EP0422791A1 - Kompakter Nockenwellenantrieb mit variabler Ventilzeitsteuerung - Google Patents

Kompakter Nockenwellenantrieb mit variabler Ventilzeitsteuerung Download PDF

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Publication number
EP0422791A1
EP0422791A1 EP90310453A EP90310453A EP0422791A1 EP 0422791 A1 EP0422791 A1 EP 0422791A1 EP 90310453 A EP90310453 A EP 90310453A EP 90310453 A EP90310453 A EP 90310453A EP 0422791 A1 EP0422791 A1 EP 0422791A1
Authority
EP
European Patent Office
Prior art keywords
cam phaser
variable cam
piston
oil
pistons
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
EP90310453A
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English (en)
French (fr)
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EP0422791B1 (de
Inventor
Michael Joseph Niemiec
Thomas Howard Lichti
Michael Edward Mccarroll
Kenneth Anthony Kovacevich
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.)
Motors Liquidation Co
Original Assignee
Motors Liquidation Co
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 Motors Liquidation Co filed Critical Motors Liquidation Co
Publication of EP0422791A1 publication Critical patent/EP0422791A1/de
Application granted granted Critical
Publication of EP0422791B1 publication Critical patent/EP0422791B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]

Definitions

  • This invention relates to phase-adjusting drives and especially to camshaft phasing devices for varying the timing of valve actuation by an engine-­driven camshaft.
  • variable valve timing devices employed have been camshaft phasing devices, often in the form of drive pulleys and the like incorporating phase-­changing means for varying the phase between a rotatably-driving input member such as a gear, pulley or sprocket and a rotatably-driven output member such as a camshaft.
  • a rotatably-driving input member such as a gear, pulley or sprocket
  • a rotatably-driven output member such as a camshaft.
  • the pertinent prior art are mechanisms having splined pistons which are hydraulically actuated against a spring to vary the phasing of outwardly and inwardly engaged drive and driven members. Such arrangements are shown for example in US-A-4,231,330 (Garcea) and US-A-4,811,698 (Akasaka et al).
  • the present invention extends the concepts of the prior art to provide an especially compact and effective form of phase-adjusting (or hereinafter termed as "phasing") drive.
  • the invention is used as a variable cam phaser (VCP) applied in an engine camshaft drive to vary the phase or timing of a driven camshaft relative to a driving member, such as a sprocket, pulley or gear, that is driven in timed relation to an engine crankshaft or the like.
  • VCP variable cam phaser
  • a feature of the invention is that multiple return springs engage one of a pair of axially-spaced inwardly-biased (i.e,towards one another) anti-backlash annular drive pistons in such a manner as to minimize anti-backlash friction during return motions of the pistons.
  • An extremely compact assembly results from the arrangement in which the springs extend from a front cover through one of the pistons into engagement with the more distant of the two pistons.
  • a further feature is that wave spring washers are used with headed pins for biasing of the helically-splined annular drive pistons towards one another to take up the backlash in a limited length assembly.
  • a thin sheet oil seal is provided adjacent the inner piston having teeth closely fitted or conformed to a mating hub and shaft to minimize leakage of pressure oil past the drive pistons.
  • the seal may be bonded to the pressure side of the inner drive piston. Additionally or alternatively, sealing may be aided by filling the valleys of the splines with a deformable material such as wax, epoxy resin, metal or plastics material. Either sealing method is consistent with the intent of minimizing the length of the phasing means to provide a compact VCP.
  • numeral 10 generally indicates an internal combustion engine of a type having a camshaft 11 driven by a crankshaft, not shown, through a chain 12 or other suitable drive means.
  • the camshaft 11 carries a plurality of cams (not shown) for actuating cylinder intake and/or exhaust valves (not shown) of the engine in known manner. It is supported in part by an enlarged front bearing journal 13 that is carried in a suitable bearing within a front wall 14 of an engine cylinder head or camshaft carrier.
  • VCP variable cam phaser
  • the sprocket comprises a drive member with a peripheral drive portion, i.e., wheel 18, that is toothed and is drivably engaged by the chain 12 for rotatably driving the sprocket 16 on an axis 19 that is co-axial with the camshaft 11.
  • a forwardly-extending large front hub 20 and a rearwardly-extending smaller rear hub 22 Within the wheel 18 is a forwardly-extending large front hub 20 and a rearwardly-extending smaller rear hub 22.
  • the rear hub 22 abuts the front end of the camshaft front journal 13 and the VCP assembly is enclosed within a housing 23 and cover 24 mounted on the engine front wall 14.
  • the VCP assembly 15 further includes a stubshaft in the form of a spline shaft 26 having an external helical spline 27 at one end and a finished journal 28 at the other.
  • the journal end is secured through a central opening 29 to the front end of the camshaft by a screw 30, with a dowel pin 31 received in openings 32, 34 of the spline shaft 26 and camshaft 11 to maintain a fixed drive relationship between the two shafts.
  • a bowed retaining ring 35 engaging a groove 36 between the spline and journal ends of the spline shaft 26, bears against the sprocket wall adjacent the smaller hub 22 to hold the sprocket hub in position against the camshaft.
  • the axial spring force applied by the bowed ring 35 prevents axial displacement of the sprocket that would otherwise occur when torque reversals on the camshaft are transmitted through the helical splines.
  • the journal end of the hub 22 is carried for oscillating motion on the journal 28.
  • the splined end of the spline shaft 26 extends forward within the front hub 20 concentric with the inner diameter 38 thereof.
  • a sleeve 39 having an internal helical spline 40 is fitted within the hub 20 and is maintained in fixed driving relation by a drive pin 42 or any other suitable means such as shrink-fitting or an adhesive.
  • Use of the splined sleeve insert 39 simplifies manufacturing and shortens the axial length by avoiding the need for an undercut at the inner end of the internal spline.
  • the facing splines 27, 40 have opposite and, preferably, equal leads (or helix angles) to provide for the phasing action to be later described.
  • both splines Between and engaging both splines are two axially-spaced annular drive pistons, called, for convenience, an outer piston 43 and an inner piston 44, the latter being closer to the inner sprocket wall.
  • Both pistons have inner and outer helical splines drivingly mated with the splines 27, 40 of the spline shaft 26 and sleeve 39 respectively.
  • the splines are mis-aligned so that, when the pistons are urged inwardly towards one another, they engage opposite sides of the mated splines 27, 40 and thus take up the lash that would otherwise occur in transferring drive torque between the sprocket 16 and spline shaft 26.
  • the pistons 43, 44 are urged, i.e., biased, towards one another and are maintained in a drive piston assembly 45 by annularly spaced pins 46 press-fitted in the inner pistons 44 and having heads 47 compressing wave spring washers 48 in recesses 50 on the far side of the outer pistons 43.
  • the short axial length of the spring washers contributes to the compactness of the VCP 15.
  • An oil seal 51 formed of a thin sheet of preferably formable material such as an elastomer or oil-resistant plastics is mounted against and preferably bonded, or otherwise secured, to the inside face of the inner piston 44 of assembly 45.
  • the seal 51 may be made with teeth originally mating with the splines 27, 40 with a close or slight interference fit. The teeth are worn or deformed upon installation to closely fitting conformity with their mating splines. In this way a highly effective seal against oil loss through the splines is provided.
  • the valleys of the splines of the inner piston 44 and its mating external and internal splines 27, 40 may be filled with a deformable or shearable material such as wax, plastics or soft metal to minimize the leak paths therethrough.
  • a deformable or shearable material such as wax, plastics or soft metal to minimize the leak paths therethrough.
  • the deformable material on the splines could be used instead of the thin seal 51. Both means avoid axial extension of the unit in order to provide an oil seal.
  • the seal 51 together with the splines 27, 40 and the adjacent wall of the sprocket define an annular chamber 52.
  • Engine oil pressure may be supplied to or discharged from this chamber through connecting oil passages 54 in the spline shaft 26 and 55 in the camshaft journal 13 that leads to an annular groove 56.
  • the groove is connected through schematically-illustrated passage means 58 with any suitable form of three-way valve such as solenoid valve 59 which operates to supply pressure oil from an oil gallery 60 or to drain oil to a discharge line 62 whilst blocking the flow from the gallery 60.
  • the piston assembly 45 is urged in a direction compressing the chamber 52 by eight (or any suitable number of) coil return springs 63 that extend between the ends of recesses 64 in the inner piston 44 and through apertures in the outer piston 43 to an inner face of a cover 66 that is threaded or otherwise retained on the outer hub 20.
  • the arrangement significantly contributes to axial compactness of the VCP.
  • valve 59 when the control valve 59 is not energized the valve 59 preferably closes off the gallery 60 and opens the annular chamber 52 to the drain line 62.
  • the springs 63 are thus able to maintain the drive piston assembly 45 to its extreme inner position near the sprocket wall whereby the volume of the annular chamber 52 is held at a minimum.
  • the camshaft is preferably maintained by the piston assembly 45 in a retarded phase relation with the sprocket for operation of the actuated engine valves under desired retarded timing conditions.
  • the solenoid valve When the engine operating conditions call for advanced valve timing, the solenoid valve is energized, to close off the drain line 62 and to open the gallery 60 to supply pressurized engine oil to the annular chamber 52 in the VCP 15.
  • the oil pressure moves the piston assembly 45 against the bias of springs 63 to the extreme opposite position adjacent the cover 66. Because of the opposite lead of the inner and outer helical splines 27, 40, the outward motion of the piston assembly 45 advances the timing or phase angle of the camshaft relative to the sprocket so that the timing of the associated engine valves is likewise advanced.
  • a return to retarded timing when called for is accomplished by de-energizing the solenoid valve 59, blocking oil flow from the pressure gallery 60 and allowing the VCP annular chamber 52 to drain to line 62.
  • the springs 63 then return the piston assembly 45 to its initial retarded position adjacent the sprocket inner wall.
  • valve 59 to control oil flow has the advantage that oil flow is used only for the purpose of advancing the camshaft timing and is shut off at other times. In this way the capacity and power requirements of the engine oil pump may be lessened.
  • any other suitable type of valve and supply arrangement may be used to control the oil flow to and from the annular chamber 52.
  • the valve and oil passages may be arranged in any desired manner and located in any appropriate location to accomplish the purpose without departing from the invention.
  • the pistons 43, 44 of the assembly 45 are also the means through which all torque is transferred from the sprocket 16 to the camshaft 11 and vice versa via their helical splines and the mating splines 27, 40.
  • the mis-alignment of the piston splines and their biasing towards one another by the pins 46 and wave washers 48 takes up any clearance lash in the spline connections by urging the pistons 43, 44 into engagement with opposite sides of the engaged splines 27, 40 as was previously described.
  • the passing of the return springs 63 through openings, not numbered, in the outer piston 43 to extend between recesses 64 in the inner piston and the inside of the cover 66 has dual benefits.
  • the overall length of the VCP unit 15 is thereby shortened while the length of the return springs remains relatively long to provide for adequate axial motion of the piston assembly 45.
  • the pulling of the outer piston 43 behind the inner piston 44 as it is moved inwards by the return springs tends to increase slightly the separation of the pistons from one another and thereby reduce the lash take-up force, thus reducing the friction that opposes the return motion of the piston assembly.
  • the required force of the return springs may thereby be reduced.
  • Figure 4 discloses an embodiment of the invention for use with a reinforced rubberlike timing belt drive. Such drive belts are in current use and require an environment that is relatively free of oil.
  • an engine 67 of Figure 4 carries a camshaft 68 with a front bearing journal 70 and an outwardly adjacent seal flange 71.
  • a seal 72 engages the flange outer surface to prevent oil leakage into an adjacent camshaft drive housing 74.
  • a variable cam phaser (VCP) or phase adjuster 75 is mounted on the front end of camshaft 68.
  • the VCP includes a pulley 76 having an outer toothed wheel 78 driven by a timing belt 79 and connected with an inner hub 80.
  • the hub includes an end wall 82 having a seal-carrying central opening 83 that is journalled on a finished journal end 84 of a spline shaft 86.
  • a screw 87 secures the spline shaft 86 to the camshaft 68 in a manner similar to that shown in Figure 1.
  • the hub 80 receives a sleeve 88 having helical internal splines 90 that concentrically oppose helical external splines 91 of opposite lead on the projecting outer end of the spline shaft 86. These splines are engaged by a lash-free piston assembly 45 with oil seal 51 inwardly biased by return springs 63 as in Figure 1.
  • the springs 63 are seated in an annular cover 92 sealingly secured in the hub 80 and sealingly engaging a seal surface 94 near the end of the spline shaft 86.
  • the VCP 75 defines an annular chamber 52 which is communicated with a source of oil under pressure or drained through passages 54, 55 in the spline shaft 86 and camshaft 68 in the same manner as in Figure 1.
  • the operation of these portions of the VCP 75 is the same as previously described in the embodiment shown in Figures 1-3.
  • FIG. 5 illustrates another embodiment of VCP 100 which includes a sprocket 101, spline shaft 102, retaining ring 104, sleeve 105, drive piston assembly 106, return springs 108 and cover 109 which, although of slightly differing form, are the functional equivalents of the corresponding parts of the Figure 1 embodiment.
  • Figure 5 differs in that a screw 110 that secures the spline shaft 102 to the camshaft, not shown, also incorporates a three-way oil control valve.
  • the threaded shank of the screw has an axial feed passage 111 for receiving oil under pressure from a gallery, not shown, in the centre of the camshaft.
  • passage 111 connects with a valve chamber 112 having opposed first and second valve seats 114, 115.
  • Cross-­passages 116 lead transversely from the valve chamber 112 to an annular space 118 that is connected by a duct 119 to an annular chamber 120 that borders on the piston assembly 106.
  • a pintle 121 having a head seatable on the valve seats 114, 115 and a stem 122 extending axially into a socket 123 provided for driving the screw 110. Drain grooves 124 in a seat insert around the stem 122 connect the valve chamber 112 to drain.
  • a solenoid actuator not shown, or other suitable actuating means may be mounted on the associated engine in a position to engage the stem 122 of the valve pintle 121 when desired.
  • a seal ring 125 around the head of the screw 110 closes a leakage path for oil under pressure from the annular space 118.
  • the solenoid actuator would normally be biased against the stem 122 with a force sufficient to seat the pintle 121 against the first valve seat 114, thereby cutting off pressure oil flow and discharging any oil in the annular chamber 119 through the drain grooves 124.
  • Energizing the solenoid actuator would release the force on the stem 122, allowing the pintle 121 to be forced off the first seat 114 and seated on the second seat 115 by the force of engine oil pressure in the feed passage 111. This closes the drain grooves 124 and allows pressure oil to flow to the annular chamber 120 to actuate the drive piston assembly 106 in the manner previously described with the other embodiments. De-energizing the solenoid actuator would return the system to the previous condition.
  • the arrangement has the advantage of providing a compact internal control valve for use with applications of the variable cam phaser (VCP) of the invention in appropriate engine configurations.
  • VCP variable cam phaser
EP19900310453 1989-10-10 1990-09-25 Kompakter Nockenwellenantrieb mit variabler Ventilzeitsteuerung Expired - Lifetime EP0422791B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US41801989A 1989-10-10 1989-10-10
US418019 1989-10-10

Publications (2)

Publication Number Publication Date
EP0422791A1 true EP0422791A1 (de) 1991-04-17
EP0422791B1 EP0422791B1 (de) 1994-01-05

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EP19900310453 Expired - Lifetime EP0422791B1 (de) 1989-10-10 1990-09-25 Kompakter Nockenwellenantrieb mit variabler Ventilzeitsteuerung

Country Status (6)

Country Link
EP (1) EP0422791B1 (de)
JP (1) JPH0694803B2 (de)
AU (1) AU610784B1 (de)
BR (1) BR9005041A (de)
CA (1) CA2025058C (de)
DE (1) DE69005776T2 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0518529A1 (de) * 1991-06-11 1992-12-16 Borg-Warner Automotive Transmission And Engine Components Corporation Variable Zeitsteuervorrichtung für eine riemenangetriebene Nockenwelle
GB2261931A (en) * 1991-11-28 1993-06-02 Atsugi Unisia Corp Valve timing control system for internal combustion engine
WO1994016203A1 (de) * 1992-12-30 1994-07-21 Meta Motoren- Und Energie-Technik Gmbh Vorrichtung zur variablen steuerung der ventile von brennkraftmaschinen, insbesondere zur drosselfreien laststeuerung von ottomotoren
US5447126A (en) * 1993-11-18 1995-09-05 Unisia Jecs Corporation Variabe cam phaser for internal combustion engine
EP0742350A2 (de) * 1995-05-11 1996-11-13 Carraro S.P.A. Eine mechanische Vorrichtung zur Veränderung der Phasenbeziehung zwischen der Antriebswelle und einer Nockenwelle einer Brennkraftmaschine
US5722356A (en) * 1995-08-09 1998-03-03 Unisia Jecs Corporation Camshaft phase changing device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10356908B4 (de) * 2003-12-02 2007-11-22 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung für Verbrennungskraftmaschinen von Fahrzeugen, vorzugsweise Kraftfahrzeugen

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2019613A (en) * 1978-04-22 1979-10-31 Bosch Gmbh Robert Improvements in fuel injection pumps
GB2157364A (en) * 1984-02-07 1985-10-23 Alan John Graham I.C. engine variable valve timing device
US4811698A (en) * 1985-05-22 1989-03-14 Atsugi Motor Parts Company, Limited Valve timing adjusting mechanism for internal combustion engine for adjusting timing of intake valve and/or exhaust valve corresponding to engine operating conditions

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1093715B (it) * 1978-03-24 1985-07-26 Alfa Romeo Spa Variatore di fase della distribuzione per motore alternativo a combustione interna
JPS55119310U (de) * 1979-02-19 1980-08-23
JPS598642A (ja) * 1982-07-05 1984-01-17 Tsuchiya Chem Kk 剥離性被膜塗料によるガラスの着色法
US4601266A (en) * 1983-12-30 1986-07-22 Renold Plc Phasing device for machine applications
US4811694A (en) * 1987-03-24 1989-03-14 Holmquist Melvin L Bird feeder with scale

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2019613A (en) * 1978-04-22 1979-10-31 Bosch Gmbh Robert Improvements in fuel injection pumps
GB2157364A (en) * 1984-02-07 1985-10-23 Alan John Graham I.C. engine variable valve timing device
US4811698A (en) * 1985-05-22 1989-03-14 Atsugi Motor Parts Company, Limited Valve timing adjusting mechanism for internal combustion engine for adjusting timing of intake valve and/or exhaust valve corresponding to engine operating conditions

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5361735A (en) * 1989-10-16 1994-11-08 Borg-Warner Automotive Transmission & Engine Components Corporation Belt driven variable camshaft timing system
EP0518529A1 (de) * 1991-06-11 1992-12-16 Borg-Warner Automotive Transmission And Engine Components Corporation Variable Zeitsteuervorrichtung für eine riemenangetriebene Nockenwelle
GB2261931A (en) * 1991-11-28 1993-06-02 Atsugi Unisia Corp Valve timing control system for internal combustion engine
US5309873A (en) * 1991-11-28 1994-05-10 Atsugi Unisia Corporation Valve timing control system for internal combustion engine
GB2261931B (en) * 1991-11-28 1995-01-11 Atsugi Unisia Corp Valve timing control system for internal combustion engine
WO1994016203A1 (de) * 1992-12-30 1994-07-21 Meta Motoren- Und Energie-Technik Gmbh Vorrichtung zur variablen steuerung der ventile von brennkraftmaschinen, insbesondere zur drosselfreien laststeuerung von ottomotoren
US5447126A (en) * 1993-11-18 1995-09-05 Unisia Jecs Corporation Variabe cam phaser for internal combustion engine
EP0742350A2 (de) * 1995-05-11 1996-11-13 Carraro S.P.A. Eine mechanische Vorrichtung zur Veränderung der Phasenbeziehung zwischen der Antriebswelle und einer Nockenwelle einer Brennkraftmaschine
EP0742350A3 (de) * 1995-05-11 1997-05-02 Carraro Spa Eine mechanische Vorrichtung zur Veränderung der Phasenbeziehung zwischen der Antriebswelle und einer Nockenwelle einer Brennkraftmaschine
US5722356A (en) * 1995-08-09 1998-03-03 Unisia Jecs Corporation Camshaft phase changing device

Also Published As

Publication number Publication date
CA2025058C (en) 1995-01-03
JPH0694803B2 (ja) 1994-11-24
AU610784B1 (en) 1991-05-23
EP0422791B1 (de) 1994-01-05
CA2025058A1 (en) 1991-04-11
BR9005041A (pt) 1991-09-10
DE69005776D1 (de) 1994-02-17
DE69005776T2 (de) 1994-05-11
JPH03134209A (ja) 1991-06-07

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