EP2375014A1 - Dispositif de réglage d'un arbre à cames avec une soupape hydraulique - Google Patents

Dispositif de réglage d'un arbre à cames avec une soupape hydraulique Download PDF

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Publication number
EP2375014A1
EP2375014A1 EP11157216A EP11157216A EP2375014A1 EP 2375014 A1 EP2375014 A1 EP 2375014A1 EP 11157216 A EP11157216 A EP 11157216A EP 11157216 A EP11157216 A EP 11157216A EP 2375014 A1 EP2375014 A1 EP 2375014A1
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EP
European Patent Office
Prior art keywords
hydraulic valve
port
opening
switching position
hydraulic
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
EP11157216A
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German (de)
English (en)
Other versions
EP2375014B1 (fr
Inventor
Andreas Knecht
Dirk Pohl
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP2375014A1 publication Critical patent/EP2375014A1/fr
Application granted granted Critical
Publication of EP2375014B1 publication Critical patent/EP2375014B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve according to the preamble of claim 1.
  • the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already relate to a Schwenkmotornockenwellenversteller with a hydraulic valve, which has two working ports. These two working ports each have axially adjacent to each other a standard opening and an opening for utilizing pressure peaks due to camshaft alternating torques.
  • a hydraulic pressure can be conducted from a supply connection to the work connection to be loaded, while the work connection to be relieved is guided to a tank connection.
  • the hydraulic valve is designed as a 4/3-way valve in cartridge design.
  • In the sleeve check valves are used on the inside, which are designed as band-shaped rings. By means of these check valves camshaft alternating torques are used to adjust the camshaft adjuster particularly fast or with a relatively low oil pressure can.
  • the check valves cover the openings for the use of pressure peaks due to camshaft alternating torques.
  • the object of the invention is to provide a simple to be controlled with little effort Schwenkmotornockenwellenversteller.
  • the camshaft alternating torques for fast phasing of the camshaft can be used in the invention Schwenkmotornockenwellenversteller. Moreover, due to the use of camshaft alternating torques, it is advantageously possible to enable adjustment with a relatively low oil pressure. A thus possible small dimensions of the oil pump improves the efficiency of the internal combustion engine. The saved volume flow of hydraulic fluid is different Consumers, such as a hydraulic valve lift adjustment available.
  • Pivot camshaft phasors have also recently been applied to the combustion engines with fewer cylinders to reduce fuel consumption, increase performance, and reduce exhaust emissions.
  • the smaller the number of cylinders the greater the fluctuations of the Nockwellen dockmomente.
  • the hydraulic valve is proportional to a first switching position adjustable in which the effect of check valves for the use of camshaft alternating torques is bypassed. Due to the proportional controllability of the control process between use of the camshaft alternating torques and circumvention of this use is continuously controlled.
  • the hydraulic valve is additionally adjustable in favor of a higher control quality in a switching position to bypass the use of camshaft alternating torque.
  • Fig. 1 shows in a circuit diagram a by means of an electromagnet 17 against a spring force of a spring 21 operable hydraulic valve 3, which is controlled proportionally.
  • a Schwenkmotornockenwellenversteller 4 is pivotable.
  • the angular position between the crankshaft and the camshaft is changed during operation of an internal combustion engine.
  • the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine brings its optimal performance at the respective speed.
  • the Schwenkmotornockenwellenversteller 4 allows a continuous adjustment of the camshaft relative to the crankshaft.
  • a first consumer port A and a second consumer port B go to the Schwenkmotornockenwellenversteller 4 from.
  • the hydraulic valve 3 has four ports and five shift positions and can thus also be referred to as a 4/5-way valve with a locking middle position 7.
  • the hydraulic valve 3 is in one of the two switching positions 16, 19, which are represented by the two switch box behind the locking center position 7.
  • the hydraulic valve is in the switch position 19 of the switch box at the very rear.
  • pressure chambers 6 associated with this direction of rotation 1 are acted upon by the first consumer port A, which pressure comes from a supply port P.
  • the pressure chambers 5 assigned to the second, ie opposite, direction of rotation 2 are relieved to the second consumer connection B.
  • the second consumer port B is guided to a tank 20 via a tank connection T.
  • the adjustment of the camshaft takes place with use of the camshaft alternating torques.
  • an outermost switching position 18 similar to the immediately adjacent switching position 15 is executed.
  • a volume flow from the hydraulic fluid coming from a check valve RSV-A assigned to the first supply connection A is made available to the supply connection P.
  • the other outermost switching position 19 is similar to the immediately adjacent switching position 16 executed.
  • a volume flow of hydraulic fluid coming from a check valve RSV-B assigned to the second supply connection B is made available to the supply connection P.
  • This additional volume flow from the load connection A or B to be relieved is fed into the volume flow coming from an oil pump 12 at the supply connection P.
  • the supply port P leads via a pump check valve RSV-P to the oil pump 12, which applies the pressure for adjusting the Schwenkmotornockenwellenverstellers 4.
  • This pump check valve RSV-P blocks the pressures in the hydraulic valve 3 so that peak pressures coming from the load connection A or B to be relieved can be made available to a larger proportion of the adjustment assistance than is the case with an open oil pump line 14a, 14b would.
  • Fig. 2 to Fig. 6 show a constructive embodiment of the hydraulic valve 3 in the five switching positions 18, 15, 7, 16, 19 according to Fig. 1 ,
  • Fig. 2 shows the hydraulic valve 3 in the first switching position 18, in which the electromagnet 17 according to Fig. 1 a hollow piston 22 of the hydraulic valve 3 does not move.
  • the stroke of the piston 22 is thus at zero.
  • the piston 22 is displaceable within a bushing 27 against the force of the spring designed as a helical compression spring 21.
  • the electromagnet 17 facing the front end is closed to produce a contact surface for an actuating plunger of the electromagnet 17, whereas the other end face for the realization of the tank port T is open.
  • the piston 22 has at its two ends outer webs 23, 24, which are guided relative to the bushing 27.
  • the two outer webs 23, 24 are pierced by transverse bores 29, 30, so that from these transverse bores 29, 30 via the interior of the hollow piston 22 access to the tank port T is present.
  • two narrow ribs 31, 32 are provided, which rotate around the piston 22.
  • These circumferential ribs 31, 32 correspond to two annular webs 33, 34 extending radially inwardly from the bush 27.
  • two axially outer annular webs 35, 36 are provided.
  • These four ring lands 33 to 26 are formed, since five inner ring grooves 37 to 41 are turned out of the socket. In this five réelleringnuten 37 to 41 five connection holes, which are drilled through the wall of the socket 27 open.
  • the axially inner openings A2, B2 for provided a camshaft alternating torque use.
  • the axially inner openings A2, B2 have the band-shaped check valves RSV-A, RSB-B.
  • one of the band-shaped check valves RSV-A and RSB-B is inserted into an inner annular groove 25 and 26 radially inside the axially inner openings A2 and B2 of the bush 27.
  • band-shaped pump check valve RSV-P is still provided in an inner annular groove 28.
  • This pump check valve RSV-P has basically the same structure as the two check valves RSV-A, RSV-B. However, this pump check valve RSV-P may have a different response force.
  • the other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the the second working port B associated standard opening B1.
  • short-term peak pressures due to the camshaft alternating torques from the first working port A associated opening A2 through its check valve RSV-A.
  • the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
  • the hydraulic valve 3 is in the switching position 15.
  • the rear rib 32 covers the corresponding annular land 34 so far that a flow through the very narrow gap is possible only with increased flow resistance.
  • the very slightly biased check valve RSV-A has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the first working port A to the second working port B.
  • the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
  • the hydraulic valve 3 is in the locking center position 7.
  • the supply port P is closed by the two ribs 31, 32.
  • the ribs 31, 31 cover the corresponding annular webs 33, 34 in a correspondingly large extent.
  • the two working connections A, B are blocked against the tank drain T.
  • both transverse bores 29, 30 are located axially outside the axially outer inner annular grooves 37, 41.
  • the hydraulic valve 3 is in the switching position 16.
  • coming from the supply port P hydraulic fluid through the gap between the rear rib 32 and the corresponding ring land 34 to the standard opening A1 of the first working port A pass.
  • the front rib 31 covers the corresponding annular web 33 so far that a flow through the very narrow Gap is only possible with increased flow resistance.
  • the very slightly biased check valve RSV-B has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the second working port B to the first working port A.
  • the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
  • the two middle ribs 31, 32 axially spaced from the two annular ridges 33, 34, so that hydraulic fluid can pass through the gaps between them.
  • hydraulic fluid can pass through the gap between the rearmost outer web 24 and the corresponding annular web 36.
  • the other outer web 23 blocks the foremost inner annular groove 37 and the standard opening B1 of the second working port B for this purpose.
  • the outer web 23 and the foremost annular web 35 overlap over a large sealing length. In this way, in this switching position 19 hydraulic fluid can reach from the supply connection P via the pump check valve RSV-P to the standard opening A1 of the first working connection A.
  • the other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the standard opening B1 of the second working port B.
  • short-term peak pressures due to the camshaft alternating torques from the opening B2 of the second working port B by the Check valve RSV-B let through.
  • the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
  • the standard opening A1 or B1 and the opening A2 or B2 are summarized for use of camshaft alternating moments only outside the bushing 27 to the working port A and B respectively.
  • an annular groove can be incorporated radially outside into the socket.
  • ball check valves may be used instead of band check valves.
  • the ball check valves need not necessarily be installed in the socket of a cartridge valve. It is also possible, for example, to use the ball check valves in a rotor and run the piston as a central valve which is arranged coaxially and centrally within the rotor hub slidably.
  • screens may also be provided in the direction of flow in front of one or more or even all ports, which protect the running surfaces between the piston and the bushing.
  • the hydraulic valve can also find application in a so-called central valve.
  • the socket is not directly connected to the magnetic part. Instead, the hydraulic valve is centrally located in the rotor of the Schwenkmotornockenwellenverstellers so that the sleeve rotates together with the piston.
  • the magnet is rotationally fixed relative to the cylinder head arranged, so that a relative movement between the plunger of the magnetic member and the piston takes place.
  • camshaft alternating torques does not have to be provided for both directions of rotation. It is also possible to dispense with one of the two axially outermost switching position 18 or 19. As a result, the camshaft alternating torques can then be used directly for faster adjustment only for the one direction of rotation.
  • a use of the camshaft alternating torques can be provided for both directions, but then to one of the two check valves RSV-A, RSV-B bypassing switch positions 15, 16 is omitted.
  • a further switching position in which both working ports A, B are relieved against the tank port T, so that a so-called center locking is made possible.
  • a locking bolt is provided in the Schwenkmotornockenwellenversteller, which fixes the rotor in an angular position against the stator, which is not an end position.
  • Such a central locking is for example in the DE 10 2004 039 800 B4 and the not pre-published DE 10 2009 022 869.1-13 shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP11157216.0A 2010-04-10 2011-03-07 Dispositif de réglage d'un arbre à cames avec une soupape hydraulique Active EP2375014B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010014500 2010-04-10
DE102010045358A DE102010045358A1 (de) 2010-04-10 2010-09-14 Schwenkmotornockenwellenversteller mit einem Hydraulikventil

Publications (2)

Publication Number Publication Date
EP2375014A1 true EP2375014A1 (fr) 2011-10-12
EP2375014B1 EP2375014B1 (fr) 2013-07-10

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Application Number Title Priority Date Filing Date
EP11157216.0A Active EP2375014B1 (fr) 2010-04-10 2011-03-07 Dispositif de réglage d'un arbre à cames avec une soupape hydraulique

Country Status (5)

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US (1) US8662040B2 (fr)
EP (1) EP2375014B1 (fr)
JP (1) JP6025134B2 (fr)
CN (1) CN102213120B (fr)
DE (1) DE102010045358A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010061337A1 (de) 2010-12-20 2012-06-21 Hydraulik-Ring Gmbh Hydraulikventil für einen Schwenkmotorversteller
CN104110286A (zh) * 2013-04-22 2014-10-22 德国海利特有限公司 用于可逆式电动机调节器的中心阀
DE102013104051A1 (de) 2013-04-22 2014-10-23 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
DE102013104031A1 (de) 2013-04-22 2014-10-23 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
US9322331B2 (en) 2013-07-05 2016-04-26 Hilite Germany Gmbh Connecting rod for two stage variable compression
EP2905434B1 (fr) * 2014-02-06 2017-09-27 Hilite Germany GmbH Déphaseur oscillant doté d'une soupape hydraulique pour arbreà cames
EP3399168A1 (fr) * 2017-05-04 2018-11-07 ECO Holding 1 GmbH Module hydraulique pourvu d'une soupape d'inversion permettant de commander un flux de fluide hydraulique d'un bielle pour un moteur à combustion interne à compression variable ainsi que bielle
DE102019101159A1 (de) 2018-02-21 2019-08-22 ECO Holding 1 GmbH Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
EP3530891A1 (fr) 2018-02-21 2019-08-28 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
EP3530892A1 (fr) 2018-02-21 2019-08-28 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
US10502128B2 (en) 2017-05-04 2019-12-10 ECO Holding 1 GmbH Hydraulic module with switch valve for controlling a hydraulic fluid flow of a connecting rod for an internal combustion engine with variable compression and connecting rod
CN112302752A (zh) * 2019-07-25 2021-02-02 句容嘉晟汽车配件有限公司 一种vvt系统

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DE102009050779B4 (de) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren
DE102009054055A1 (de) * 2009-11-20 2011-05-26 Schaeffler Technologies Gmbh & Co. Kg Schaltbare Vorrichtung zur Druckversorgung
CN103168152B (zh) 2010-11-02 2015-10-21 博格华纳公司 凸轮扭矩致动-扭转辅助相位器
JP5447543B2 (ja) * 2012-01-26 2014-03-19 株式会社デンソー バルブタイミング調整装置、およびその組付方法
DE102012201566B4 (de) * 2012-02-02 2017-05-18 Schaeffler Technologies AG & Co. KG Anordnung eines Volumenspeichers im Nockenwellenversteller
US10156164B2 (en) 2012-02-02 2018-12-18 Schaeffler Technologies AG & Co. KG Arrangement of a volume accumulator in a camshaft adjuster
CN102705029B (zh) * 2012-05-30 2014-12-10 绵阳富临精工机械股份有限公司 一种凸轮相位器
US20160097605A1 (en) * 2014-10-07 2016-04-07 Spx Corporation Hydraulic Closure Unit and Retrofit System for a Plate Heat Exchanger
DE102016210177B4 (de) 2015-07-08 2022-03-31 Ford Global Technologies, Llc Variable Nockenwellensteuervorrichtung
DE102016107986A1 (de) * 2015-11-04 2017-05-04 Hilite Germany Gmbh Hydraulikventil und Pleuel mit einem Hydraulikventil
DE102016118962A1 (de) * 2016-10-06 2018-04-12 Denso Corporation Nockenwellensteller und zugehöriger Schaltkörper
JP6690633B2 (ja) 2017-01-19 2020-04-28 株式会社デンソー バルブタイミング調整装置およびチェック弁
WO2018135584A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution et clapet de non-retour
US10113451B2 (en) 2017-03-28 2018-10-30 ECO Holding 1 GmbH Hydraulic valve for a cam phaser
DE102017106938A1 (de) 2017-03-31 2018-10-04 ECO Holding 1 GmbH Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
JP6780573B2 (ja) * 2017-04-21 2020-11-04 株式会社デンソー バルブタイミング調整装置
US10883616B2 (en) * 2019-02-06 2021-01-05 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve

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DE102007012967B4 (de) 2007-03-14 2009-01-08 Hydraulik-Ring Gmbh Ventil, insbesondere Cartridgeventil, mit integriertem Rückschlagsventil
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JP6025134B2 (ja) 2016-11-16
DE102010045358A1 (de) 2011-10-13
JP2011226474A (ja) 2011-11-10
US8662040B2 (en) 2014-03-04
CN102213120B (zh) 2013-06-05
CN102213120A (zh) 2011-10-12

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