WO2019069265A1 - Moteur doté d'un arbre à cames concentrique - Google Patents

Moteur doté d'un arbre à cames concentrique Download PDF

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Publication number
WO2019069265A1
WO2019069265A1 PCT/IB2018/057717 IB2018057717W WO2019069265A1 WO 2019069265 A1 WO2019069265 A1 WO 2019069265A1 IB 2018057717 W IB2018057717 W IB 2018057717W WO 2019069265 A1 WO2019069265 A1 WO 2019069265A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
camshaft
engine
drive
relative
Prior art date
Application number
PCT/IB2018/057717
Other languages
English (en)
Inventor
Mark Walton
Ian Methley
Aspinall JONATHAN
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.
Publication of WO2019069265A1 publication Critical patent/WO2019069265A1/fr

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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
    • 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

Definitions

  • An adjustable assembled camshaft that comprises a camshaft tube with two groups of cam lobes mounted on its outer surface.
  • the first group of cam lobes is permanently fixed to the tube for rotation with the tube, while the second group of cam lobes is free to rotate relative to the surface of the tube and is connected for rotation with a drive shaft passing through the bore of the tube, by means of connecting pins that pass through circumferentially elongated slots in the tube.
  • camshaft also known 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.
  • actuators are also known that can control the timing of both groups of cam lobes independently relative to the crankshaft.
  • the present invention is particularly concerned with engines with variable valve timing that utilise a dry timing belt to connect a camshaft to the crankshaft.
  • the aim of the present invention is to provide an engine in which an actuator is integrated into a timing belt pulley driving a concentric camshaft and in which the actuator is sealed to prevent any oil contamination of the belt by oil escaping from the actuator.
  • DE102008019745 is believed to represent the closest prior art to the present invention.
  • the latter patent discloses an actuator (15) securable to a bearing (37) that is shrink-fitted to the camshaft (6) . Because the bearing (37) is secured to the camshaft (6) rather than the actuator, an extra seal (49) must be provided to prevent egress of oil from the engine when the actuator is fitted to the bearing.
  • the element that seals against the camshaft housing forms part of the actuator, rather than the camshaft, and as a result the requirement for an additional seal is obviated.
  • WO 2017/140351 discloses a hydraulic phaser controlling the timing of the cam lobes where the drive connection to the camshaft is positioned inside the engine block as
  • the present invention provides a solution for fitting a sealed actuator to an adjustable camshaft assembly while maintaining access to the seal located behind the actuator.
  • the invention employs an actuator design for a concentric camshaft that is suitable for applications requiring the actuator to be fully oil tight. This is a requirement when the actuator is located on the outside of the main engine structure, as is often the case when the drive connection to the crankshaft utilises a dry timing belt.
  • the actuator of the invention can be assembled to a
  • concentric camshaft in a separate operation after the camshaft has been fitted to the engine or cylinder head and this provides access for the assembly and servicing of an annular seal, typically a lip seal, located concentrically with the camshaft and fitted to a stationary part of the engine behind the actuator. Once the seal is in place the actuator can be fitted to the concentric camshaft and connected to drive both groups of cam lobes on the camshaft.
  • an annular seal typically a lip seal
  • Embodiments of the invention provide means for connecting the actuator to drive the camshaft which are applicable to both electric and hydraulic types of actuator.
  • embodiments demonstrate the application of the invention to single actuators, where one group of cam lobes is driven in synchronism with the crankshaft and the actuator controls the phasing of the second group of cam lobes.
  • embodiments demonstrate the application of the invention to twin actuators, which control the phasing of both groups of cam lobes relative to the crankshaft.
  • twin actuators which control the phasing of both groups of cam lobes relative to the crankshaft.
  • the requirement for total sealing is not generally compatible with an oil control valve mounted directly in the actuator, so the embodiments of the invention also show how hydraulic
  • hydraulic actuators typically utilise a mechanical lock to set the relative angular orientations of the drive and driven members during start-up when there is insufficient oil pressure to control the actuator
  • the mechanical lock is conventionally released by oil pressure and requires a vent to ambient pressure in order to release effectively.
  • Embodiments of the invention illustrate how a vent can be provided for the locking system by providing a connection to the engine crankcase, thus avoiding any external oil leak path.
  • Any concentric camshaft requires the axial position of the inner drive shaft relative to the camshaft tube to be controlled.
  • Embodiments of the invention demonstrate how the relative axial positions may be set via the driving
  • Figure 1 is a first exploded view of a first embodiment of the invention
  • Figure 2 is a second exploded view of the embodiment shown in Figure 1,
  • Figure 3 is a section through the embodiment of
  • Figure 4 is an exploded view of a second embodiment of the invention.
  • Figure 5 is a section through the embodiment of
  • Figure 6 is an exploded view of a third embodiment of the invention.
  • Figure 7 is a section through the embodiment of
  • Figure 8 is an exploded view of a fourth embodiment of the invention.
  • Figure 9 is a section through the embodiment of
  • Figure 10 is an exploded view of a fifth embodiment of the invention.
  • Figure 11 is a section through the embodiment of
  • FIG. 1 A first embodiment of the invention is shown in Figures 1 to 3.
  • an actuator 10 has a pulley 12 for accepting drive from the crankshaft via a toothed belt, neither of which is shown.
  • the pulley 12 is connected to a drive member comprising two end plates 14a and 14b, and three sealed vanes 16 via three threaded fasteners 18 as shown most clearly in Figure 2.
  • the driven member of the actuator 10 is formed as a disc 20 with three arcuate cavities 22 through which the three vanes 16 of the drive member pass.
  • Each vane 16 acts to divide its respective cavity 22 into two hydraulic working volumes that are supplied with hydraulic oil to change the relative angle of the drive and driven members .
  • an outer ring 24 encloses the driven member 20 and is sealed between the end plates 14a, 14b of the drive member by two sealing rings 26.
  • a lock pin 28 loaded by means of a spring 30 is installed in the driven member 20.
  • the lock pin 28 serves to fix the relative angular positions of the drive and driven members by latching in a bore 32 located in the front end plate 14b of the drive member, as shown in Figure 2.
  • oil pressure is applied to the end face of the lock pin 28 that is engaged into the bore and when the oil pressure exceeds the pre-load force of the spring 30, the lock pin slides fully into the driven member and the actuator is free to rotate.
  • the lock pin In order for the lock pin to function correctly it is essential for the cavity 34
  • the actuator 10 is mounted to a concentric camshaft, generally designated 50, in the manner shown in the
  • the camshaft 50 is formed of an outer tube 52 and concentric inner shaft 54. Two sets of cam lobes are mounted on the outer tube 52, multiple lobes of each set being shown in the section of Figure 3.
  • the first set of cam lobes 56 is fixed for rotation with the outer tube 52, for example by heat shrinking.
  • the second set of cam lobes 58 is free to rotate about the outer tube 52 and is connected for rotation with the inner shaft 54 by means of pins 60 that pass through circumferentially extending slots in the outer tube 52.
  • Figure 3 also shows a timing wheel 59 connected for rotation with the inner shaft 54 by means of a pin 61.
  • the drive member 14a, 14b is connected for rotation with the outer tube 52 of the camshaft via a threaded connection 70, comprising a female thread in a bore in the rear end plate 14a that engages with a thread machined directly into the camshaft tube 52. Concentricity is maintained by a close fitting bore diameter 72 adjacent to the thread.
  • actuator 10 can be tightened on to the tube via a drive hex located on the front plate 14b of the drive member.
  • the drive pulley 12 has elongated holes 13 for the threaded fastenings 18 securing it to the drive member 14a, 14b so that the timing of the camshaft relative to the crankshaft can be accurately set .
  • the camshaft timing may be set, in the same way as carried out conventionally, by providing reference features on the camshaft 50 and the crankshaft that can be positioned relative to the engine structure by a pin or key to
  • the timing belt can then be fitted and tensioned, allowing the pulley 12 to take up its preferred angular position by rotating it relative to the rear plate 14a of the drive member. Finally, the three actuator fastenings 18 can be tightened to secure the pulley 12 in the correct angular position.
  • the driven member 20 is connected for rotation with the inner shaft 54 of the camshaft by means of a clamping bolt 80.
  • a sealing cover 82 is fitted to the front plate 14b to prevent any oil leakage once this clamping bolt 80 has been fitted .
  • the orientation of the driven member 20 relative to the inner shaft 54 is not defined due to the threaded connection to the tube, so it is not
  • a rotary oil seal 90 is fitted to the engine cylinder head, part of which is shown in Figure 3 and designated 92.
  • the oil seal 90 engages a cylindrical surface of the rear plate 14a of the drive member to prevent any oil leakage from inside the engine that could contaminate the timing belt.
  • the rear plate 14a also has a hole 94 drilled through it, to allow the vent for the lock pin 28 to pass through the rotary seal 90.
  • the hydraulic connections for controlling the actuator 10 are shown in Figure 3 and comprise a first passage 96 located between the inner surface of the camshaft tube 52 and the outer surface of the inner shaft 54, and a second passage 98 located between the fixing bolt 80 securing the driven member 20 and an associated counter-bore in the inner shaft 54.
  • a separate oil control valve can be connected to these oil feeds via the front journal bearing of the actuator 10
  • the second embodiment of the invention shown in Figures 4 and 5, is generally similar to the first, but utilises a simpler actuator construction.
  • identical components have been allocated the same reference numerals and modified components serving an analogous function have been allocated reference numerals with the same last two significant digits.
  • the drive member is a toothed belt pulley 112 that is clamped between two end plates 114a and 114b by means of four threaded fasteners 118.
  • the drive member is connected to the camshaft tube 52 via a threaded connection 70, such that the actuator 110 is assembled as a unit onto the front of the camshaft 50 but its angular orientation with respect to the camshaft is not defined due to the threaded connection.
  • the end of the camshaft tube 52 is not itself threaded, and instead a threaded drive adaptor 103 is permanently fitted to the end of the outer tube 52 by shrink fitting or a similar method.
  • the drive adaptor also provides a location for a ball bearing 105 to provide radial support and axial location of the camshaft 50 in the engine as well as a concentric location diameter for the drive member 114a.
  • a rotary oil seal 190 is located around the camshaft 50, and this seal can be fitted once the camshaft is in place, but before the actuator 110 is fitted.
  • the actuator 110 can then be fitted to the end of the camshaft 50 and tightened using a drive hex on the front plate 114b, or other features on the drive member. After tightening the actuator 110 in position, the angular
  • orientation of the toothed belt pulley relative to the camshaft can be adjusted to set the camshaft timing
  • the second embodiment also shows a method for incorporating a bias spring 107 into the actuator 110.
  • the bias spring 107 applies a torque between the drive member and the driven member to act against the mean drive torque of the inner shaft. This can be used to balance the actuator phasing response in both directions, or to bias the actuator towards its locked position when there is insufficient oil pressure to control the actuator effectively.
  • the third embodiment of the invention uses a hollow threaded fastener 213 to secure the actuator 210 to the camshaft tube 52, instead of having a direct threaded connection to the camshaft tube 52. This allows the actuator to be fitted in a defined angular orientation.
  • a threaded drive adaptor 203 is permanently fitted to the end of the outer tube 52 by shrink fitting or a similar method.
  • the drive adaptor 203 has a location diameter with a key slot 205 so that the rear plate 214a of the actuator can be positioned concentrically and at the required angular orientation.
  • the outer surface of the actuator plate 214a engages with the rotary seal 290 as the actuator plate 214a is assembled to the drive adaptor 203 and secured to the camshaft by tightening the hollow fastener 213 surrounding the inner shaft 54.
  • the rest of the actuator 210 can be secured using four smaller threaded fasteners 218 and the driven member 220 can then be secured to the inner shaft of the camshaft using the centre bolt 280.
  • a first oil passage 298 is located between the inner surface of the camshaft tube 52 and the outer surface of the inner shaft 54 and passes through the bore of the hollow fastener 213.
  • the second oil passage 296 passes into the inner shaft 54 and through a hole in the centre fixing bolt 280 securing the driven member 220 to the inner shaft 54.
  • these oil feeds are connected to an oil control valve via the front journal bearing of the camshaft.
  • the drive pulley 212 has elongated fixing holes to allow the camshaft timing to be set accurately, but the actuator 210 of the third embodiment could also have a drive pulley fitted in a fixed orientation or combined with another part of the drive member because its orientation relative to the camshaft is defined by the timing key.
  • the hollow fastener 213 it would be possible to extend the camshaft drive adaptor 203 through the rear plate 214a of the actuator 210 and provide an externally threaded portion. The rear plate 214a of the actuator could then be secured in position using a nut.
  • the advantage of the third embodiment is that it allows the actuator 210 to be assembled to the camshaft 50 in a defined angular orientation. Its main disadvantage is that the actuator 210 cannot be fitted as a single unit because the rear plate 214a needs to be fitted and the hollow fastener 213 tightened before the rest of the actuator 210 is fitted.
  • the fourth embodiment of the invention illustrates how the invention can be applied to a double actuator, also known as a twin phaser, in order to control the timing of each of the two groups of cam lobes independently relative to the crankshaft.
  • the actuator 310 has a drive member 312 connected for rotation in synchronism with the crankshaft and two driven members 320a and 320b, the first being connected for rotation with the camshaft outer tube 52, the second connected for rotation with the inner shaft 54.
  • a threaded drive adaptor 303 is permanently fitted to the end of the outer tube 52 by shrink fitting or a similar method.
  • the actuator 310 is designed to be assembled to the camshaft in two parts, the first comprising the drive pulley 312, rear closing plate 314a and a first rotor 320a and stator 321a, the second comprising a separator plate 314c, the second rotor 320b and stator 321b, and the front closing plate 314b.
  • the first part of the actuator is assembled by sliding the rear closing plate 314a on to the camshaft drive adaptor 303, engaging its outer surface with the rotary seal 390 fitted to the cylinder head 392. Then, then the first driven member 320a of the actuator is secured to the drive adaptor 303 by a hollow fastener 313, the correct angular
  • the second part of the actuator 310 can then be fitted to the first driven member, and secured by a group of five threaded fasteners 318, before the centre bolt 380 is tightened to secure the second driven member 320b to the inner shaft 54 of the camshaft. Finally, the sealing cap 382 can be fitted over the centre bolt 380 to seal the actuator oil supply.
  • the angle of the drive pulley is adjustable to allow accurate setting of the camshaft timing the drive pulley being secured in position by the five fasteners 318 securing the two parts of the actuator together.
  • the fourth embodiment also illustrates how the hydraulic connections for controlling the double actuator can be provided from the outer surface of the camshaft drive adaptor 303.
  • a first oil passage is defined between the inner surface of the drive adaptor 303 and the outer surface of the hollow fastener 313, a second passage between the inner surface of the fastener 313 and the outer surface of the inner shaft 54, a third passage between the bore of the inner shaft 54 and the outer surface of the centre bolt 380 and a fourth passage through the centre of the bolt 380.
  • Seals are also provided on the outside of the inner shaft 54 in order to separate the oil flow paths.
  • the fifth embodiment of the invention utilises a separate mounting flange 531 that engages with a splined or form fit connection on the drive adaptor 503 of the camshaft 50 and is retained by a hollow fastener 513 in order to mount the actuator 510.
  • the mounting flange 531 engages into the rotary seal 590 mounted into the cylinder head and a seal 533 is used to prevent any oil leakage between the actuator 510 and the mounting flange 531.
  • This arrangement allows the actuator 510 to be
  • the stator of the electric actuator 510 is secured to the flange 531 mounted on the camshaft 50 by four
  • threaded fasteners 518 and the rotor 520 of the actuator 510 is engaged by a spline or form fit connection to the inner shaft 54 of the camshaft and is axially retained via a central bolt 580.
  • the actuator 510 is engaged via a drive coupling with an electric motor 521 mounted by fastenings 517 to a stationary part 519 of the engine.
  • the rotational speed of the motor 521 is variable relative to the camshaft rotational speed in order to advance or retard the timing of the inner shaft 54 relative to the outer tube 52 of the camshaft 50.
  • a second rotary seal 541 mounted to the electric motor 521 engages with a cylindrical surface 543 on the actuator 510 to enclose the drive coupling such that it can be lubricated during operation without any oil contamination of the timing belt .
  • the proposed invention has the following advantages when compared to existing designs: -
  • the actuator of the invention can be used for concentric camshaft applications where 100% oil sealing is required.
  • the design is applicable to both hydraulic and electric actuators.
  • the design can be adapted for both single and double actuator applications
  • the actuator drive connections can be used to define hydraulic connections between the actuator and the concentric camshaft.
  • the actuator is able to control the axial location of the inner drive shaft inside the camshaft tube.
  • the invention is compatible with a variety of common procedures for setting the camshaft timing.

Landscapes

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

Abstract

L'invention concerne un moteur comprenant un ensemble arbre à cames réglable (50) ayant des premier (56) et second (58) groupes de lobes de came et un actionneur ('10) pour faire varier la phase d'au moins l'un des groupes de lobes de came (56, 58) par rapport à un vilebrequin du moteur. L'ensemble arbre à cames (50) est du type connu sous le nom arbre à cames concentrique et l'actionneur ('10) comprend un élément d'entraînement ('14a,'14b) et un ou plusieurs éléments entraînés ('20) qui peuvent tourner par rapport à l'élément d'entraînement, les groupes de lobes de came de l'ensemble arbre à cames réglable étant chacun reliés pour une rotation avec un élément respectif parmi l'élément d'entraînement et l'élément entraîné (s) de l'actionneur. Selon l'invention, l'actionneur ('10) est apte à être monté sur l'ensemble arbre à cames (50) pour établir une liaison d'entraînement entre le tube externe (52) et l'arbre interne (54) de l'ensemble arbre à cames (50) et les éléments respectifs ('14a,'14b;'20) de l'actionneur ('10), après que l'ensemble arbre à cames a été monté sur le moteur, et un joint annulaire étanche à l'huile ('90) est monté sur le moteur autour de l'ensemble arbre à cames (50) pour venir en prise de manière coulissante avec une surface de l'actionneur ('10) pour retenir l'huile à l'intérieur d'un compartiment du moteur logeant l'ensemble arbre à cames.
PCT/IB2018/057717 2017-10-05 2018-10-04 Moteur doté d'un arbre à cames concentrique WO2019069265A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17195055.3 2017-10-05
EP17195055.3A EP3467274A1 (fr) 2017-10-05 2017-10-05 Moteur comportant un arbre à cames concentrique

Publications (1)

Publication Number Publication Date
WO2019069265A1 true WO2019069265A1 (fr) 2019-04-11

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PCT/IB2018/057717 WO2019069265A1 (fr) 2017-10-05 2018-10-04 Moteur doté d'un arbre à cames concentrique

Country Status (2)

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EP (1) EP3467274A1 (fr)
WO (1) WO2019069265A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008019745A1 (de) 2008-04-19 2009-10-22 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102008023066A1 (de) * 2008-05-09 2009-11-12 Hydraulik-Ring Gmbh Nockenwellenverstellung mit trockener Lauffläche
DE102008032412A1 (de) * 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
WO2017140351A1 (fr) 2016-02-16 2017-08-24 Volvo Truck Corporation Dispositif permettant de commander au moins une soupape dans un moteur à combustion interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008019745A1 (de) 2008-04-19 2009-10-22 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102008023066A1 (de) * 2008-05-09 2009-11-12 Hydraulik-Ring Gmbh Nockenwellenverstellung mit trockener Lauffläche
DE102008032412A1 (de) * 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
WO2017140351A1 (fr) 2016-02-16 2017-08-24 Volvo Truck Corporation Dispositif permettant de commander au moins une soupape dans un moteur à combustion interne

Also Published As

Publication number Publication date
EP3467274A1 (fr) 2019-04-10

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