EP1607590A2 - Moteur muni d'un déphaseur d'arbre à cames hydraulique - Google Patents

Moteur muni d'un déphaseur d'arbre à cames hydraulique Download PDF

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Publication number
EP1607590A2
EP1607590A2 EP05010196A EP05010196A EP1607590A2 EP 1607590 A2 EP1607590 A2 EP 1607590A2 EP 05010196 A EP05010196 A EP 05010196A EP 05010196 A EP05010196 A EP 05010196A EP 1607590 A2 EP1607590 A2 EP 1607590A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic fluid
volume
hydraulic
piston
accumulator
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
EP05010196A
Other languages
German (de)
English (en)
Other versions
EP1607590B1 (fr
EP1607590A3 (fr
Inventor
Jochen Auchter
Michael Busse
Andreas Strauss
Dirk Heintzen
Lutz Witthöft
Jürgen Plate
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
INA Schaeffler KG
Schaeffler 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 INA Schaeffler KG, Schaeffler KG filed Critical INA Schaeffler KG
Publication of EP1607590A2 publication Critical patent/EP1607590A2/fr
Publication of EP1607590A3 publication Critical patent/EP1607590A3/fr
Application granted granted Critical
Publication of EP1607590B1 publication Critical patent/EP1607590B1/fr
Expired - Fee Related 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
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to an internal combustion engine having a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft, comprising: a rotor with wings arranged thereon, which is rotatably connected to the camshaft and a stator which is non-rotatably connected to a driven by the crankshaft drive wheel, wherein on both sides of the wing pressure chambers are provided, which are pressurizable or emptying via a hydraulic system with hydraulic fluid.
  • Such a device is generic from DE 199 63 094 A1 previously known.
  • This trained as so-called rempligelzellenverstell Sharp Device consists essentially of one with a crankshaft Internal combustion engine in drive connection stationary stator, the rotation with a drive wheel is connected, and a rotationally fixed to a camshaft the internal combustion engine connected rotor.
  • the stator has a formed by a hollow cylindrical peripheral wall and two side walls Cavity in which by boundary walls hydraulic work spaces be formed.
  • the rotor has radially on the circumference of its hub each a working space of the drive wheel extending wings, which the work spaces in two oppositely acting hydraulic pressure chambers divide.
  • each working space The pressure chambers of each working space are against each other sealed and cause with selective and simultaneous pressurization with hydraulic fluid from a hydraulic fluid circuit, in usually with engine oil, a pivoting movement or a fixation of the rotor relative to the stator and thus the camshaft relative to the crankshaft.
  • the invention is therefore based on the object in a hydraulic fluid circuit provided with a device for rotational angle adjustment Internal combustion engine to reduce pressure fluctuations as much as possible and thus in particular to eliminate pressure peaks.
  • this object is achieved by the features of the characterizing Part of claim 1 solved. Accordingly, in the hydraulic fluid circuit between the device for rotational angle adjustment and the associated Hydraulic valve arranged a volume storage.
  • This one stands out characterized in that its volume is variable and solely by the pressure in the Hydraulic fluid circuit is determined. Increases then suddenly the Pressure in the hydraulic fluid circuit, there is an increase in the hydraulic fluid available volume through the volume memory. This volume release counteracts the pressure change. In the reverse In the case, the volume accumulator reduces this for the hydraulic fluid in the hydraulic fluid circuit available volumes. Is the inertia of the Volume memory low, it can also be generated by a pressure peak Pulsing counteract as a vibration damper.
  • the spring element for example, designed as a helical spring is located in the piston and faces the open side of the piston.
  • the blind hole be executed as a clearance.
  • the leakage, which despite the fit located behind the piston is discharged through a vent hole, so that the way of the piston is not limited early.
  • the space behind the piston can also by means of a Seal to be sealed.
  • the spring element tries under the opening pressure of the piston accumulator, the piston in the direction Hydraulic fluid system to press and may be a hydraulic fluid line close.
  • a forward-acting path limiter in the hydraulic fluid system brought in This can be an additional component, for example is arranged in the hydraulic fluid line or in the volume memory, but can also be done by a suitable design of the piston crown.
  • the bias is chosen so that in each case a flow in the Hydraulic fluid system is possible, even if there is no pressure in the system.
  • a locking unit of the device which at insufficient pressure in the hydraulic fluid system, the device in one Fixed position fixed, at the same time to use as a volume storage. Because locking units in all modern devices for angular adjustment exist, manufacturing steps can be saved or eliminated.
  • the volume accumulator can also act as a bubble or as a membrane reservoir will be realized. Both types of memory serve as well as the piston accumulator in addition, the volume for the hydraulic fluid in the hydraulic fluid system to increase, so as to reduce pressure fluctuations. As the bubbles or Membrane memory supporting element can be any element, the springs are used. The main advantages of these solutions the piston spring accumulator are in their faster response. This can be cached with a piston spring accumulator a larger volume.
  • the membrane of a membrane memory has a low inertia a piston spring storage solution. This means significantly higher vibration frequencies possible. Due to their frequency complementary behavior the piston spring accumulator is particularly suitable combination of these two Solutions: Most high-frequency vibrations are low Amplitude and can be absorbed well through a membrane. The lower frequency vibrations have a larger amplitude, which a larger compensating volume requires that with a piston spring accumulator can be better realized. Due to the lower frequency is one in comparison To the membrane slower response here is not a disadvantage.
  • the inventively designed volume storage so dynamic Pressure changes in the hydraulic fluid system caught and also reduces any pulsation of the volume flow. This will be an improvement in the reliability of the device for adjusting the rotational angle and other hydraulic systems in the internal combustion engine. In addition, the durability of seals and other components elevated.
  • FIGS. 1 a and 1 b show a device 1 for adjusting the rotational angle between a crankshaft not shown and also not shown Camshaft out.
  • This device 1 is as Rotationskolbenverstell Road at the drive end of the cylinder head, not shown the internal combustion engine mounted camshaft attached and in principle designed as a hydraulic actuator, depending on different Operating parameters of the internal combustion engine by a hydraulic valve. 2 via hydraulic fluid lines 19 of a hydraulic fluid system 32 is controlled.
  • the device 1 consists essentially of a with the crankshaft via a drive wheel 3 in drive connection Stator 4 and a rotatably connected to the camshaft rotor 5, wherein the rotor 5 is pivotally mounted in the drive wheel 3 and with this in Power transmission connection is.
  • the drive wheel 3 has a through a hollow cylindrical peripheral wall 6 and two side walls 7, 7 'formed Cavity, in which directed by the longitudinal central axis of the device 1 radial reference walls 8, 8 'evenly distributed hydraulic working spaces 9 are formed.
  • the rotor 5 has accordingly on the circumference of his Wheel hub 10 equally circumferentially distributed and each in a work space 9 of the drive wheel 3 extending wings 11, which the work spaces Divide 9 into each of an A-pressure chamber 12 and a B-pressure chamber 13, in the case of selective or simultaneous pressurization with a Hydraulic fluid against a pivoting movement or fixation of the rotor 5 the stator 4 and thus a rotational angle adjustment or a hydraulic Causing clamping of the camshaft relative to the crankshaft.
  • a locking element 14 can be seen, which is to avoid a from the alternating torques of the camshaft resulting Anschlagklapperns of the rotor 5 at the start of the internal combustion engine is used.
  • the locking element 14 is below one required for adjustment Hydraulic fluid pressure in a preferred base position within its Adjustment range mechanically coupled to the stator 4. It's as sleeve-like Cylindrical pin formed and in a continuous axial bore 15 in arranged the wheel hub 10 of the rotor.
  • a locking spring element 16 which on the one hand on the back of the locking element 14 and on the other hand on a likewise inserted into the axial bore 15 counter-holder is capable of, within a receptacle 18 in the camshaft facing away Side wall 6 of the stator 4, the locking element 14 to move.
  • the A-pressure chambers 12 and B-pressure chambers 13 are through Hydraulic fluid lines 19 connected to the hydraulic valve 2. In the Hydraulic fluid lines 19, a volume memory 20 is arranged.
  • FIG. 2 shows a cross section of a piston accumulator 34 Volume memory 20. It adjoins formed as a blind hole 21 directly to the Hydraulic fluid line 19 on.
  • a piston 22 with arranged a piston skirt 23, wherein the piston skirt 23, the piston 22nd in the blind hole 21 leads axially, a spring element 24 receives and by his Form limits the axial spring travel, while at large deflection of the Spring element 24 at the bottom of the blind hole 21 touches.
  • a change the pressure in the hydraulic fluid line 19 therefore causes a deflection of the spring element 24, which is a change of the hydraulic fluid available volume.
  • the volume change counteracts the pressure change.
  • the selection of a suitable spring element 24 or the arrangement of a Wegbeskyrs 33 put it sure that the hydraulic fluid line 19 is never completely closed.
  • the blind hole 21 is designed as a clearance fit. The oil leakage, which is despite the fit behind the piston, for example removed via a vent hole 25. This will be the way of the Piston 22 not limited early.
  • the volume memory 20 may be formed as a separate unit, or it is integrated into the locking element 14.
  • the axial bore corresponds 15 the blind hole 21 and the piston 22 the locking element 14th
  • FIGS. 3 a and 3 b show a volume accumulator integrated in the wing 11 20.
  • the wing 11 is formed in two parts and has a passage opening 29, wherein within the wing 11 in the radial direction at least one Cavity 27 is formed in the two designed as slices piston 22nd are used so that the piston 22, the passage opening 29 to both Close sides.
  • the pistons 22 are interconnected by disc springs 30 and on the other, outer side by the respective edge region 31 of the wings 11 supported. Instead of disc springs 30 can also another, elastic element can be used.
  • the piston 22 is displaced and thus causes a volume change of the chamber.
  • the repressed Air in the cavity 27 is through a vent hole 25, which with the cavity 27 is connected, as well as a potential hydraulic fluid leakage dissipated.
  • FIG. 4 shows a volume accumulator 20, which acts as an elastic tube 26 trained diaphragm accumulator is realized.
  • a cavity 27 is introduced, in which the elastic Tubes 26 are arranged. These are made of plastic or metal.
  • the elastic tube 26 takes over the same function the piston 22 and the spring element 24 of the piston accumulator design.
  • the spring stiffness of the system is determined by the design of the elastic Pipe 26 set. Conveniently, the membrane is glued or trapped.
  • the membrane 28 can also be shaped as a bubble and the function as a working component of a assume the hydraulic fluid line 19 arranged bladder accumulator.
  • the gas-filled bladder is fixed in place, and its extent depends after the pressure surrounding them.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP05010196A 2004-06-15 2005-05-11 Moteur muni d'un déphaseur d'arbre à cames hydraulique Expired - Fee Related EP1607590B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004028868 2004-06-15
DE102004028868A DE102004028868A1 (de) 2004-06-15 2004-06-15 Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle

Publications (3)

Publication Number Publication Date
EP1607590A2 true EP1607590A2 (fr) 2005-12-21
EP1607590A3 EP1607590A3 (fr) 2008-10-15
EP1607590B1 EP1607590B1 (fr) 2013-02-13

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EP05010196A Expired - Fee Related EP1607590B1 (fr) 2004-06-15 2005-05-11 Moteur muni d'un déphaseur d'arbre à cames hydraulique

Country Status (3)

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US (1) US7222597B2 (fr)
EP (1) EP1607590B1 (fr)
DE (1) DE102004028868A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009089984A1 (fr) * 2008-01-19 2009-07-23 Schaeffler Kg Dispositif de réglage variable des temps d'ouverture et de fermeture des soupapes d'échange des gaz d'un moteur à combustion interne
WO2011032805A1 (fr) * 2009-09-18 2011-03-24 Schaeffler Technologies Gmbh & Co. Kg Dispositif pour le réglage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne
CN103244222A (zh) * 2012-02-02 2013-08-14 谢夫勒科技股份两合公司 止回阀、具有其的转子和具有该转子的凸轮轴调节器
CN103291399A (zh) * 2012-02-02 2013-09-11 谢夫勒科技股份两合公司 容积存储器在凸轮轴调节器中的布置方案
CN110730856A (zh) * 2017-06-19 2020-01-24 舍弗勒技术股份两合公司 液压凸轮轴调节器和用于运行液压凸轮轴调节器的方法

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DE102005044176A1 (de) * 2005-09-16 2007-03-29 Braun Gmbh Haarentfernungsgerät
JP4640616B2 (ja) 2006-08-23 2011-03-02 アイシン精機株式会社 弁開閉時期制御装置
DE102007056550A1 (de) * 2007-11-23 2009-05-28 Schaeffler Kg Modular aufgebauter Nockenwellenversteller mit Ketten- oder Riemenrad
DE102008037997B4 (de) 2008-08-16 2019-08-22 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE112009002377A5 (de) * 2008-10-16 2011-06-30 Schaeffler Technologies GmbH & Co. KG, 91074 Hydraulikanordnung zur Steuerung eines Getriebes
US8524185B2 (en) * 2008-11-03 2013-09-03 Basf Corporation Integrated SCR and AMOx catalyst systems
DE102010012482B4 (de) * 2010-03-24 2018-07-12 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102010053685B4 (de) * 2010-12-08 2014-10-30 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle
DE102010063700A1 (de) * 2010-12-21 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Nockenellenversteller
DE102011003991A1 (de) * 2011-02-11 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller mit einem Druckspeicher
DE102012201560B4 (de) * 2012-02-02 2019-02-21 Schaeffler Technologies AG & Co. KG Volumenspeicherausführung in einer Nockenwellenverstellvorrichtung
US10156164B2 (en) 2012-02-02 2018-12-18 Schaeffler Technologies AG & Co. KG Arrangement of a volume accumulator in a camshaft adjuster
DE102012201551B4 (de) 2012-02-02 2022-05-12 Schaeffler Technologies AG & Co. KG Nockenwellenversteller und Verfahren zum Füllen eines Volumenspeichers in einem Nockenwellenversteller
DE102015204040B4 (de) 2015-03-06 2021-07-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
CA3002136C (fr) * 2015-10-16 2020-12-22 Yamaha Hatsudoki Kabushiki Kaisha Module d'entrainement destine a des vehicules relies par chevauchement
DE102017102273A1 (de) 2017-02-06 2018-08-09 Denso Corporation Nockenwellensteller mit Dämpfungs-Akkumulator
DE102018000609A1 (de) 2018-01-25 2019-07-25 Daimler Ag Drehwinkelverstelleinheit für eine Verbrennungskraftmaschine

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DE19903624A1 (de) 1998-01-30 1999-08-12 Aisin Seiki Variabler Ventilsteuerzeitenregler
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JP2001263008A (ja) 2000-03-16 2001-09-26 Aisin Seiki Co Ltd 弁開閉時期制御装置

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Publication number Priority date Publication date Assignee Title
DE19837693A1 (de) 1997-08-21 1999-02-25 Schaeffler Waelzlager Ohg Anordnung zur Steuerung einer Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE19903624A1 (de) 1998-01-30 1999-08-12 Aisin Seiki Variabler Ventilsteuerzeitenregler
DE19963094A1 (de) 1999-12-24 2001-06-28 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere hydraulische Nockenwellen-Verstelleinrichtung in Rotationskolbenbauart
JP2001263008A (ja) 2000-03-16 2001-09-26 Aisin Seiki Co Ltd 弁開閉時期制御装置

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009089984A1 (fr) * 2008-01-19 2009-07-23 Schaeffler Kg Dispositif de réglage variable des temps d'ouverture et de fermeture des soupapes d'échange des gaz d'un moteur à combustion interne
US8459221B2 (en) 2008-01-19 2013-06-11 Schaeffler Technologies AG & Co. KG Device for variably adjusting the control times of gas exchange valves of an internal combustion engine
KR101489985B1 (ko) * 2008-01-19 2015-02-06 섀플러 테크놀로지스 게엠베하 운트 코. 카게 내연 기관의 가스 교환 밸브들의 제어 시간 가변 조정 장치
WO2011032805A1 (fr) * 2009-09-18 2011-03-24 Schaeffler Technologies Gmbh & Co. Kg Dispositif pour le réglage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne
US8763574B2 (en) 2009-09-18 2014-07-01 Schaeffler Technologies Gmbh & Co. Kg Device for variably adjusting the control times of gas exchange valves of an internal combustion device
CN103244222A (zh) * 2012-02-02 2013-08-14 谢夫勒科技股份两合公司 止回阀、具有其的转子和具有该转子的凸轮轴调节器
CN103291399A (zh) * 2012-02-02 2013-09-11 谢夫勒科技股份两合公司 容积存储器在凸轮轴调节器中的布置方案
CN110730856A (zh) * 2017-06-19 2020-01-24 舍弗勒技术股份两合公司 液压凸轮轴调节器和用于运行液压凸轮轴调节器的方法
CN110730856B (zh) * 2017-06-19 2022-02-01 舍弗勒技术股份两合公司 液压凸轮轴调节器和用于运行液压凸轮轴调节器的方法

Also Published As

Publication number Publication date
EP1607590B1 (fr) 2013-02-13
US7222597B2 (en) 2007-05-29
DE102004028868A1 (de) 2006-01-05
EP1607590A3 (fr) 2008-10-15
US20050274344A1 (en) 2005-12-15

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