft and an associated adjuster is from the DE 10 2014 206 291 A1 known.
  • the DE 10 2014 206 291 A1 it is proposed to connect the rotor of the adjuster to the inner shaft via an Oldham coupling in order to compensate for offsets between the inner shaft and the outer shaft in the axial and angular directions.
  • a contour or shape is provided on the inner shaft and a counter-shape or counter-contour for forming the Oldham coupling is provided on an intermediate piece that is connected to the rotor in a rotationally fixed manner.
  • a sleeve for supplying the camshaft arrangement with a fluid for simultaneous control and lubrication penetrates axially through the intermediate piece and into the inner shaft.
  • the present invention is therefore concerned with the object of specifying improved or at least different embodiments for a camshaft arrangement of the type mentioned above and for an internal combustion engine system with such a camshaft arrangement, which in particular are characterized by a simplified structure and / or an improved compensation of Mark offsets.
  • the present invention is based on the general idea, in a camshaft arrangement with an adjustable camshaft and an adjuster for adjusting the camshaft, an axially plugged positive connection as a coupling between a rotor of the adjuster and an inner shaft of the camshaft via an existing socket for supplying the Realize arrangement with lubricant.
  • An additional intermediate piece for realizing the form-fit connection between the rotor and the inner shaft can thus be omitted and the structure of the camshaft arrangement can thus be simplified.
  • the omission of the additional intermediate piece also leads to an improved compensation of offsets between the inner shaft and the outer shaft of the camshaft, in particular offsets in the axial direction and / or angular offsets, ie. H. Offset in the circumferential direction.
  • the camshaft arrangement has the adjustable camshaft and the adjuster.
  • the camshaft has an outer shaft and an inner shaft rotatably arranged in the outer shaft, the outer shaft and the inner shaft each being non-rotatably connected to at least one associated cam.
  • the adjuster has a stator and the rotor.
  • the stator is connected to the outer shaft in a rotationally fixed manner.
  • the rotor is non-rotatably connected to the bushing, with which the arrangement is supplied with lubricant.
  • the socket here has at least one channel which, during operation, is connected to a connection for the fluidic supply of the arrangement of lubricant, the connection being provided on an outer shell of the arrangement.
  • the socket on its axially facing the inner shaft end face has a shape that with a Counter-shape on the inner shaft that forms the axially plugged form-fit connection and thus the coupling.
  • the directions given here relate in particular to an axis of the outer shaft.
  • the axial direction therefore corresponds in particular to the axis of rotation of the outer shaft.
  • the angular direction corresponds accordingly to the circumferential direction surrounding the axial direction.
  • the lateral direction corresponds accordingly to a radial direction running perpendicular to the axial direction. Accordingly, axial offsets of the inner shaft to the outer shaft are relative displacements of the inner shaft to the outer shaft in the axial direction, angular offsets are relative movements of the inner shaft to the outer shaft in the circumferential direction and lateral offsets are relative movements of the inner shaft to the outer shaft in the radial direction.
  • an axially plugged form-fit connection and thus an axially plugged coupling is to be understood as a coupling having the shape on the socket and the counter-shape on the inner shaft, the shape and the counter-shape being axially plugged into one another and thus a rotationally fixed connection between the inner shaft and the Establish a rotor that is non-rotatably connected to the socket
  • the coupling is preferably designed as an Oldham coupling.
  • the coupling can thus be implemented easily and inexpensively.
  • the coupling is also conceivable to design the coupling as an elastomer coupling.
  • the lubricant is also preferably used for control, in particular for adjusting the inner shaft relative to the outer shaft.
  • the lubricant is accordingly preferably a fluid.
  • the lubricant is lubricating oil.
  • the socket is therefore in particular an oil guide socket.
  • the bushing is expediently arranged axially between the rotor and the inner shaft. It is preferred if the bushing is not only non-rotatably connected to the rotor, but is also fixed to the rotor, so that the bushing is also firmly connected axially and laterally to the rotor.
  • the counter-shape provided on the inner shaft can be formed integrally on the inner shaft. A simple construction of the arrangement and a reliable compensation of offsets with the aid of the coupling are thus possible.
  • Embodiments are preferred in which the outer shaft projects axially beyond the inner shaft on the side facing the socket with a receiving section, the socket being rotatably arranged in the receiving section of the outer shaft. This means that the bushing is received in the outer shaft and is rotatably arranged. This leads to a compact design of the camshaft arrangement and a simple implementation of the clutch.
  • Embodiments prove to be advantageous in which between a radial inside of the outer shaft, hereinafter also referred to as the outside shaft inside, in the receiving section and a radial outside of the bushing, hereinafter also called the bush outside, at least one elastic Seal is arranged.
  • a fluidic sealing of the receiving area is thus achieved.
  • the flow of the lubricant out of the receiving area is prevented or at least reduced.
  • at least two axially spaced apart seals are provided.
  • An axial flow of the lubricant is thus at least reduced in both axial directions.
  • at least one of the at least one seals is arranged and received in an associated, radially open outer groove in the outer shaft inside or the bush outside, advantageously in the bush outside.
  • seal is arranged radially between the outside of the bushing and the associated sliding ring.
  • An associated sliding ring is advantageously arranged radially between at least one of the at least one seals, preferably the respective seal, and the inside of the outer shaft or the outside of the bush.
  • the sliding ring is preferably arranged radially between the associated seal and the inside of the outer shaft.
  • the sliding ring serves to protect the seal during relative movements, in particular rotations, between the outer shaft and the inner shaft.
  • the transmission of shear forces to the seal is avoided or at least reduced. As a result, damage to the seal is reduced so that the seal is sealed for a longer period of time.
  • At least one of the at least one sliding rings is advantageously a slotted sliding ring, that is to say interrupted in the circumferential direction.
  • the sliding ring can thus be installed in a particularly simplified manner. Rectangular rings are also conceivable.
  • the elastic seal can be designed as desired.
  • the seal is an annular seal. This leads to a homogeneous and / or improved sealing effect. Designs in the form of sliding or rectangular rings with reduced static and sliding friction coefficients for improved response behavior and reduced losses during operation are also conceivable. PTFE-coated rings are particularly advantageous for this.
  • the bushing is advantageously arranged radially freely in the outer shaft.
  • the bushing can be spaced more radially from the outer shaft and / or the bushing can be dispensed with in the outer shaft.
  • the outer shaft and / or the bushing can thus be produced in a simplified manner.
  • the outer shaft can be manufactured radially on the inside and / or the bushing on the radial outside with higher tolerances.
  • fine machining of the inside of the outer shaft can be dispensed with.
  • easier positioning of the rotor relative to the inner shaft is possible in this way.
  • an exact lateral positioning of the rotor relative to the inner shaft can be dispensed with in this way.
  • the rotor can be rotatably mounted on a radially outer outside of the outer shaft, also referred to below as the outer shaft outer side.
  • the rotor can be rotatably mounted exclusively on the outside of the outer shaft. This leads in particular to the fact that a separate machining of the inside of the outer shaft can be dispensed with, so that the outer shaft can be manufactured more cost-effectively overall. In particular, it is thus possible to produce the inside of the outer shaft with increased tolerances.
  • a compensation and / or reduction of lateral offsets between the inner shaft and the outer shaft is achieved via the rotatable mounting of the rotor on the outer shaft outside.
  • the mounting of the rotor on the outside of the outer shaft is advantageously realized in such a way that the outer shaft has an axial projection which penetrates into the adjuster, in particular protrudes beyond the bushing in the axial direction.
  • the rotor is rotatably mounted on the outside of the outer shaft of the projection. This leads in particular to the fact that the mounting of the rotor on the outer shaft is implemented efficiently and in a space-saving manner. In particular, because of the proximity of the rotor to the projection, a simple mounting of the rotor on the outer shaft can take place in this way.
  • the rotationally fixed connection of the rotor to the bushing is preferably implemented via a bolt, which can be part of a screw.
  • the bolt can in particular have an external thread which forms a screw connection with an internal thread of the socket.
  • a screw head or a nut of the screw connection can act on the rotor axially against the bushing in such a way that the rotor is connected in a rotationally fixed manner to the bushing.
  • the bolt advantageously has a cavity inside, which is also referred to below as the bolt cavity. It is preferred here if the bolt cavity is fluidically connected to the interior of the bushing, in particular a cavity formed in the interior of the bushing, hereinafter also referred to as the bushing cavity. In this way it is possible, in particular, to supply and discharge the lubricant via the bushing and the bolt.
  • the camshaft arrangement expediently has a drive wheel which is used to drive the camshaft.
  • the drive wheel is expediently non-rotatably connected to the stator.
  • the drive wheel can be in an associated system with an internal combustion engine, hereinafter also an internal combustion engine system called, be driven by a crankshaft of the internal combustion engine.
  • the drive wheel can in particular be a spur wheel.
  • the drive wheel and the stator in one piece.
  • the drive wheel and the stator can be produced together, for example by sintering.
  • a simple centering of the stator with respect to the outer shaft can be achieved if the stator is connected directly or indirectly to the receiving section of the outer shaft. This also means that the adjuster is simply centered relative to the outer shaft and / or the inner shaft.
  • At least one centering collar for example on the drive wheel, can be provided for centering the adjuster.
  • the bushing can have a bushing cavity which is used in particular to supply the arrangement with the lubricant.
  • the socket cavity is expediently closed on the side axially facing the mold and thus on the side axially facing the inner shaft.
  • the bushing preferably has at least two axially spaced apart channels which are each fluidically connected to the bushing cavity, the channels being arranged axially between two slip rings.
  • the socket also has at least two such channels spaced apart from one another in the circumferential direction. This results in an improved supply of lubricant to the arrangement during operation.
  • an internal combustion engine system with such a camshaft arrangement also belongs to the scope of this invention.
  • the internal combustion engine system includes the internal combustion engine, which has at least two valves that are actuated by the cams of the camshaft during operation.
  • the camshaft arrangement 1 has an adjustable camshaft 3 with a hollow outer shaft 4 and an inner shaft 5, which is rotatably arranged in the outer shaft 4.
  • the outer shaft 4 can be rotated about an axis of rotation 6 which corresponds to an axial direction 7.
  • the inner shaft 5 and the outer shaft 4 are arranged coaxially, that is to say that the inner shaft 5 and the outer shaft 4 have the same axis of rotation 6.
  • At least one associated cam 8, with which a valve of the internal combustion engine can be actuated, is attached to the outer shaft 4 in a rotationally fixed manner.
  • the camshaft assembly 1 of the Figure 1 can furthermore have a drive wheel 9 which is connected in a rotationally fixed manner to the outer shaft 4 and thus rotates the outer shaft 4.
  • the camshaft arrangement 1 has an adjuster 10.
  • the adjuster 10 has a stator 11 connected to the outer shaft 4 in a rotationally fixed manner.
  • the stator 11 is non-rotatably connected to the drive wheel 9, for example via screw connections 13.
  • the adjuster 10 also has a rotor 12 that is non-rotatably connected to the inner shaft 5 and that is rotatable relative to the stator 11, this being done via a corresponding rotation of the rotor 12 to the stator 11.
  • the stator 11 is arranged radially between the drive wheel 9 and the outer shaft 4.
  • the rotor 12 is arranged axially on the front side of the drive wheel 9.
  • a side view of the camshaft arrangement 1 can be seen, the camshaft arrangement 1 being shown axially between the adjuster 10 and the inner shaft 5 in an axially extending longitudinal section which extends radially centrally.
  • the camshaft arrangement 1, hereinafter also referred to as arrangement 1 for short, has a bushing 14 which is used to supply the arrangement 1 with a lubricant, in particular with oil.
  • the lubricant is also used for control, in particular for moving the inner shaft 5 relative to the outer shaft 4.
  • the bushing 4 is fluidly supplied with the lubricant during operation via at least one connection 15 provided on an outer shell of the arrangement 1 in Figure 1
  • two such connections 15 are provided, one of which is used to supply the lubricant and the other to discharge the lubricant.
  • the socket 14 has at least one channel 16, which also has a cavity 17 formed in the interior of the socket 14 Socket cavity 17 called, fluidly connects to the associated connection 15.
  • the socket 14 for the respective connection 15 has at least two associated channels 16, which are spaced apart from one another in a circumferential direction 37.
  • the respective channel 16 here runs radially through the bush 14.
  • the rotor 12 is non-rotatably connected to the inner shaft 5 via the bushing 14.
  • the bush 14 is arranged axially between the rotor 12 and the inner shaft 5.
  • the bushing 14 has a shape 19 on its end face 18 axially facing the inner shaft 5, which is axially inserted with a counter-shape 20 on the inner shaft 5 and thus forms an axially inserted coupling 21.
  • an intermediate piece 23 having the counter-mold 20 is attached non-rotatably to the inner shaft 5 and is arranged axially between the end face 18 of the bushing 14 and the inner shaft 5.
  • Figure 2 a frontal view in the axial direction 7 of the end face 18 and thus of the mold 19 and Figure 3 the in Figure 2 Section marked III in the axial direction 7 through the bush 14.
  • Figure 4 Figure 14 shows an isometric view of the socket 14.
  • the coupling 21 is designed as an Oldham coupling 22.
  • the socket 14 in the exemplary embodiments shown is closed on the side facing the end face 18 and is designed to be open on the side facing away from the end face 18.
  • the rotationally fixed connection of the rotor 12 to the bushing 14 takes place via a bolt 24, which is part of a screw 25 with a screw head 26.
  • the bolt 24 has for this purpose an external thread, not shown, which is not with a
  • the internal thread shown cooperates in the cavity 17 of the socket 14, the screw head 26 pressing the rotor 12 axially in the direction of the socket 14 and thus connecting the rotor 12 to the socket 14 in a rotationally fixed manner.
  • the bolt 24 is designed to be hollow in the exemplary embodiments shown and has a cavity 27 in its interior, which is also referred to below as the bolt cavity 27.
  • the bolt cavity 27 is open on the side axially facing the socket 14 or the inner shaft 5, so that the bolt cavity 27 and the socket cavity 17 are fluidically connected to one another.
  • the outer shaft 4 protrudes in the axial direction 7 beyond the inner shaft 5 and has a receiving portion 28 projecting beyond the inner shaft 5, in which the bushing 14 is received and rotatably arranged.
  • the connections 15 are each formed in the receiving section 28 of the outer shaft 4.
  • the bush 14 and thus the rotor 12 are rotatably arranged within the receiving portion 28.
  • the outer shaft 4 has a radially inner inner side 29, hereinafter also called outer shaft inner side 29.
  • the socket 14 has a radially outer outside 30, hereinafter also referred to as the socket outside 30.
  • At least one elastic seal 32, in particular ring seal 33, is arranged radially between the outer shaft inner side 29 and the bush outer side 30, with which in particular an outflow of the lubricant is prevented or at least reduced.
  • two such seals 32 are used, which are spaced apart from one another in the axial direction 7, the channels 16 of the socket 14 and the connections 15 being arranged axially between the seals 32. An outflow of the lubricant in both axial directions is thus prevented or at least reduced.
  • the socket 14 has on the socket outer side 30 for the respective seal 32 an annular outer groove 34 which is open radially outward and in which the seal 32 is received.
  • an associated slide ring 31 is arranged radially between the respective seal 32 and the outer shaft inner side 29 or the bush outer side 30.
  • the respective sliding ring 31 is arranged radially between the seal 32 and the inner side 29 of the outer shaft.
  • the sliding ring protects the associated seal 32 against relative movements, in particular rotations, between the inner shaft 5 and the outer shaft 4.
  • Such a sliding ring 31 is in Figure 6 is shown separately and isometric. Figure 6 it can be seen that the sliding ring 31 is interrupted in the circumferential direction 37 and is thus designed to be slotted.
  • the seals 32 and the coupling 21 allow the bushing 14 to be freely positioned radially in the outer shaft 4. A mounting of the bush 14 in the outer shaft 4 can thus be dispensed with.
  • FIG Figure 7 shows a section through the camshaft arrangement 1 in the axial direction 7 and thus a longitudinal section, and wherein the rotor 12 is not shown.
  • This in Figure 7 Shown embodiment are different from the in the Figures 1 to 6 embodiment shown in that the in Figure 7 Rotor 12, not shown, is rotatably mounted on a radially outer outer side 35 of outer shaft 4, hereinafter also referred to as outer shaft outer side 35.
  • the bush 14 is also rotatably mounted on the outer shaft outside 35 via the rotor 12, so that a mounting on the outer shaft inside 29 can be dispensed with.
  • the outer shaft 4 has in the in Figure 7
  • the embodiment shown has a projection 36 penetrating axially into the adjuster 10, the rotor 12 being rotatably mounted on the outer shaft outer side 35 of the projection 36.
  • seals 32 in particular ring seals 33, can be received in the outer grooves 34 radially between the outer shaft inner side 29 and the bush outer side 30 in order to achieve a corresponding seal.
  • the in Figure 7 The exemplary embodiment shown shows that the stator 11 can be attached in a rotationally fixed manner, in particular shrunk on, for the rotationally fixed connection to the outer shaft 4 on the outer shaft outer side 35.
  • the respective camshaft arrangement 1 compensates for an axial and angular offset between the inner shaft 5 and the outer shaft 4 via the coupling 21.
  • the mounting of the rotor 12 and the bushing 14 on the outer shaft 4 also compensates for a lateral offset between the inner shaft 5 and the outer shaft 4.
  • the respective camshaft arrangement 1 is compact and easy to manufacture in this way.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP20202817.1A 2019-11-08 2020-10-20 Agencement d'arbre à cames Withdrawn EP3819481A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019217295.4A DE102019217295A1 (de) 2019-11-08 2019-11-08 Nockenwellen-Anordnung

Publications (1)

Publication Number Publication Date
EP3819481A1 true EP3819481A1 (fr) 2021-05-12

Family

ID=72944044

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20202817.1A Withdrawn EP3819481A1 (fr) 2019-11-08 2020-10-20 Agencement d'arbre à cames

Country Status (4)

Country Link
US (1) US20210140349A1 (fr)
EP (1) EP3819481A1 (fr)
CN (1) CN112780376A (fr)
DE (1) DE102019217295A1 (fr)

Citations (5)

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GB2424258A (en) * 2005-03-18 2006-09-20 Mechadyne Plc Camshaft to phaser coupling
US20100089351A1 (en) * 2008-10-09 2010-04-15 Schaeffler Kg Camshaft phaser for a concentric camshaft
DE102014206291A1 (de) 2014-04-02 2015-10-08 Mahle International Gmbh Nockenwelle
DE102015224012A1 (de) 2015-12-02 2017-06-08 Mahle International Gmbh Verstellbare Nockenwelle
EP3564501A1 (fr) * 2018-05-03 2019-11-06 Mechadyne International Limited Arbre à cames concentrique à interface de modulateur de phase double

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
DE102015200139B4 (de) * 2015-01-08 2021-07-08 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleranbindung an eine Doppelnockenwelle
DE102015200541A1 (de) * 2015-01-15 2015-11-05 Schaeffler Technologies AG & Co. KG Abstützfeder eines Nockenwellenverstellers angeordnet direkt zwischen zwei koaxial zueinander angeordneten Nockenwellen
DE102015205272A1 (de) * 2015-03-24 2016-09-29 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Oldham-Kupplung zur Anbindung an eine Nockenwelle

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