EP3396122A1 - Arbre à came concentrique et ensemble actionneur - Google Patents

Arbre à came concentrique et ensemble actionneur Download PDF

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Publication number
EP3396122A1
EP3396122A1 EP17168117.4A EP17168117A EP3396122A1 EP 3396122 A1 EP3396122 A1 EP 3396122A1 EP 17168117 A EP17168117 A EP 17168117A EP 3396122 A1 EP3396122 A1 EP 3396122A1
Authority
EP
European Patent Office
Prior art keywords
actuator
camshaft
assembly
tube
outer tube
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Withdrawn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
EP17168117.4A
Other languages
German (de)
English (en)
Inventor
Timothy Mark Lancefield
Mark Walton
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.)
Mechadyne International Ltd
Original Assignee
Mechadyne International Ltd
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 Mechadyne International Ltd filed Critical Mechadyne International Ltd
Priority to EP17168117.4A priority Critical patent/EP3396122A1/fr
Publication of EP3396122A1 publication Critical patent/EP3396122A1/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Withdrawn legal-status Critical Current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
    • F01L1/02—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
    • F01L1/3442—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
    • 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
    • F01L1/34—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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves

Definitions

  • the present invention relates a concentric camshaft and actuator assembly, the concentric camshaft comprising a camshaft tube with two groups of cam lobes on its outer surface, wherein the cam lobes of the first group are permanently fixed for rotation with the tube and the cam lobes of the second group are free to rotate on the outside of the tube and are connected for rotation with an inner drive shaft mounted within the inner bore of the tube, via connecting pins that pass through circumferentially extending slots in the tube.
  • This assembled camshaft which is referred to herein as a 'concentric camshaft' allows the timing of its two groups of cam lobes to be varied in relation to one another by relative rotation of the camshaft tube and the inner drive shaft.
  • the assembly of the invention further includes an actuator for adjusting the relative timing of the two groups of cam lobes which is integrated with the concentric camshaft, so that the concentric camshaft and its actuator may be mounted to the engine as a single unit.
  • the present invention aims to provide an actuator and concentric camshaft assembly of reduced complexity, to reduce manufacturing cost and packaging space.
  • the actuator has a drive member and at least one driven member that is rotatable relative to the drive member.
  • the camshaft tube is attached for rotation with a first of the actuator members using a firm jointing method, such as a shrink fit or welding, while the second actuator member is connected for rotation with the inner drive shaft via a connecting pin that passes through a clearance slot in the camshaft tube.
  • the actuator can be separate from the camshaft drive connection to the crankshaft and be used purely to adjust the relative timing of the two groups of cam lobes.
  • the actuator may be integrated with a chain sprocket or gear to provide a drive connection to the camshaft from the crankshaft.
  • the design is compatible with either an electric or a hydraulic type of actuator.
  • a central fixing bolt is commonly used to create a drive connection between the actuator and the inner drive shaft.
  • the bore of the camshaft tube need not be obstructed, neither by its connection to the first actuator member nor by the connection of the inner shaft to the second actuator member. Consequently, in the case where a hydraulic actuator is used, the central bore of the camshaft tube can accommodate an integrated control valve.
  • the control valve may be supplied with oil via the clearance between the bore of the camshaft tube and the outer surface of the inner drive shaft.
  • the actuator may act to control the relative axial positions via its driving connections to the camshaft tube and inner drive shaft.
  • Figures 1A, 1B, 2 and 3 show the construction of a first embodiment of an assembly of a concentric camshaft 10 and hydraulic actuator 50 configured to control the relative timing of the two sets of cam lobes 12a, 12b.
  • the drive connection to the crankshaft may be achieved by a sprocket or gear (not shown) mounted to the opposite end of the camshaft tube, either driving the tube directly, if the phase of the cam lobes of the first group is to be fixed in relation to the engine crankshaft, or via a conventional camshaft phasing system, if the phase of the cam lobes of the first group is to be variable in relation to the engine crankshaft.
  • the camshaft tube 14 drives the inner member 52, sometimes referred to as the rotor, of the actuator 50.
  • the inner member 52 is rigidly attached to the camshaft tube 14 via a shrink fit, welding, adhesive or by mechanical deformation of the camshaft tube to generate an interference.
  • the outer member of the actuator 50 is comprised of a central plate 54, defining, in conjunction with the inner member 52, a number of arcuate hydraulic cavities and two end plates 56,58 that are clamped together around the inner member 52 via three fixing bolts 60 and thus limit the axial movement between the inner and outer members of the actuator 50.
  • the end plate 56 on the camshaft side of the actuator 50 includes a sleeve 62 and has a close fitting bore 64 that rotatably engages on the outer surface of the camshaft tube 14.
  • a radial connecting pin 66 engaged in the sleeve 62 passes through clearance slots in the tube 14 and connects the outer member 54,56,58 of the actuator 50 for rotation with the inner drive shaft 16.
  • the driving connection between the outer member and the inner drive shaft is similar to the connection between the drive shaft and the second group of cam lobes. In this embodiment, the drive from the crankshaft would be at the other end of the cam and would incorporate the camshaft axial position control.
  • a hydraulic spool valve 70 is provided in the inner bore of the camshaft tube 14 in order to control the relative timing of the inner 52 and outer 54,56,58 actuator members in response to the force of a solenoid 72 mounted on a stationary part of the surrounding engine.
  • Timing features 76 are also integrated onto the end plate 56 connected to the inner drive shaft 16 in order to provide actuator position feedback to the Engine Management System (EMS). It will be appreciated that timing features for this purpose may alternatively be provided on the central plate 54 or on the opposing end plate 58.
  • Oil is supplied to the control spool 70 from the adjacent camshaft support bearing 80 via a check valve 82 and an oil feed sleeve 84 located in the bore of the camshaft tube 14. It would additionally be possible to include a filter for preventing any particles in the oil supply from entering the spool valve.
  • the actuator also includes a lock pin 88 for fixing the relative timing of the two sets of cam lobes 12a, 12b when there is insufficient oil pressure to control the actuator position accurately.
  • a torque spring 90 is also mounted to the actuator 50 to bias the relative angle of the inner and outer members of the actuator towards the locked position.
  • the outer member 54,56,58 of the actuator is adjustable to eliminate the effect of manufacturing and assembly tolerances on the relative angular positions of the two sets of cam lobes.
  • the central plate 54 has circumferentially elongated fixing bolt holes 92 to allow its rotational position to be adjusted before tightening the three fixing bolts 60.
  • the second embodiment of the invention illustrated in Figures 4, 5 and 6 , is generally similar to that of the first embodiment and the same reference numerals have been allocated to unchanged components. To avoid repetition, in the description of the three remaining embodiments shown in the drawings, modified components serving an analogous function have been allocated reference numerals with the same last two significant digits.
  • the actuator 150 has been adapted to provide the drive connection to the engine crankshaft, second camshaft or auxiliary system by the addition of a sprocket 151 (or a gear) to the end plate 156 of the outer member of the actuator 150.
  • the axial position of the camshaft in the engine may also be controlled by one or more thrust features adjacent to the sleeve 162 on the end plate 156.
  • the second embodiment also shows how the design may be adapted to utilise an external hydraulic control valve by providing two separate oil feeds 181, 183 in the adjacent camshaft support bearing 180 that are communicated into the actuator 150 via the camshaft tube 14 and inner drive shaft 16.
  • the feature 176 for generating a timing feedback signal is integrated into a support hub 175 for the bias spring 190 to provide feedback of the angular position of the tube 14 and thus the inner member 152 of actuator 150, rather than the outer member feedback used in the first embodiment.
  • the inner drive member 152 of the actuator has additional features 153 in its inner bore to form a more positive drive connection with the camshaft tube 14.
  • the features are depicted as short splines, but other form locking features may alternatively be used.
  • Figures 7 and 8 show a third embodiment of the invention wherein the actuator 250 is controlled via an external oil control valve 273 mounted on a stationary part of the engine and supplying oil to the actuator 250 via two axially separated oil feeds located in the bore of the camshaft outer tube, the oil feed connections being sealed via rotatable sealing rings 275.
  • the central plate 254 of the actuator has sprocket teeth 251 to enable it to be driven by the crankshaft and, unlike the first two described embodiments, it is the central plate 254 that is mounted for rotation with the outer tube 14 of the concentric camshaft.
  • the end plates 256 and 258 are in this embodiment connected by the bolts 260 for rotation with radial vanes 252 that together with the end plates 256 and 258 constitute the inner member, or rotor, of the actuator 250.
  • Figure 9 illustrates a fourth embodiment of the invention in a diagrammatic form, and shows a concentric camshaft integrated with an electric actuator 350.
  • the electric actuator 350 is controlled by a motor 373 mounted on a stationary part of the surrounding engine.
  • the actuator 350 has a stator 354 connected for rotation with the inner shaft 16 of the concentric camshaft by a pin 366 passing through circumferentially elongated slots in the outer tube 14 and a rotor 352 coupled for rotation with the outer tube 14 of the concentric camshaft.
  • the third embodiment serves to illustrate that in all embodiments the stator and rotor of the actuator may be interchanged and each of them can be connected either to the inner shaft or the outer tube of the concentric camshaft.
  • the actuator itself could be a twin hydraulic actuator, or a hybrid electric/hydraulic actuator.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP17168117.4A 2017-04-26 2017-04-26 Arbre à came concentrique et ensemble actionneur Withdrawn EP3396122A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP17168117.4A EP3396122A1 (fr) 2017-04-26 2017-04-26 Arbre à came concentrique et ensemble actionneur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17168117.4A EP3396122A1 (fr) 2017-04-26 2017-04-26 Arbre à came concentrique et ensemble actionneur

Publications (1)

Publication Number Publication Date
EP3396122A1 true EP3396122A1 (fr) 2018-10-31

Family

ID=58669615

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17168117.4A Withdrawn EP3396122A1 (fr) 2017-04-26 2017-04-26 Arbre à came concentrique et ensemble actionneur

Country Status (1)

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EP (1) EP3396122A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111558824A (zh) * 2019-02-13 2020-08-21 舍弗勒技术股份两合公司 凸轮轴装配方法及配属的凸轮轴调节系统
WO2020244705A1 (fr) * 2019-06-05 2020-12-10 Schaeffler Technologies AG & Co. KG Arbre à cames comportant un canal d'huile, déphaseur d'arbre à cames comportant un arbre à cames et procédé de montage de déphaseur d'arbre à cames

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2432645A (en) * 2005-11-28 2007-05-30 Mechadyne Plc Variable phase drive coupling
DE102008032412A1 (de) * 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
US20130025403A1 (en) * 2010-04-06 2013-01-31 Borgwarner Inc. Cam phaser centrally located along concentric camshafts
DE102015200139A1 (de) * 2015-01-08 2016-07-14 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleranbindung an eine Doppelnockenwelle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2432645A (en) * 2005-11-28 2007-05-30 Mechadyne Plc Variable phase drive coupling
DE102008032412A1 (de) * 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
US20130025403A1 (en) * 2010-04-06 2013-01-31 Borgwarner Inc. Cam phaser centrally located along concentric camshafts
DE102015200139A1 (de) * 2015-01-08 2016-07-14 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleranbindung an eine Doppelnockenwelle

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111558824A (zh) * 2019-02-13 2020-08-21 舍弗勒技术股份两合公司 凸轮轴装配方法及配属的凸轮轴调节系统
CN111558824B (zh) * 2019-02-13 2025-01-07 舍弗勒投资(中国)有限公司 凸轮轴装配方法及配属的凸轮轴调节系统
WO2020244705A1 (fr) * 2019-06-05 2020-12-10 Schaeffler Technologies AG & Co. KG Arbre à cames comportant un canal d'huile, déphaseur d'arbre à cames comportant un arbre à cames et procédé de montage de déphaseur d'arbre à cames

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