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WO2016019955A1 - Déphaseur d'arbre à cames muni d'une unité de réglage commandée par pression court-circuitant les chambres - Google Patents

Déphaseur d'arbre à cames muni d'une unité de réglage commandée par pression court-circuitant les chambres Download PDF

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Publication number
WO2016019955A1
WO2016019955A1 PCT/DE2015/200356 DE2015200356W WO2016019955A1 WO 2016019955 A1 WO2016019955 A1 WO 2016019955A1 DE 2015200356 W DE2015200356 W DE 2015200356W WO 2016019955 A1 WO2016019955 A1 WO 2016019955A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
chamber
camshaft adjuster
bypass line
hydraulic fluid
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.)
Ceased
Application number
PCT/DE2015/200356
Other languages
German (de)
English (en)
Inventor
Torsten Zschieschang
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201580041880.XA priority Critical patent/CN106574525B/zh
Priority to US15/328,607 priority patent/US10385739B2/en
Publication of WO2016019955A1 publication Critical patent/WO2016019955A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • 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

  • the invention relates to a camshaft adjuster of the vane type, with a rotor having radially projecting wings, wherein the rotor, together with a rotor rotatably receiving the stator, vane formed, each of which is divided by a wing in two adjustable, prepared for hydraulic fluid chambers.
  • camshaft adjusters are used in valve trains of internal combustion engines, as they are known, for example, from DE 102 39 748 A1. From the prior art, such as the US 2008/0173267 A1 or US 7,182,052 B2 or DE 10 2008 000 083 A1 and camshaft adjuster are known as valve timing devices.
  • a valve timing controller controls a valve timing of an intake / exhaust valve of an internal combustion engine.
  • the device has a housing which is rotated by a drive shaft.
  • the housing has a chamber space receiving a paddle rotatable with a driven shaft to a delay and a Voreilseite relative to the housing by being acted upon by a hydraulic pressure in a delay and Voreilhunt in the chamber space.
  • a filter is provided for removing contaminants in a fluid passage extending from a sliding portion between the driven shaft and a bearing to both the housing and the paddle rotor through a connected portion between the driven shaft and the paddle rotor.
  • the filter is provided on the side of both the housing and the blade rotor with respect to the sliding portion.
  • Camshaft adjusters are also known from documents US Pat. No. 7,245,077 B2, US Pat. No. 7,318,401 B2 and US Pat. No. 7,000,580 B1.
  • the invention is in the field with pressure accumulators and additional control functions in the switching valve.
  • Hydraulikfluidreguliervorides arranged for hydraulic fluid conduction between the chambers and / or interconnected / connected, that a pressure drop, preferably below a predetermined limit pressure in the chambers, which is caused or amplified by operating camshaft alternating torques, is inserted for fluid-permeable opening of the hydraulic fluid control device.
  • Critical pressure in certain situations equivalent to a limit pressure, can be understood as the pressure at which the system begins to suck air or oil begins to degas.
  • a limiting pressure is understood to be the pressure which is the pressure set via the spring preload and piston effective area.
  • the hydraulic fluid control device has at least one bypass line closure device or preferably two bypass line closure devices. In this way, both hydraulic fluid from the one Kamner in the other Kannnner be spent in pressure drop, but also from the other Kannnner in a Kannnner. An optimization in both adjustment of the camshaft adjuster is then reached. If the two bypass line closing devices are arranged in parallel to one another in a fluid-conducting manner, the reaction times can be kept low.
  • the bypass line closure device includes a valve, such as a 2/2-way valve, and a spring acting thereon, such as a compression or tension spring. It can then be arranged on / in the camshaft adjuster two open / close valves, which are actuated when the pressure in the first chamber decreases. The actuated valve then opens a channel to allow oil flow from the other chamber to the first chamber.
  • a valve such as a 2/2-way valve
  • a spring acting thereon such as a compression or tension spring
  • a hydraulic fluid control unit which connects chambers A and B, ie a first chamber and a second chamber, only when the pressure set by a regulator / switch (p kr it) is fallen below in a chamber. Then a pressure equalization between the chambers can take place.
  • the already caused by the (camshaft) alternating moments pressure gradient between the chambers is utilized.
  • each path A or B with the respectively connected chambers each requires a separate control unit, which changes the pressure in the corresponding path or opens the bypass to the other chamber when the critical pressure in one of the chambers is undershot.
  • the differential pressure between the chambers does not matter.
  • a bypass / a bypass line is opened when the pressure is lower than the control unit set level decreases (limit pressure). Then it comes to overflow through this bypass line.
  • the pressure level is not “compensated”, but the camshaft adjuster now takes the oil additionally available to it (ie the oil "what he can get”) and thus becomes faster in its adjustment movement.
  • bypass line closing device is preset so that when a limit pressure (p kr it) is fallen below in a first of the chambers, a switching position of the bypass line closing device is forced, in / by the hydraulic fluid through a bypass line of the other, second chamber enters the one, first chamber.
  • the spring is adjusted to the limit pressure / pressure set by the regulator (pcrit). With the help of the spring, the area ratios and / or the effective areas on the piston exactly this limit pressure is set.
  • Hydraulikfluidleitvornchtung is integrated or installed in a wing. In this way, a very compact camshaft adjuster can be achieved.
  • bypass line closure device has a pilot line which produces a pressure-transmitting connection between the first chamber and a closure element, wherein the spring in its basic position, the closure element hydraulicfluidhneunterbindend in those connecting the two chambers bypass line urges and in an activation position, when reaching and / or falling below the limit pressure in the first chamber, opens the bypass line.
  • An advantageous embodiment is also characterized in that two mutually movable toward and away from each other piston are arranged in a channel, wherein the pistons are arranged so that they are driven only by the associated pilot line.
  • the two pistons are therefore hydraulically separated from each other controllable. So it should be a pressure-tight separation in the channel, the be designed in the manner of a bore, be held.
  • an embodiment in a wing as a male element with two separate chambers and piston / cups can be used.
  • the male member may be provided with two sections with holes in a sleeve.
  • the spring-loaded pistons or cups seal the holes in a basic position, whereby the pressure in both chambers is above the critical pressure. If, in one of the two chambers, the pressure falls below the critical pressure, the piston located on this chamber side moves, whereby the piston releases a bore and an overflow from the other chamber into that chamber takes place with the lower pressure via the bypass line ,
  • Such a camshaft adjuster can also be further developed by virtue of the fact that the shift range is that region of the common pilot line which ensures a hydraulic fluid-permeable connection between the two bypass lines in the case of pressure-dependent / pressure-drop-dependent displacement of one of the pistons.
  • Fig. 1 is a circuit diagram for a first embodiment of an inventive
  • Camshaft adjuster wherein a first chamber A is supplied via a pump with hydraulic fluid, the pressure in the first chamber A is above the critical pressure, the torsional moments are not critical, the system functions as an OPA system, and a short-circuited AB to a main valve / 1, in the situation in which the pressure in the first chamber A drops below the critical pressure p kr it, ie there is a suction phase, the torsional moments dominating the behavior of the camshaft adjuster, driving it Furthermore, the pressure supply from the pump is no longer sufficient, with a Hydraulikfluidregelvorrich- / pressure regulating unit releases a short circuit via a bypass line from the second chamber B to the first chamber A, so long as the system pressure-equalizing from the second chamber to the first chamber and hydraulikfluidnacheredd ensures that the pressure again on the crit 1, wherein the second chamber B is supplied with hydraulic fluid by the pump, but the pressure in the chamber B is above the critical pressure, the Torsionsmomente
  • FIG. 4 shows the situation in the adjustment direction, as in Fig. 3, but the pressure in the second chamber B drops below the critical pressure (suction phase), the torsional moments drivingly dominate the behavior of the camshaft adjuster, the pressure regulator / hydraulic fluid control device releasing the short circuit / bypass line from chamber A to chamber B, the system being so long from the chamber A to the chamber B pressure-compensating and hydraulikfluidnachided acts until the pressure in the chamber B is again above the critical pressure,
  • FIG. 5 shows a further embodiment in which two valves are integrated in a rotor blade and spring-loaded cups / pistons are used
  • FIG. 6 shows the embodiment of FIG. 5 but with bypass line opener
  • Fig. 7 shows a further embodiment for positioning the valves in the wing, wherein the pilot hole can also be centered to the piston or cup axis, so that the bypass line must not be discontinued, but can also be drilled in one go, if the piston or the cup in a blocking position sufficiently shuts off the opposite chamber and, in an open position, releases sufficient passage for the flow,
  • FIG. 8 shows a further embodiment in a bypass-line-locked position
  • FIG. 9 shows the embodiment of FIG. 8 in the bypass-line-opened position.
  • FIG. 1 shows a first embodiment of a camshaft adjuster 1 according to the invention.
  • This camshaft adjuster 1 is provided for use in a valve train on an internal combustion engine.
  • I has a rotor 2, the radially projecting wing 3 has. Usually, three or more wings 3 are used. Particularly preferred are four wings 3.
  • the rotor 2 is rotatably arranged in a stator 4, which can be connected, for example. Via a gear with a continuous traction means such as a chain.
  • the rotor 2 and the stator 4 form vane 5, which are each divided by a wing 3 in a first chamber 6 and a second chamber 7.
  • the first chamber may also be referred to as chamber A and the second chamber as chamber B or vice versa.
  • a main shut-off / change-over valve 9 is provided in a line system 8.
  • This Hauptabsperr- / Umschaltventil 9 is between a pump (P) 10 and a tank (T)
  • the hydraulic fluid control device 12 preferably has two bypass line closing devices 13. Both bypass
  • Line closing devices 13 have a valve 14, such as a 2/2 way valve 15.
  • This valve 14, which can also be referred to as a slide / slide valve, is biased by a spring 16.
  • the bypass line closing devices 13 are arranged in each case in a bypass line 17 or arranged in a common bypass line 17.
  • the bypass line 17 is opened by the right-hand valve 14 in the figure as long as the pressure P in the first chamber 6 drops below the critical pressure p kr it.
  • the adjustment direction of the rotor 2 relative to the stator 4 is symbolized by the arrow 19.
  • FIGS. 5 and 6 A variant of the embodiments shown in FIGS. 1 to 4, however, is shown in FIGS. 5 and 6.
  • a first bypass line 17, and a second bypass line 17 is closed, whereas due to the pressure transmission from the first chamber 6 because of a biased by the spring 16 closure element 20, a bypass line 17 is open, so that hydraulic fluid can pass from the second chamber 7 into the first chamber 6.
  • Each bypass line closure device 13 has a pilot line 18 to the respectively associated first or second chamber 6 or 7, which allows in coordination with the acting spring 16 opening and closing of the respective associated bypass / bypass line 17.
  • the pilot line 18 may also be referred to as a pilot channel.
  • the arrangement is chosen so that the first and second chambers are hydraulically separated from each other in a basic valve position, that is, when the pilot pressure is above the critical pressure. Neither the (over) pressure in the first chamber 6, nor the pressure in the second chamber 7 can bring the closure element 12, in the manner of a piston or a cup, for opening, nor a pressure gradient between the two chambers 6 and 7.
  • a suitable undercut in the sense of a depression for the frontal reception of the closure element 20, can assist the secure closing of the closure element / the valve body / the cup / the piston.
  • the pressure is above the critical pressure.
  • the valves are in their normal position, whereby the bypass / the bypass line 17 is closed.
  • the pressure in the first chamber 6 has fallen below the critical pressure.
  • the volume flow supply by the pump 10 is then no longer guaranteed sufficient.
  • the first chamber 6 so the first chamber 6, a pressure that drops below the critical pressure.
  • closure element 20 is then pulled out of its seat or undercut by the "negative pressure" in the first chamber 6 against the illustrated spring 16.
  • the short circuit from the second chamber 7 into the first chamber 6 is thus opened is also hydraulically assisted by acting on the now released end face of the closure element 20 chamber pressure in the second chamber. 7
  • valve / closure element 20 falls back into the seat and closes the bypass / the bypass line 17.
  • a slight undercut for receiving the closure element 20 ensures a secure seal against a laterally acting pressure from the chambers 6 and 7.
  • the system works as long as a traditional phaser in pure OPA mode until the pressure in a chamber 6 or 7 as a result of the applied alternating moments and the way of the spring 16, and an effective area of the closing element inside or piston area set critical pressure P cr it decreases.
  • the system is operated with oil pressure control and is not dependent on the "pumping" between the chambers, which has an advantageous effect on the adjustment speed or the adjustment behavior with small torsional torques
  • the adjustment is additionally supported by the pumping between the chambers , in the sense of a CTA adjustment, ie a "cam torque actuation".
  • the pressure drop between the chambers 6 and 7 additionally helps in achieving higher adjustment speeds.
  • the potential for Sucking air or outgassing from the oil is minimized. Of course, this also depends on the set pilot pressure.
  • FIG. 7 shows a further embodiment in which there are (orthogonally) pilot lines 18 originating from the two chambers 6 and 7 and acting on adjusting devices 19 / closing elements 20, which are in operative connection with springs 16.
  • the closure elements 20 close oblique bypass lines 17.
  • Two independently movable closure elements 20 in a bore orthogonal to the surface of the wing 3, the two chambers 6 and 7 together, are shown in Figs. 8 and 9. Falls below the limit pressure in the second chamber 7, for example, the closer the second chamber 7 closing element 20, so the corresponding piston to the second chamber 7 sucked / displaced.
  • a passage for oil from one section of the bypass line 17 to the other section of the bypass line 17 is enabled, so that according to the arrow direction shown in Fig. 9 in the bypass line 17 hydraulic fluid from the first chamber 6 in the second chamber 7 spent.

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 déphaseur d'arbre à cames (1) de type à palettes, comportant un rotor (2) qui présente des palettes (3) en saillie radialement, le rotor (2) formant avec un stator (4) dans lequel le rotor (2) est logé rotatif des cellules de palette (5) qui sont divisées respectivement par une palette (3) en deux chambres préparées pour recevoir un fluide hydraulique. Un dispositif de régulation (12) du fluide hydraulique dirigeant le fluide hydraulique entre les chambres (6, 7) est agencé et/ou raccordé de telle manière qu'une baisse de pression dans les chambres (6, 7) provoquée ou amplifiée par les couples alternés de l'arbre à cames produits en cours de fonctionnement est utilisée pour ouvrir le dispositif de régulation (12) du fluide hydraulique pour le passage du fluide.
PCT/DE2015/200356 2014-08-05 2015-06-11 Déphaseur d'arbre à cames muni d'une unité de réglage commandée par pression court-circuitant les chambres Ceased WO2016019955A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580041880.XA CN106574525B (zh) 2014-08-05 2015-06-11 具有将腔短接的压力控制的执行单元的凸轮轴调节器
US15/328,607 US10385739B2 (en) 2014-08-05 2015-06-11 Camshaft adjuster having a chamber short-circuiting, pressure-controlled control unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014215419.7 2014-08-05
DE102014215419.7A DE102014215419A1 (de) 2014-08-05 2014-08-05 Nockenwellenversteller mit kammernkurzschließender druckgesteuerter Stelleinheit

Publications (1)

Publication Number Publication Date
WO2016019955A1 true WO2016019955A1 (fr) 2016-02-11

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2015/200356 Ceased WO2016019955A1 (fr) 2014-08-05 2015-06-11 Déphaseur d'arbre à cames muni d'une unité de réglage commandée par pression court-circuitant les chambres

Country Status (4)

Country Link
US (1) US10385739B2 (fr)
CN (1) CN106574525B (fr)
DE (1) DE102014215419A1 (fr)
WO (1) WO2016019955A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016225001A1 (de) * 2016-12-14 2018-06-14 Volkswagen Aktiengesellschaft Tankentlüftungsanlage für ein Kraftfahrzeug sowie Kraftfahrzeug und Verfahren zum Betreiben einer Tankentlüftungsanlage
DE102018119829A1 (de) 2018-08-15 2020-02-20 Volkswagen Aktiengesellschaft Tankentlüftungsvorrichtung für einen Kraftstofftank sowie Fahrzeug
DE102021130428B3 (de) 2021-11-22 2023-03-23 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Steuerpin

Citations (11)

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Publication number Priority date Publication date Assignee Title
EP0518529A1 (fr) * 1991-06-11 1992-12-16 Borg-Warner Automotive Transmission And Engine Components Corporation Dispositif de calage variable pour arbre à cames entraîné par courroie
JPH1113430A (ja) * 1997-06-24 1999-01-19 Toyota Motor Corp 内燃機関のバルブタイミング制御装置
WO2003067034A1 (fr) * 2002-02-09 2003-08-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Dispositif permettant de regler l'angle de rotation d'un arbre a cames d'un moteur a combustion interne par rapport a une roue motrice
DE10239748A1 (de) 2002-08-29 2004-03-11 Ina-Schaeffler Kg Nehmereinheit eines strömungsmittelbetätigten variablen Ventiltriebs einer Brennkraftmaschine
US7000580B1 (en) 2004-09-28 2006-02-21 Borgwarner Inc. Control valves with integrated check valves
US7182052B2 (en) 2004-06-28 2007-02-27 Denso Corporation Valve timing controller
US20070107684A1 (en) * 2005-11-15 2007-05-17 Denso Corporation Valve timing adjusting apparatus
US7245077B2 (en) 2002-11-25 2007-07-17 Technology Trade And Transfer Corporation Structure of AC type PDP
DE102007000249A1 (de) * 2006-04-28 2007-10-31 Denso Corp., Kariya Ventilzeitsteuerung
US7318401B2 (en) 2006-03-15 2008-01-15 Borgwarner Inc. Variable chamber volume phaser
US20080173267A1 (en) 2007-01-18 2008-07-24 Denso Corporation Valve timing control apparatus

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JP4159241B2 (ja) * 2000-11-30 2008-10-01 株式会社デンソー 内燃機関用バルブタイミング調整装置
WO2006127348A1 (fr) * 2005-05-23 2006-11-30 Borgwarner Inc Clapet pour la reduction du volume d'une chambre de lubrification
JP2008144589A (ja) * 2006-12-06 2008-06-26 Denso Corp 内燃機関の制御装置
DE102008037997B4 (de) * 2008-08-16 2019-08-22 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102011007883A1 (de) * 2011-04-21 2012-10-25 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0518529A1 (fr) * 1991-06-11 1992-12-16 Borg-Warner Automotive Transmission And Engine Components Corporation Dispositif de calage variable pour arbre à cames entraîné par courroie
JPH1113430A (ja) * 1997-06-24 1999-01-19 Toyota Motor Corp 内燃機関のバルブタイミング制御装置
WO2003067034A1 (fr) * 2002-02-09 2003-08-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Dispositif permettant de regler l'angle de rotation d'un arbre a cames d'un moteur a combustion interne par rapport a une roue motrice
DE10239748A1 (de) 2002-08-29 2004-03-11 Ina-Schaeffler Kg Nehmereinheit eines strömungsmittelbetätigten variablen Ventiltriebs einer Brennkraftmaschine
US7245077B2 (en) 2002-11-25 2007-07-17 Technology Trade And Transfer Corporation Structure of AC type PDP
US7182052B2 (en) 2004-06-28 2007-02-27 Denso Corporation Valve timing controller
US7000580B1 (en) 2004-09-28 2006-02-21 Borgwarner Inc. Control valves with integrated check valves
US20070107684A1 (en) * 2005-11-15 2007-05-17 Denso Corporation Valve timing adjusting apparatus
US7318401B2 (en) 2006-03-15 2008-01-15 Borgwarner Inc. Variable chamber volume phaser
DE102007000249A1 (de) * 2006-04-28 2007-10-31 Denso Corp., Kariya Ventilzeitsteuerung
US20080173267A1 (en) 2007-01-18 2008-07-24 Denso Corporation Valve timing control apparatus
DE102008000083A1 (de) 2007-01-18 2008-07-31 Denso Corp., Kariya Ventilzeitsteuergerät

Also Published As

Publication number Publication date
CN106574525A (zh) 2017-04-19
US20170211430A1 (en) 2017-07-27
DE102014215419A1 (de) 2016-02-11
US10385739B2 (en) 2019-08-20
CN106574525B (zh) 2020-07-28

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