EP1989404A1 - Dispositif d'ajustement variable des instants d'activation des soupapes d'un moteur a combustion interne - Google Patents

Dispositif d'ajustement variable des instants d'activation des soupapes d'un moteur a combustion interne

Info

Publication number
EP1989404A1
EP1989404A1 EP07712058A EP07712058A EP1989404A1 EP 1989404 A1 EP1989404 A1 EP 1989404A1 EP 07712058 A EP07712058 A EP 07712058A EP 07712058 A EP07712058 A EP 07712058A EP 1989404 A1 EP1989404 A1 EP 1989404A1
Authority
EP
European Patent Office
Prior art keywords
inner rotor
internal combustion
camshaft
combustion engine
coupling elements
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.)
Withdrawn
Application number
EP07712058A
Other languages
German (de)
English (en)
Inventor
Matthias Friedrichs
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 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 KG filed Critical Schaeffler KG
Publication of EP1989404A1 publication Critical patent/EP1989404A1/fr
Withdrawn legal-status Critical Current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
    • F01L1/34—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
    • 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

Definitions

  • the invention relates to a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with an inner rotor and a rotatably arranged relative to this outer rotor, wherein the inner rotor has a constant phase relation to a crankshaft of the internal combustion engine, wherein the device comprises one or more coupling elements, in the a drive shaft of an auxiliary unit can engage, and wherein by means of the one or more coupling elements torque can be transmitted from the device to the drive shaft. Furthermore, the invention relates to an internal combustion engine having a device for the variable adjustment of the timing of gas exchange valves of the internal combustion engine and an additional unit, which is driven by a drive shaft via the device.
  • the conventionally used devices for adjusting the rotational angle are in principle designed as a hydraulic actuator which is designed either as a so-called axial piston adjuster or similar to the device known from EP 0 818 609 B1 as a so-called rotary piston displacer.
  • This device is arranged on the anthebs districten end of the mounted in several radial bearings in the cylinder head of the engine camshaft and consists essentially of a standing in driving connection with the crankshaft of the internal combustion engine drive unit and a rotatably connected to the camshaft of the internal combustion engine output unit.
  • the output unit is specifically designed as an impeller (hereinafter referred to as inner rotor) and secured by an axial central screw on the camshaft.
  • the drive unit is designed as a hollow cylinder enclosing the output unit (referred to below as the outer rotor), wherein this arrangement can be closed in a pressure-tight manner by means of two axial side walls.
  • the outer rotor By means of a plurality of radial boundary walls formed on the outer rotor and a plurality of radial vanes formed or mounted on the inner rotor, two pressure chambers, which are acted upon optionally or simultaneously by a hydraulic pressure medium, are formed within the device between two boundary walls, via which the outer rotor is in force transmission connection with the inner rotor.
  • a hydraulic pressure medium for the device while the example taken from one of the radial bearings of the camshaft or an oil distributor lubricating oil of the internal combustion engine is used, which is supplied via radial and axial oil passages of the device.
  • the inner rotor can also be in driving connection with the crankshaft and the outer rotor can be connected in a rotationally fixed manner to the camshaft.
  • a first shaft is driven at one end, for example via a chain, belt or gear wheel, by the crankshaft.
  • a camshaft adjuster can be arranged, wherein the inner rotor rotatably connected to the camshaft.
  • a second shaft can in this case be in drive connection, for example via a chain, belt or gear drive, with the rotatably arranged to the inner rotor outer rotor of the camshaft adjuster.
  • the first shaft may be an intake camshaft (exhaust camshaft) and the second shaft may be an exhaust camshaft (intake camshaft).
  • the timing of the intake camshaft (exhaust camshaft) is fixed.
  • the timing of the other camshaft but variable via the camshaft adjuster.
  • the vacuum pumps for a servo load commonly used in internal combustion engines are usually designed as a vane pump, as can be seen, for example, from DE 85 18 157 U1.
  • This vacuum pump is arranged on a common longitudinal axis with the camshaft in the cylinder head of the internal combustion engine and essentially consists of a stationary to the cylinder head or cylinder head cover of the internal combustion engine arranged housing with a bearing neck and arranged in the housing rotor with a drive shaft which in the is rotatably mounted in the cylinder head of the internal combustion engine protruding bearing neck of the housing.
  • the camshaft still has an axial lubricating oil channel leading to its end face, which is connected on the one hand via a coupling tube with an axial lubricating oil collecting space in the drive shaft of the vacuum pump and on the other hand with the lubricating oil circuit of the internal combustion engine, so that the vacuum pump at the same time with the lubricating oil of the internal combustion engine is lubricated.
  • an internal combustion engine which is equipped with both a device for variable adjustment of the timing of gas exchange valves, as well as with an additional unit.
  • the auxiliary unit in this case a vacuum pump, is equipped with a drive shaft.
  • tattet which is rotatably connected by means of a coupling with the outer rotor or rotatably connected to the outer rotor components.
  • the additional unit is supplied with lubricant by means of a connecting tube via a channel formed within the central screw.
  • Another disadvantage is the supply of lubricant from the camshaft adjuster to the auxiliary unit via the mutually rotating components (inner rotor fixed central screw and outer rotor fixed drive shaft of the additional unit).
  • the invention is therefore based on the object to eliminate these disadvantages and thus an apparatus for variable adjustment of the timing of gas to propose change-over valves of an internal combustion engine, which is suitable for driving an auxiliary unit, such as a vacuum pump, uniformly without negative effects on the adjustment speed and the response of the device occur.
  • the additional unit Due to the rotationally fixed connection of the drive shaft of the auxiliary unit with the inner rotor, which has a fixed phase reference to the crankshaft in each operating state of the internal combustion engine, the moving mass of the additional aggregate is decoupled from the component to be adjusted, in this case the outer rotor.
  • the additional unit does not adversely affect the adjustment speed and the response of the phaser and inertia-related overshoots of the phasing at the end of an adjustment process are avoided.
  • the additional unit is a vacuum pump, for example, for a servo consumer.
  • the inner rotor is fastened to the camshaft by means of a central screw. It can be provided to form the one or more coupling elements on the central screw.
  • this embodiment represents a cost-effective solution.
  • the number of components does not increase and there are only minor modifications, for example to the screw head necessary, which can be realized cost neutral.
  • the coupling elements may be formed, for example, as grooves on the screw head of the central screw.
  • the coupling elements may be designed as formed on the central screw, such as the screw head, formed inside or outside key surfaces.
  • a driver may be provided, which has the one or more coupling elements and executed in one piece with the inner rotor or formed separately to this and rotatably connected to the inner rotor. It can be provided that the separate carrier and the inner rotor are rotatably secured by a central screw on the camshaft.
  • the driver can be cup-shaped, with the central screw passes through the bottom of the driver.
  • the formation of the coupling elements directly to the rotor is a cost-effective solution.
  • at least the side facing away from the camshaft side is formed with a central bore, which is integrally formed with the inner rotor driver or allows the coupling elements to pass through in the axial direction.
  • the coupling elements for example, axially extending pins, can pass through the side cover in the region of circumferentially extending grooves.
  • the coupling elements can already be considered cost-neutral in the forming tool, for example in a sintered form.
  • the drive shaft of the additional unit can be driven by means of one or more separately manufactured to the inner rotor tiger driver, wherein the one or more drivers are rotatably connected to the inner rotor.
  • An inexpensive solution can be realized by the attachment of the driver via the central screw, which rotatably connects the inner rotor with the camshaft.
  • the driver in the interference fit screw - inner rotor - camshaft is arranged.
  • the formation of the coupling elements can be done in a variety of ways.
  • a cost-effective embodiment can be realized, for example, in that the one or more coupling elements are formed as grooves or projections which are complementary to provided on the drive shaft projections or grooves.
  • the camshaft side lubricant can be supplied, wherein at least one outlet opening provided in the region of the coupling element or is, which opens into a receiving opening. This outlet opening may for example be formed centrally on the screw head of the central screw.
  • a connecting tube arranged within the drive shaft, which likewise has a lubricant channel, can engage in the receiving opening in this embodiment, as a result of which the lubricant supply of the additional assembly can be ensured.
  • the outer contour of the connecting tube can be adapted to the inner contour of the receiving opening, whereby leakage is avoided.
  • the connecting tube and the drive shaft of the additional unit are made in one piece or non-rotatably connected to each other, a relative movement of the outer contour of the connecting tube to the inner contour of the receiving opening of the lubricant channel is prevented in this way. As a result, wear and thus lubricant leakage is avoided at this juncture.
  • the device according to the invention is provided according to one of the previously described embodiments.
  • FIG. 1 shows very schematically an internal combustion engine
  • 2a shows a longitudinal section through a first embodiment of a device according to the invention, which is non-rotatably connected by means of a central screw with a camshaft
  • 2a shows a longitudinal section through a first embodiment of a device according to the invention, which is non-rotatably connected by means of a central screw with a camshaft
  • FIG. 2b shows a cross-section through the device from FIG. 2a along the line MB-IIB
  • FIG. 3 shows an enlarged view of the detail Z from FIG.
  • FIG. 4 shows a plan view of the driver and the central screw along the arrow IV in FIG.
  • FIG. 5 shows a longitudinal section through a second embodiment of a device according to the invention
  • FIG. 6 a perspective view of a central screw of the device illustrated in FIG. 5,
  • FIG. 7 shows a longitudinal section through a third embodiment of a device according to the invention
  • FIG 8 shows a longitudinal section through a fourth embodiment of a device according to the invention.
  • FIG. 1 shows by way of example an internal combustion engine 1 in which a device 10 according to the invention can be used.
  • a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a first traction mechanism 5a and two gears 6 with an intake camshaft 7a in drive Connection.
  • a device 10 for the variable adjustment of the timing of gas exchange valves 9a, 9b is arranged thereon.
  • the device 10 drives an exhaust camshaft 7b via a second traction mechanism drive 5b.
  • Cams 8a, 8b of the camshafts 7a, 7b actuate an intake gas exchange valve 9a and an exhaust gas exchange valve 9b, respectively.
  • Torque is transmitted from the crankshaft 2 via the first traction mechanism 5a to the intake camshaft 7a, which is in a fixed phase relation to the crankshaft 2.
  • the second traction mechanism 5b and a gear 6 the exhaust camshaft 7b is driven, wherein the timing of the exhaust gas exchange valve 9b can be varied by means of the device 10.
  • the auxiliary unit 1 1 has a drive shaft 12 which is driven by the device 10.
  • the device 10 according to the invention can also be used in other internal combustion engines 1, for example in internal combustion engines 1 in which an arbitrary camshaft 7a, 7b is driven by means of a traction mechanism 5a, wherein an inner rotor of the device 10 is in direct drive connection with the traction mechanism 5a and an outer rotor rotationally fixed is connected to the camshaft 7a, 7b.
  • FIG. 2a shows a first embodiment of a device 10 according to the invention in longitudinal section.
  • the device 10 is fastened to a camshaft 21 by means of a central screw 20. Furthermore, a portion of the drive shaft 12 of the auxiliary unit 1 1 is shown.
  • the device 10 is shown in cross section.
  • the device 10 has an outer rotor 22, an inner rotor 23 and two side covers 24, 25.
  • the inner rotor 23 is rotatably connected by means of the central screw 20 with the camshaft 21, which is driven at the other end of the crankshaft 2.
  • the inner rotor 23 has at least one essentially cylindrical hub element 26, from the outer cylindrical lateral surface of which extends at least one, in the illustrated embodiment, five wings 27 in the radial direction outwards. In this case, the wings 27 may be integrally formed with the hub member 26.
  • a plurality of projections 30 extend radially inwardly.
  • the protrusions 30 are integrally formed with the peripheral wall 29.
  • the projections 30 wings are provided which are mounted on the peripheral wall 29 and extend radially inwardly.
  • the outer rotor 22 is mounted by means of radially inner circumferential walls of the projections 30 relative to the inner rotor 23 rotatably mounted on this.
  • a sprocket 6 is formed, by means of which a second, not shown camshaft can be driven via a chain drive, also not shown. Alternatively, a belt or gear drive can be provided.
  • each of the projections 30 an axial opening 31 is provided for this purpose, wherein each axial opening 31 is penetrated by a fastening element 32, for example a bolt or a screw, which serves for the rotationally fixed fixing of the side cover 24, 25 on the outer rotor 22.
  • a fastening element 32 for example a bolt or a screw
  • a pressure space 33 is formed, which in the circumferential direction of opposite, substantially radially extending Begren- tion walls 34 adjacent projections 30, in the axial direction of the side covers 24, 25, radially inwardly of the hub member 26 and radially outwardly of the peripheral wall 29 is limited.
  • a wing 27 In each of the pressure chambers 33 projects a wing 27, wherein the wings 27 are formed such that they abut both on the side walls 24, 25, and on the peripheral wall 29. Each wing 27 thus divides the respective pressure chamber 33 into two oppositely acting pressure chambers 35, 36.
  • the outer rotor 22 is rotatably arranged in a defined Winkeibreich to the inner rotor 23.
  • the angular range is limited in a direction of rotation of the outer rotor 22 in that at least one of the vanes 27 comes into contact with a boundary wall 34 of the pressure space 33 formed as an early stop 34a.
  • the angular range in the other direction of rotation is limited by the fact that at least one vane 27 comes into contact with the other boundary wall 34, which serves as a late stop 34b.
  • a rotation limiting device may be provided which limits the rotation angle range of the outer rotor 22 to the inner rotor 23.
  • the phase angle of the outer rotor 22 to the inner rotor 23 can be varied.
  • the phase position of the two rotors 22, 23 can be kept constant relative to one another.
  • hydraulic pressure medium the oil removed from an oil distributor 37 lubricating oil of the internal combustion engine 1 is used in the illustrated embodiment. This passes from the oil distributor 37 via radial and axial oil passages 38 within the camshaft 21 and via radial pressure medium lines 39, which are formed on the inner rotor 23, to the pressure chambers 35, 36th
  • the inner rotor 23 is fixed to the camshaft 21 by means of the central screw 20.
  • the inner rotor 23 is formed with a shoulder 40, in which the camshaft 21 engages.
  • the central screw 20 passes through a formed on the inner rotor 23 recess 41 and is rotatably connected to the Camshaft 21 bolted.
  • a screw head 42 of the central screw 20 By means of a screw head 42 of the central screw 20, an interference fit is produced between the central screw 20, the inner rotor 23 and the camshaft 21, and thus the inner rotor 23 is non-rotatably connected to the camshaft 21 via a non-positive connection.
  • a driver 43 is arranged within this interference fit.
  • the driver 43 is formed as a cup-shaped member, which is made for example of a steel sheet by means of a chipless forming process.
  • the central screw 20 passes through the base of the cup-shaped carrier 43 and connects it rotatably with the inner rotor 23.
  • the driver 43 and the screw head 42 of the central screw 20 are shown in enlarged form in FIGS. 3 and 4.
  • 43 coupling elements 44 are formed on the driver, can engage in the complementary coupling elements of the drive shaft 12 of the auxiliary unit 11.
  • the coupling elements 44 are formed as slots or grooves in a circular circumferential, in cross-section U-shaped edge of the driver 43.
  • FIG 2a engage in the coupling elements 44 complementary coupling elements of the drive shaft 12 of the auxiliary unit 1 1 a.
  • the lubrication of the auxiliary unit 11 takes place in this embodiment via a arranged within the drive shaft 12 connecting pipe 46.
  • the central screw 20 is formed with an axial lubricant channel 47, which is applied at one end via a radial bearing 37a with lubricant.
  • the screw head 42 is provided with a receiving opening 48 into which one end of the connecting tube 46 sealingly engages.
  • the lubricant channel 47 opens into the receiving opening 48 via an outlet opening 48a.
  • a further lubricant channel 49 is formed, via which lubricant entering from the lubricant channel 47 into the receiving opening 48 can reach the additional unit 11.
  • the lubricant supply of the auxiliary unit 1 1 can bei- For example, directly via a housing of the additional unit 1 1 done.
  • FIG. 5 shows a second embodiment of a device 10 according to the invention.
  • This embodiment is largely identical to the embodiment shown in FIG. 2a.
  • the driver 43 was omitted here and the coupling elements 44, as shown in Figure 6, incorporated directly into the screw head 42 of the central screw 20.
  • the coupling elements 44 may be formed, for example, as grooves 45a on the outer circumference of the central screw 20 or as internal or external key surfaces 45b on the screw head 42 of the central screw 20.
  • FIGS. 7 and 8 show two further embodiments of a device 10 according to the invention. These are largely identical to the first embodiment, with the difference that the coupling elements 44 are formed integrally with the inner rotor 23.
  • the coupling elements 44 are designed as blind-hole-like receptacles which are formed on an axial side surface of the inner rotor 23. In this recordings engage on the drive shaft 12 formed pin.
  • a driver 43 on which the coupling elements 44 are formed, or coupling elements 44 themselves are formed integrally with the inner rotor 23.
  • the driver 43 and the coupling elements 44 which are configured as pins, for example, pass through elongated holes in the axial direction which are formed on the camshaft side cover 24 and extend in the circumferential direction, with the coupling elements 44, for example pins, engaging in complementary coupling elements of the drive shaft.
  • the coupling elements can also pass through a central opening of the side cover 24 facing away from the camshaft in the axial direction.
  • the application of the invention is not limited to the illustrated embodiment of a camshaft adjuster.
  • the inner rotor 23 is designed as a camshaft-fixed and the outer rotor 22 as a rotatable element.
  • the invention in electromechanical phasers, in which the adjustment between outer rotor 22 and inner rotor 23 via a mechanical transmission, such as a planetary gear, an réelleexzentergetriebe, a swash plate gear, a wave gear or similar gearbox, with the aid of an electrical see drive ,
  • the inner rotor 23 may be formed as camshaft-fixed and the outer rotor 23 as rotatably arranged gear member.

Landscapes

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

Abstract

L'invention concerne un dispositif (10) qui permet d'ajuster de manière variable les instants d'activation des soupapes (9a, 9b) d'un moteur à combustion interne (1), lequel dispositif présente un rotor intérieur (23) et un rotor extérieur (22) disposé à rotation par rapport au premier, le rotor intérieur (22) présentant un déphasage constant par rapport à l'arbre de vilebrequin (2) du moteur à combustion interne (1). Le dispositif (10) présente un ou plusieurs éléments d'accouplement (44) dans lesquels un arbre d'entraînement (12) d'un mécanisme supplémentaire (11) peut s'engager, le couple de rotation pouvant être transmis du dispositif (10) à l'arbre d'entraînement (12) au moyen du ou des éléments d'accouplement (44). Il est prévu selon l'invention de relier le ou les éléments d'accouplement (44) à rotation solidaire au rotor intérieur (23) ou de les former d'un seul tenant avec ce dernier.
EP07712058A 2006-02-18 2007-01-19 Dispositif d'ajustement variable des instants d'activation des soupapes d'un moteur a combustion interne Withdrawn EP1989404A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006007671A DE102006007671A1 (de) 2006-02-18 2006-02-18 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2007/050521 WO2007093480A1 (fr) 2006-02-18 2007-01-19 Dispositif d'ajustement variable des instants d'activation des soupapes d'un moteur a combustion interne

Publications (1)

Publication Number Publication Date
EP1989404A1 true EP1989404A1 (fr) 2008-11-12

Family

ID=37993266

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07712058A Withdrawn EP1989404A1 (fr) 2006-02-18 2007-01-19 Dispositif d'ajustement variable des instants d'activation des soupapes d'un moteur a combustion interne

Country Status (6)

Country Link
US (1) US7886704B2 (fr)
EP (1) EP1989404A1 (fr)
JP (1) JP2009526941A (fr)
KR (1) KR101291503B1 (fr)
DE (1) DE102006007671A1 (fr)
WO (1) WO2007093480A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008031120A1 (de) * 2007-11-02 2009-05-07 Daimler Ag Brennkraftmotorenventiltriebvorrichtung
DE102008007561B4 (de) * 2008-02-05 2019-08-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Nockenwellensteller mit einem Mitnehmerflansch, mit dem zumindest ein Nebenaggregat einer Brennkraftmaschine drehend antreibbar ist
DE102011001301B4 (de) * 2011-03-16 2017-09-21 Hilite Germany Gmbh Schwenkmotorversteller
US8800513B2 (en) * 2011-05-20 2014-08-12 Delphi Technologies, Inc. Axially compact coupling for a camshaft phaser actuated by electric motor
JP7022219B2 (ja) * 2018-09-28 2022-02-21 本田技研工業株式会社 内燃機関

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260546A1 (de) * 2002-12-21 2004-07-01 Ina-Schaeffler Kg Brennkraftmaschine mit einer Vorrichtung zur hydraulischen Drehwinkelverstellung ihrer Nockenwelle gegenüber ihrer Kurbelwelle sowie mit einer Vakuumpumpe für einen Servoverbraucher, insbesondere für einen Bremskraftverstärker

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Publication number Priority date Publication date Assignee Title
DE8518157U1 (de) 1985-06-22 1986-10-16 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Flügelzellenvakuumpumpe
JP3888395B2 (ja) 1996-07-11 2007-02-28 アイシン精機株式会社 弁開閉時期制御装置
GB2350660A (en) * 1999-06-01 2000-12-06 Mechadyne Internat Plc Phase change coupling
JP2001263025A (ja) * 2000-03-16 2001-09-26 Nissan Motor Co Ltd 内燃機関の補機駆動用カップリング装置
JP4042661B2 (ja) * 2003-08-29 2008-02-06 アイシン精機株式会社 弁開閉時期制御装置
GB2415745A (en) * 2004-06-29 2006-01-04 Mechadyne Plc Engine with VVT drives an auxiliary device from an unphased part of the camshaft
JP4161277B2 (ja) 2005-03-11 2008-10-08 アイシン精機株式会社 弁開閉時期制御装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260546A1 (de) * 2002-12-21 2004-07-01 Ina-Schaeffler Kg Brennkraftmaschine mit einer Vorrichtung zur hydraulischen Drehwinkelverstellung ihrer Nockenwelle gegenüber ihrer Kurbelwelle sowie mit einer Vakuumpumpe für einen Servoverbraucher, insbesondere für einen Bremskraftverstärker

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2007093480A1 *

Also Published As

Publication number Publication date
US7886704B2 (en) 2011-02-15
KR20080103053A (ko) 2008-11-26
DE102006007671A1 (de) 2007-09-06
US20090013948A1 (en) 2009-01-15
KR101291503B1 (ko) 2013-08-01
WO2007093480A1 (fr) 2007-08-23
JP2009526941A (ja) 2009-07-23
WO2007093480A8 (fr) 2008-11-27

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