EP1491728B1 - Nockenwellenversteller - Google Patents

Nockenwellenversteller Download PDF

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Publication number
EP1491728B1
EP1491728B1 EP04014612A EP04014612A EP1491728B1 EP 1491728 B1 EP1491728 B1 EP 1491728B1 EP 04014612 A EP04014612 A EP 04014612A EP 04014612 A EP04014612 A EP 04014612A EP 1491728 B1 EP1491728 B1 EP 1491728B1
Authority
EP
European Patent Office
Prior art keywords
receiving hole
rotor
housing member
lock
relative rotation
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 - Fee Related
Application number
EP04014612A
Other languages
English (en)
French (fr)
Other versions
EP1491728A3 (de
EP1491728A2 (de
Inventor
Masaki c/o I.P.D AISIN SEIKI KAB. KAISHA Kobayashi
Katsuhiko c/o I.P.D AISIN SEIKI KAB KAISHA Eguchi
Kazumi c/o I.P.D AISIN SEIKI KAB. KAISHA Ogawa
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.)
Aisin Corp
Original Assignee
Aisin Seiki Co 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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP1491728A2 publication Critical patent/EP1491728A2/de
Publication of EP1491728A3 publication Critical patent/EP1491728A3/de
Application granted granted Critical
Publication of EP1491728B1 publication Critical patent/EP1491728B1/de
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • This invention generally relates to a variable valve timing control device. More particularly, the present invention pertains to a variable valve timing control device for controlling an opening and closing timing of an intake valve and exhaust valve of an internal combustion engine.
  • US 2001/054405 A1 discloses a variable valve timing control device.
  • the head portion of the lock member is tapered with its diameter decreasing towards the bottom of the receiving hole.
  • the receiving hole is cylindrical with a constant diameter along its length.
  • the receiving hole is formed with an inner tapered surface, the diameter of which decreases towards the bottom surface of the receiving hole.
  • the lock member of both embodiments is formed with a step portion between its body portion, which is guided in an accommodating hole, and its head portion. The head portion contacts the receiving hole at its opening edge at a locus of points where the diameter of the receiving hole becomes identical to the diameter of the head portion.
  • variable valve timing control device 1 includes a torsion spring 60 disposed between the inner rotor 20 and the front plate 40, four vanes 70 assembled to the inner rotor 20, and a lock plate 80 (lock member) (see Fig. 2 ) assembled to the outer rotor 30.
  • the operation fluid (fluid pressure) is supplied to or discharged from the four advanced angle chambers R1, which are defined and divided by the vanes 70, via the advanced angle fluid passage 11 and the first fluid passage 23.
  • the operation fluid is supplied to or discharged from three retarded angle chambers R2 out of four via the retarded angle fluid passage 12 and the second fluid passage 24.
  • the operation fluid is supplied to the lock plate 80 from the lock fluid passage 25 formed on the bottom portion 22d of the receiving hole 22.
  • the operation fluid is supplied to or discharged from the remaining (i.e. one out of four) retarded angle chamber R2 via the fluid groove 24a connecting the lock fluid passage 25 and that retarded angle chamber R2. Accordingly, for one retarded angle chamber R2 out of four, the second fluid passage 24 is not provided and the lock fluid passage 25 is shared to be used, which may achieve a simple structure of the fluid pressure circuit.
  • Both side portions of the outer rotor 30 in the axial direction thereof are integrally fixed to the annular shaped front plate 40 and the rear plate 50 respectively via five connecting bolts 92.
  • the timing sprocket 31 is integrally formed on an outer periphery of the outer rotor 30 and on an end side in the axial direction thereof to which the rear plate 50 is connected.
  • five convex portions 33 are formed on the inner circumference of the outer rotor 30 in the circumferential direction thereof so as to project in the radially inward direction.
  • Each inner circumferential face of each convex portion 33 is slidably in contact with an outer circumferential face of the inner rotor 20. That is, the outer rotor 30 is rotatably supported on the inner rotor 20.
  • a head portion 80a of the lock plate 80 i.e. facing the bottom portion 22d of the receiving hole 22, has a trapezoidal shape in cross section formed by a convex taper portion extending in the radially inward direction of the outer rotor 30 and a top portion.
  • An inner peripheral face 22b is formed by a concave taper portion 22c having a trapezoidal shape in cross section and gradually expanding towards an opening portion 22a, and the bottom portion 22d.
  • An end portion 80b (contact portion) of the top portion of the lock plate 80 is in contact with the inner peripheral face 22b of the receiving hole 22 on the advanced angle side and the retarded angle side between the opening portion 22a and the bottom portion 22d of the receiving hole 22.
  • a contact width B in the circumferential direction of the contact portion 80b of the lock plate 80, with which the inner peripheral face 22b of the receiving hole 22 on the advanced angle side and the retarded angle side is in contact is larger than a bottom width D in the circumferential direction of the bottom portion 22d of the receiving hole 22.
  • the torsion spring 60 is provided by engaging with the front plate 40 at one end and the inner rotor 20 at the other end.
  • the torsion spring 60 biases the inner rotor 20 towards the advanced angle side (clockwise direction in Fig. 2 ) relative to the outer rotor 30, the front plate 40 and the rear plate 50.
  • the operation response of the inner rotor 20 to the advanced angle side may be improved.
  • the oil pump 205 when the internal combustion engine is stopped, the oil pump 205 is stopped and also the switching valve 200 is not energized. Thus, the operation fluid is not supplied to the fluid pressure chambers R0. At this time, the head portion 80a of the lock plate 80 is positioned within the receiving hole 22 of the inner rotor 20 and thus the relative rotation between the inner rotor 20 and the outer rotor 30 is restricted. Even when the internal combustion engine is started and the oil pump 205 is driven, the operation fluid supplied from the oil pump 205 is only virtually provided to the advanced angle chamber R1 via the connecting passage 16, the advanced angle fluid passage 11, and the first fluid passage 23 while the duty ratio is small for energizing the switching valve 200 (i.e. the ratio of energizing time relative to the de-energizing time per unit time is small). Therefore, the variable valve timing control device 1 is maintained in a locked state.
  • the duty ratio for energizing the switching valve 200 is brought to be large and then the position of the spool 204 is switched.
  • the operation fluid supplied from the oil pump 205 is provided to the retarded angle chamber R2 by passing through the connecting passage 15, the retarded angle fluid passage 12, and the second fluid passage 24, or by passing through the fluid groove 24a after supplied to the receiving hole 22 from the lock fluid passage 25.
  • the operation fluid stored in the advanced angle chamber R1 is sent to the first fluid passage 23, the advanced angle fluid passage 11, and the connecting passage 16 to be discharged from the discharge port 207 of the switching valve 200. Therefore, the lock plate 80 is moved against the biasing force of the spring 81, thereby moving the head portion 80a from the receiving hole 22. Then, the locked state between the inner rotor 20 and the outer rotor 30 is released. At the same time, the inner rotor 20 integrally rotating with the camshaft 10 and each vane 70 rotate relative to the outer rotor 30, the front plate 40, and the rear plate 50 in the retarded angle direction (counterclockwise direction in Fig. 2 ). Due to the aforementioned relative rotation, the timing of the cam is brought in the advanced angle state.
  • the relative rotation phase may be defined arbitrarily by controlling the duty ratio of the switching valve 200. For example, the relative rotation between the inner rotor 20 and the outer rotor 30 may be stopped at the intermediate phase.
  • the lock plate 80 and the receiving hole 22 are prevented from being strongly constrained each other under the condition that the fluctuation torque by the camshaft 10 is applied to the contact portion 80b and the inner peripheral face 22b in the advanced angle direction and the retarded angle direction alternately since the gap C is formed between the side face 33a of the convex portion 33A and the side face 70a of the vane 70A.
  • the lock plate 80 is moved from the receiving hole 22 by the operation fluid that is produced when the locked state of the relative rotation is released.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (4)

  1. Variable Ventilzeitsteuerungsvorrichtung (1) mit einem Gehäusebauteil (3), das integral mit einer von einer Kurbelwelle und einer Nockenwelle (10) eines Verbrennungsmotors dreht, einem Rotorbauteil (2), das so an das Gehäusebauteil montiert ist, dass es relativ dazu drehbar ist und auf einem konvexen Bereich (33), der an dem Gehäusebauteil ausgebildet ist, gleitbar ist, wobei das Rotorbauteil Flügelteile (70) enthält, von denen jeder eine Frühverstellwinkelkammer (R1) und eine Spätverstellwinkelkammer (R2) in dem Gehäusebauteil bildet, und integral mit der anderen von der Kurbelwelle und der Nockenwelle dreht, einem Anschlag (33a, 33b), der an dem konvexen Bereich ausgebildet ist und in Berührung mit zumindest einem der Flügelteile ist, eine relative Drehung zwischen dem Gehäusebauteil und dem Rotorbauteil zu einer Seite des Frühverstellwinkels oder einer Seite des Spätverstellwinkels zu definieren, einem Sperrmechanismus (22, 80) zum Einschränken der relativen Drehung zwischen dem Gehäusebauteil und dem Rotorbauteil durch ein Sperrbauteil (80), das an dem Gehäusebauteil angeordnet ist, um in ein an dem Rotorbauteil ausgebildetes Aufnahmeloch (22) eingebracht zu werden, wenn eine relative Drehphase zwischen dem Gehäusebauteil und dem Rotorbauteil an einer vorbestimmten Phase positioniert ist, und einem Fluiddruckkreislauf (23, 24, 25) zum Steuern eines Betriebsöls, das der Frühverstellwinkelkammer, der Spätverstellwinkelkammer und dem Sperrmechanismus zugeführt oder von diesen abgelassen werden kann, wobei das Sperrbauteil (80) einen Kopfbereich (80a) enthält, der dem Bodenbereich (22d) des Aufnahmelochs zugewandt ist, und die Innenumfangsfläche (22b) des Aufnahmelochs (22) einen konkaven Verjüngungsbereich (22c) enthält, der im Querschnitt eine Trapezform hat und sich zum Öffnungsbereich des Aufnahmelochs hin graduell erweitert, so dass, wenn die relative Drehung zwischen dem Gehäusebauteil und dem Rotorbauteil eingeschränkt wird, das Sperrbauteil mit dem Aufnahmeloch auf der Seite des Frühverstellwinkels und der Seite des Spätverstellwinkels des Aufnahmelochs in Berührung ist, dadurch gekennzeichnet, dass der Kopfbereich (80a) des Sperrbauteils (80) im Querschnitt eine rechteckige Form hat, so dass, wenn die relative Drehung zwischen dem Gehäusebauteil (3) und dem Rotorbauteil (2) eingeschränkt ist, das Sperrbauteil mit einer Innenumfangsfläche (22b) des Aufnahmelochs (22) zwischen einem Öffnungsbereich (22a) und einem Bodenbereich (22d) des Aufnahmelochs in Berührung ist.
  2. Variable Ventilzeitsteuerungsvorrichtung (1) nach Anspruch 1, wobei, wenn die relative Drehung zwischen dem Gehäusebauteil und dem Rotorbauteil eingeschränkt ist, eine Berührungsbreite (B) in einer Umfangsrichtung eines Berührungsbereichs (80b) des Sperrbauteils, mit dem eine Innenumfangsfläche (22b) des Aufnahmelochs auf der Seite des Frühverstellwinkels und der Seite des Spätverstellwinkels in Berührung ist, größer ist als eine Bodenbreite (D) in der Umfangsrichtung eines Bodenbereichs (22d) des Aufnahmelochs.
  3. Variable Ventilzeitsteuerungsvorrichtung nach Anspruch 2, wobei der Berührungsbereich (80b) abgeschrägt ist.
  4. Variable Ventilzeitsteuerungsvorrichtung nach einem der Ansprüche 1 bis 3, wobei, wenn die relative Drehung zwischen dem Gehäusebauteil (3) und dem Rotorbauteil (2) eingeschränkt ist, ein Spalt (C) zwischen dem Anschlag (33a, 33b) und dem Flügelteil (70) gebildet ist.
EP04014612A 2003-06-25 2004-06-22 Nockenwellenversteller Expired - Fee Related EP1491728B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003181475 2003-06-25
JP2003181475 2003-06-25

Publications (3)

Publication Number Publication Date
EP1491728A2 EP1491728A2 (de) 2004-12-29
EP1491728A3 EP1491728A3 (de) 2005-11-30
EP1491728B1 true EP1491728B1 (de) 2010-08-11

Family

ID=33411081

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04014612A Expired - Fee Related EP1491728B1 (de) 2003-06-25 2004-06-22 Nockenwellenversteller

Country Status (3)

Country Link
US (1) US20050022763A1 (de)
EP (1) EP1491728B1 (de)
DE (1) DE602004028552D1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2755884C (en) 2010-11-08 2013-12-17 Toyota Jidosha Kabushiki Kaisha Control device for hydraulic variable valve timing mechanism
JP5288061B2 (ja) 2011-04-07 2013-09-11 トヨタ自動車株式会社 バルブタイミング可変装置
JP6063267B2 (ja) * 2013-01-18 2017-01-18 株式会社ミクニ バルブタイミング変更装置及びその組付け方法
DE102014214610B4 (de) * 2014-07-25 2017-05-18 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung für eine Brennkraftmaschine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000230511A (ja) * 1998-12-07 2000-08-22 Mitsubishi Electric Corp ベーン式油圧アクチュエータ
JP3983457B2 (ja) * 2000-06-22 2007-09-26 株式会社日立製作所 内燃機関のバルブタイミング変更装置

Also Published As

Publication number Publication date
US20050022763A1 (en) 2005-02-03
EP1491728A3 (de) 2005-11-30
DE602004028552D1 (de) 2010-09-23
EP1491728A2 (de) 2004-12-29

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