EP0903471B1 - Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne - Google Patents

Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne Download PDF

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Publication number
EP0903471B1
EP0903471B1 EP98890262A EP98890262A EP0903471B1 EP 0903471 B1 EP0903471 B1 EP 0903471B1 EP 98890262 A EP98890262 A EP 98890262A EP 98890262 A EP98890262 A EP 98890262A EP 0903471 B1 EP0903471 B1 EP 0903471B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
electric motor
gear
planetary gear
planet
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.)
Expired - Lifetime
Application number
EP98890262A
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German (de)
English (en)
Other versions
EP0903471A1 (fr
Inventor
Siegfried Ing. Heer
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.)
TCG Unitech AG
Original Assignee
TCG Unitech AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AT0158697A external-priority patent/AT407282B/de
Application filed by TCG Unitech AG filed Critical TCG Unitech AG
Publication of EP0903471A1 publication Critical patent/EP0903471A1/fr
Application granted granted Critical
Publication of EP0903471B1 publication Critical patent/EP0903471B1/fr
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
    • 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
    • F01L1/352—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 bevel or epicyclic 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to a device for adjusting the camshaft an internal combustion engine with an adjustment mechanism, the one with the camshaft or with the drive wheel firmly connected electric motor is operated.
  • the camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.
  • DE 41 10 088 C and DE 39 29 619 A are adjusting devices known in which between one connected to the camshaft Component and a component connected to the drive wheel Adjustment element is provided, which has two helical gears that with corresponding toothing of the camshaft or the drive wheel in engagement stand.
  • An axial displacement of this adjustment element can Rotation of the camshaft relative to the drive wheel can be caused.
  • a The possibility of axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is operated.
  • the disadvantage of this solution is that to achieve the necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort.
  • the oil consumption is due to the actuation of the piston relatively large, which is a load on the engine by a corresponding Oil pump represents.
  • switched the camshaft only between two end positions become.
  • an electrical adjustment device is known from DE 41 01 676A, in which an electric motor is provided, the adjusting element via a threaded spindle shifts.
  • an axial thrust bearing can be provided, which the relative movement between the torsion-resistant and the rotating component.
  • This thrust bearing is with the known solution practically during the entire engine operation because it acts between the drive wheel and the camshaft Torsional moments always exert a force acting on the adjusting element in the axial direction is exercised.
  • This thrust bearing is therefore a critical component that limits the life of the engine.
  • an adjusting mechanism is known from GB 2 221 513 A, in which an electric motor is provided which is fixedly connected to the drive wheel which drives the camshaft.
  • the electric motor drives a screw spindle on the an adjusting element is guided, which with a Camshaft and via a second group of levers with the drive wheel in Connection is established. By operating the electric motor this way rotation of the camshaft relative to the drive wheel can be brought about.
  • Such a device is very complex and requires a relatively large one Installation space.
  • DE 36 07 256 A shows an adjustment device in which the adjustment the camshaft is done by a stepper motor, which is fixed to the drive wheel connected is.
  • this stepper motor has to absorb all the torque, that is required to drive the camshaft.
  • Such a stepper motor decides due to the required size and power consumption the practical use.
  • the US 5,293,845 A shows an adjusting mechanism for a camshaft, the has a planetary gear.
  • a fixed electric motor causes one Phase shift of the camshaft.
  • the disadvantage is that the power transmission for driving the camshaft via the rotating gear wheels of the Planetary gear takes place, so that the limited efficiency of the planetary gear leads to the corresponding losses. It also shifts at one Adjustment of the axis of the drive wheel, which is due to complex clamping mechanisms is to be balanced.
  • EP 0 234 853 A shows a device for adjusting a camshaft which is adjusted via a harmonic drive gear.
  • a transmission consists of an internally toothed gear and an elliptical deformable Gear that meshes with the internally toothed gear. The resilience and life of such a transmission has certain limits that it do not appear suitable for all applications.
  • the object of the present invention is to provide a device in which the disadvantages described above can be avoided, and in particular it enables quick and reliable adjustment in a simple manner to enable the camshaft. in particular, the device should have little installation space claim, so that an independent adjustment of two Camshafts with a small axial distance is possible.
  • the adjustment mechanism Planetary gear includes.
  • a planetary gear Adjustment elements that move in the axial direction can be avoided.
  • the mechanical structure can be simplified and a small size can be achieved.
  • Another advantage of the invention is that it is relative is simple to ensure a secure oil seal, so the electric motor runs in the dry.
  • the planetary gear preferably has a large reduction ratio, which is preferably greater than 1: 8 and particularly preferably greater than 1:12. Such a reduction ratio may result in self-locking be achieved or at least approximately achieved. On in this way, the electric motor during normal operation of the internal combustion engine, where there is no adjustment, no or only minimal load. This increases the service life and reduces the amount of energy required.
  • the electric motor and an internally toothed gear of the planetary gear are firmly connected to the drive wheel.
  • the planet carrier is preferred of the planetary gear firmly connected to the camshaft.
  • the output shaft the electric motor stands in this case with the sun gear of the planetary gear in connection. This allows a relatively large reduction ratio can be achieved.
  • the planetary gear consists only of an internally toothed gear and a planet carrier with a single planet gear mounted thereon.
  • a sun gear is not provided in such a planetary gear.
  • the number of teeth of the planetary gear is preferably only slightly smaller than the number of teeth of the internally toothed gear, preferably by one. This means that the axis of the planet gear is only slightly opposite the axis of the internally toothed gear is shifted. Stand this way always several teeth of these gears meshing simultaneously, so that one very favorable situation with regard to the load is given.
  • Such The device can therefore be made extremely compact, so that even close distance two camshafts can be adjusted independently can.
  • a large reduction ratio is achieved in this way, what is favorable in view of the required size of the electric motor is.
  • the electric motor is firmly connected to the camshaft is and that the planet gear via a synchronous clutch with the drive gear connected is.
  • the synchronous clutch for example as an Oldham clutch is formed, the axial offset of the planet gear and Drive wheel off.
  • the electric motor is fixed to the drive wheel is connected and that the planet gear via a synchronous clutch is connected to the camshaft.
  • the planet carrier as an output shaft of the electric motor is formed, which has a desaxed section where the planet gear is mounted.
  • Precise control of the adjustment angle can be achieved in that the electric motor is designed as a stepper motor.
  • the present invention relates to an internal combustion engine Combustion having a device as described above.
  • FIG. 1 a first embodiment variant the present invention in longitudinal section
  • Fig. 2 another Embodiment variant of the present invention in longitudinal section
  • Fig. 3 shows the variant of Fig. 2 in a section along line III - III in Fig. 2, wherein to increase clarity, individual components are not shown
  • the Fig. 4 is an exploded view of the embodiment of Figures 2 and 3
  • 5 shows a detail of this embodiment variant.
  • a first embodiment variant of the present invention is shown in FIG. 1.
  • a bracket 30 is rotatable on a camshaft 1, but axially fixed immovably.
  • On this bracket 30 is on the outer circumference Toothed 36 is provided, which is used to hold a toothed belt, which Drives camshaft 1 and thus represents the drive wheel.
  • the bracket 30 further carries a plate 31 on which an electric motor 15 is fixedly attached.
  • the Electric motor 15 thus rotates together with the drive wheel 36
  • Slip rings 19 are provided, which are fed by fixed sliding contacts 41 become.
  • the pinion 32 of the electric motor 15 stands over planet gears 33, 34 with a ring gear, i.e. an internally toothed gear 35 which is integrally formed in the bracket 30.
  • a planet carrier 37, the planet gears 33, 34 rotatably carries, is fixedly connected to the camshaft 1. If the electric motor 15 is not controlled, the pinion 32 is related to the Motor 15 silent, and thus pinion 32 and planet carrier 37 rotate with the Speed of the drive wheel 36, which also causes the camshaft 1 at this speed rotates. By controlling the electric motor 15, a relative movement can of the planet carrier 37 can be effected in relation to the drive wheel 36. The relatively large translation by the planetary gear ensures that the correspondingly large torques for adjusting the camshaft 1 a relatively underpowered electric motor 15 can be made available can. The sealing of the system against the oil space in the area of Camshaft 1 takes place via radial shaft sealing rings 38 and 39. A screw 40 is used to attach the planet carrier to camshaft 1.
  • the planetary gear consisting of the gears 32, 33, 34 and 35, be carried out in a known manner without play.
  • these gears 32 to 35 can be made of high-strength Be made of plastic.
  • the camshaft 1 has its End of a flange 2.
  • a drive wheel is on the flange 2 via a slide bearing 42 6 for the camshaft 1, which has a toothing 6a on its circumference Includes a drive chain, not shown.
  • Via threaded bolts 8 a holding body 43 is connected to the flange 2.
  • the threaded bolts 8 kick thereby through openings 10 in the drive wheel 6, which are arcuate Elongated holes are formed. This is the angular range of the adjustment the camshaft 1 defined.
  • a shaft nut 44 is on the holding body 43 attached, which carries an electric motor 15 via screws 45. As with the previous one Design variant is the electric motor 15 via slip rings 19 and Sliding contacts 41 supplied with power.
  • the output shaft 29 of the electric motor 15 is on the holding body via roller bearings 46 and 47 43 and mounted on the shaft nut 44 and has on the motor 15 distal end a desaxed section 48.
  • the bearings 46 and 47 are held in the axial direction by locking rings 49.
  • On the daxed Section is mounted on a needle bearing 50, a planet gear 51, which with a internally toothed gear 52 is engaged, which is integral with the holding body 43 is formed.
  • An axial plain bearing bush 53 secures the planet gear 51 in Axial direction.
  • the planet gear 51 is a so-called Oldham clutch 54 Constant velocity joint represents, with the drive wheel 6 in rotary connection.
  • the Oldham coupling 54 has an engagement part 55 which is connected to the planet gear 51 a slide guide 56 communicates which limits movement of the Engagement part 55 relative to the planet gear 51 in the plane of FIG. 2 allows.
  • the engagement part 55 stands with an adapter 58 of the drive wheel 6 via a further sliding guide 57 in connection, which has a limited movement of the engaging part 55 with respect to the drive wheel 6 in the plane of FIG. 3 enables. In this way it is possible to get the drive torque from the drive wheel 6 to be transferred to the planet gear 51, the eccentricity s being overcome becomes. Screws 59 connect the adapter 58 to the sprocket 6 and simultaneously secure the engaging part 55.
  • a housing 60 with a radial shaft seal 61 opposite the holding part 43 is sealed, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, like the electric motor 15.
  • the structure of the planetary gear is shown in FIG. 5.
  • the internally toothed Gear 52 in the holding body 43 has fourteen teeth, while the planet gear 51 has thirteen teeth.
  • the tip circle of the planet gear 51 approximately touches the tip circle of the internal gear 52. In this way, about half of all Teeth always engaged, which reduces the tooth flank load. Therefore, it can Planetary gears are designed to be very compact. It also causes one revolution the output shaft 29 of the electric motor 15 only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load of the electric motor can also be minimized.
  • the present invention makes it possible to control the valve timing Change internal combustion engine in a simple and safe way. Particularly advantageous is that any intermediate positions can also be controlled.

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

Claims (11)

  1. Dispositif pour l'entraínement d'un arbre à cames (1) d'un moteur à combustion interne avec un mécanisme d'entraínement qui est commandé par un moteur électrique (15) solidaire rigidement de l'arbre à cames, lequel moteur est alimenté en courant par des balais, caractérisé en ce que le mécanisme d'entraínement comprend un engrenage planétaire et en ce que la roue planétaire (51) est solidaire, par l'intermédiaire d'un couplage (54) d'une roue d'entraínement (6) de l'arbre à cames (1).
  2. Dispositif pour l'entraínement d'un arbre à cames (1) d'un moteur à combustion interne avec un mécanisme d'entraínement qui est commandé par un moteur électrique (15) solidaire d'une roue d'entraínement (36) d'un arbre à cames (1), lequel moteur (15) est alimenté en courant par des balais, caractérisé en ce que le mécanisme d'entraínement comprend un engrenage planétaire et en ce que la roue planétaire (51) est solidaire, par l'intermédiaire d'un couplage (54) avec l'arbre à cames (1).
  3. Dispositif selon la revendication 1 ou la revendication 2, caractérisé en ce que l'engrenage planétaire présente un rapport de transmission élevé, qui est, de préférence, supérieur à 1 : 8 et surtout, supérieur à 1 : 12.
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que l'engrenage planétaire peut être bloqué par rapport à l'entraínement de l'arbre à camés (1), grâce à la roue d'entraínement (6, 36).
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le moteur électrique (15) et une roue dentée (35) à dents internes de l'entraínement planétaire est solidaire de la roue d'entraínement (36).
  6. Dispositif selon la revendication 5, caractérisé en ce que la cage de transmission planétaire (37) de l'engrenage planétaire est solidaire de l'arbre à cames (1).
  7. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que l'engrenage planétaire est constitué seulement d'une roue dentée (52) à dents internes et d'une cage de transmission planétaire (48) avec une roue planétaire unique (51) disposée sur celle-ci.
  8. Dispositif selon la revendication 7, caractérisé en ce que le nombre de dents de la roue planétaire (51) est légèrement inférieur au nombre de dents de la roue dentée à dents internes (52) et, de préférence, par une dent.
  9. Dispositif selon la revendication 7 ou la revendication 8, caractérisé en ce que la cage de transmission (48) est réalisée en tant que partie de l'arbre d'entraínement (29) du moteur électrique (15), qui présente une portion désaxée (48) sur laquelle est placée la roue planétaire (51).
  10. Dispositif selon l'une des revendications 1 à 9, caractérisé en ce que le moteur électrique (15) est réalisé sous la forme d'un moteur pas à pas.
  11. Moteur à combustion interne, caractérisé en ce qu'il comporte un dispositif selon l'une des revendications 1 à 10.
EP98890262A 1997-09-19 1998-09-10 Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne Expired - Lifetime EP0903471B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AT158697 1997-09-19
AT0158697A AT407282B (de) 1997-09-19 1997-09-19 Vorrichtung zur verstellung einer nockenwelle
AT1586/97 1997-09-19
AT135898 1998-08-06
AT135898 1998-08-06
AT1358/98 1998-08-06

Publications (2)

Publication Number Publication Date
EP0903471A1 EP0903471A1 (fr) 1999-03-24
EP0903471B1 true EP0903471B1 (fr) 2001-12-05

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Family Applications (1)

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EP98890262A Expired - Lifetime EP0903471B1 (fr) 1997-09-19 1998-09-10 Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne

Country Status (5)

Country Link
US (1) US6138622A (fr)
EP (1) EP0903471B1 (fr)
AT (1) ATE210243T1 (fr)
DE (1) DE59802310D1 (fr)
ES (1) ES2167864T3 (fr)

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EP3868591A1 (fr) 2009-03-30 2021-08-25 TQ-Systems GmbH Engrenage, unité moteur-engrenage, véhicule, générateur avec engrenage et élément de transmission de force
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EP3929469B1 (fr) 2013-03-20 2024-06-12 TQ-Systems GmbH Démultiplicateur harmonique à couronne de broches
JP2016044627A (ja) * 2014-08-25 2016-04-04 アイシン精機株式会社 弁開閉時期制御装置
JP6531641B2 (ja) * 2015-12-21 2019-06-19 アイシン精機株式会社 弁開閉時期制御装置
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Also Published As

Publication number Publication date
ES2167864T3 (es) 2002-05-16
ATE210243T1 (de) 2001-12-15
DE59802310D1 (de) 2002-01-17
EP0903471A1 (fr) 1999-03-24
US6138622A (en) 2000-10-31

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