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WO2010006856A1 - Dispositif de réglage variable de la périodicité de soupapes d'échange de gaz d'un moteur à combustion interne - Google Patents

Dispositif de réglage variable de la périodicité de soupapes d'échange de gaz d'un moteur à combustion interne Download PDF

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Publication number
WO2010006856A1
WO2010006856A1 PCT/EP2009/057165 EP2009057165W WO2010006856A1 WO 2010006856 A1 WO2010006856 A1 WO 2010006856A1 EP 2009057165 W EP2009057165 W EP 2009057165W WO 2010006856 A1 WO2010006856 A1 WO 2010006856A1
Authority
WO
WIPO (PCT)
Prior art keywords
camshaft
opening
pressure medium
output element
flow area
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/EP2009/057165
Other languages
German (de)
English (en)
Inventor
Ahmet Deneri
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.)
IHO Holding GmbH 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
Priority to EP09779705A priority Critical patent/EP2313619A1/fr
Priority to US13/003,640 priority patent/US20110120400A1/en
Priority to CN200980127280XA priority patent/CN102089503A/zh
Publication of WO2010006856A1 publication Critical patent/WO2010006856A1/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

Definitions

  • the invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine with a drive element, an output element and a camshaft, wherein the Antriebsele- ment can be brought into driving connection with a crankshaft of the internal combustion engine, wherein the output member is rotatably connected to the camshaft and pivotally is arranged to the drive element, wherein at least a first pressure chamber is provided, wherein by supplying pressure medium to or removal of pressure medium from the first pressure chamber a phase position between the driven element and the drive element is variable, wherein an axial side surface of the camshaft at an axial Lateral side of the output element is present, wherein the camshaft has at least a first pressure medium line with a first opening at the axial side surface, wherein the output element at least a second pressure medium line with a second having opening at the axial side face and opens into the first pressure chamber and the first opening of the second opening facing axially.
  • the device is integrated into a drive train, via which torque is transmitted from the crankshaft to the camshaft.
  • This powertrain can be realized, for example, as a belt, chain or gear drive.
  • Such a device is known for example from US 5,901, 674 A.
  • the device comprises an output element which is arranged rotatably to a drive element, wherein the drive element is in drive connection with the crankshaft and the output element is non-rotatably connected to the camshaft.
  • the device is limited by a respective side cover.
  • the output element, the drive element and the two side covers define five pressure chambers, wherein each of the pressure chambers is divided by a wing into two counteracting pressure chambers.
  • the wings By supplying pressure medium to or pressure fluid removal from the pressure chambers, the wings are displaced within the pressure chambers in the circumferential direction of the device, whereby a targeted rotation of the output element is effected to the drive element and thus the camshaft to the crankshaft.
  • a plurality of axial pressure medium line are provided, which are formed as bores.
  • This pressure medium can be supplied to the pressure chambers.
  • Each of the pressure medium lines, which are formed within the camshaft opens at the axial side surface of the camshaft into a corresponding pressure medium line, which are formed as bores in the output element and communicate with at least one of the pressure chambers.
  • the opening of a pressure medium line in the axial direction is directly opposite the opening of the second pressure medium line.
  • a disadvantage of this embodiment is that care must be taken during assembly of the output element to the camshaft that the bores of the driven element are aligned with the holes of the camshaft. Deviation of the orientation in the circumferential direction lead to misalignment, whereby a throttle point arises at the interface between the camshaft and the output element. This affects the adjustment speed and the dynamics of the phase adjustment. For too large deviations speed and dynamics of phase adjustment. Too large deviations of the misalignment can also lead to the complete inoperability of the device.
  • the orientation of the components to each other is ensured by press-fit pins.
  • a bore is provided both in the camshaft and in the output element.
  • a pin is pressed into the bore of the output element, which is then likewise fixed in a non-positive fit in the bore of the camshaft.
  • this is a complex and costly, multi-stage production process.
  • due to the double interference fit of the pin tolerance deviations of the openings to each other can not be compensated. As a result, throttling effects can occur at the interface between the output element and the camshaft in spite of the orientation of the components relative to one another.
  • the invention has for its object to provide a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine, with an interface between the camshaft and the driven element to be created, which allows lossless pressure medium transfer. In this case, cost-intensive and error-prone alignment measures should be avoided during assembly of the output element to the camshaft.
  • the object is achieved in that the flow area of the first or the second opening (larger opening) is made larger than the flow area of the pressure medium line of the other opening.
  • the device has at least one drive element and at least one output element.
  • the drive element is in the assembled state of the device via a traction drive, such as a belt or chain drive, or a gear drive with the crankshaft in drive connection.
  • the Output element is arranged in a defined angular range pivotally relative to the drive element and rotatably connected to the camshaft. In this case, an axial side surface of the camshaft bears against an axial side surface of the output element.
  • the non-rotatable connection between the camshaft and the output element can be produced, for example, by means of a central screw, which passes through the output element and engages in a threaded portion of the camshaft, so that a frictional connection between the abutting side surfaces is produced.
  • At least two mutually acting pressure chambers are provided by the pressurization of the output element can be pivoted relative to the drive element.
  • several pairs are provided against each other acting pressure chambers whereby the pressure transmission is increased.
  • the first pressure medium lines open by means of openings on the output element side axial side surface.
  • the first pressure medium lines communicate with second pressure medium lines, which are formed on or within the output element.
  • These may be, for example, radially extending grooves in the camshaft side side surface of the output element, wherein each of these grooves opens into a corresponding pressure chamber.
  • axially extending pressure medium lines are provided, which extend from the side surface of the output element into this and in each case communicate with a radial bore, each of which opens into a corresponding pressure chamber.
  • the term bore is to be understood as meaning a pressure medium path of any cross-section within the component which can be produced in a wide variety of ways.
  • the bore can already be formed during the shaping of the output element. If the output element is designed, for example, as a sintered component the bore can already be taken into account in the forming tool and thus be produced during the sintering process without additional process steps. Also conceivable is the subsequent introduction of these holes by cutting process steps.
  • the second pressure medium lines open by means of second openings on the camshaft side axial side surface of the output element.
  • Each of the first openings is axially opposite one of the second openings.
  • the flow areas (cross sections) of the first or the second openings or both openings are formed larger than the flow area of the respective other pressure medium line.
  • the flow area is the area perpendicular to the flow direction of the pressure medium to understand.
  • Under flow area of the pressure medium line is in the case of uniform pressure medium lines the flow area, to understand pressure medium line with varying flow area whose minimum flow area.
  • the greater formation of one of the openings ensures that their overlap area corresponds at least to the minimum flow cross-section of the pressure medium lines.
  • the flow area of the first opening is made larger than the flow area of the second pressure medium line and that the flow area of the second opening is made larger than the flow area of the first pressure medium line.
  • the flow area of the first or the second opening is made larger than the flow area of the other opening.
  • the extent of the larger opening in the circumferential direction of the camshaft may be greater than the extent of the other opening in the circumferential direction of the camshaft.
  • the larger opening to the side surface of the opposite component has a funnel-shaped enlargement.
  • the larger opening may be formed as a groove. This is easy to realize, for example, during a sintering process, and at no extra cost. Also conceivable, however, are also machining finishing steps.
  • the output element or the camshaft has a form-locking element and the other component has a counter-form-locking element for receiving the form-locking element, wherein the form-fit element is formed integrally with the respective component.
  • the form-locking element forms an axial projection on the side surface of the respective component. This may be, for example, a free-standing projection or designed as a deviation of an otherwise rotationally symmetrical structure.
  • This one-part design of the positive-locking element with the output element or the camshaft represents a cost-effective alternative to the prior art, separately manufactured and non-positively connected with the components pins.
  • the interlocking element can be subject to larger tolerances without hindering the transfer of pressure medium. Elaborate post-processing steps are not necessary. In a concretization can be provided to form the interlocking element on the output element and perform as a local axial survey.
  • FIG. 1 shows very schematically an internal combustion engine
  • FIG. 2 shows a longitudinal section through an embodiment according to the invention of a device for changing the timing of gas exchange valves of an internal combustion engine
  • FIG. 3 shows a plan view of the output element from FIG. 2,
  • Figure 4 is a plan view of the output member end of a camshaft.
  • FIG. 1 shows an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second device 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslrawgas batventile 10.
  • it may be provided to equip only one of the camshafts 6, 7 with a device 11, or provide only a camshaft 6, 7, and this equipped with a device 11.
  • the device 11 has a drive element 12 and an output element 14.
  • the drive element 12 has a housing 13 and two side covers 15, 16, which are arranged on the axial side surfaces of the housing 13. Starting from an outer peripheral wall 19 of the housing 13, five projections 20 extend radially inwardly. In the illustrated embodiment, the projections 20 are formed integrally with the peripheral wall 19.
  • the drive element 12 is arranged by means of radially inner bearing surfaces 20a of the projections 20 relative to the output member 14 rotatable thereto.
  • the output element 14 shown in Figure 3 is in the form of an impeller and has a substantially cylindrically shaped hub member 17, extend from the outer cylindrical surface in the illustrated embodiment, five wings 18 in the radial direction outwards.
  • the wings 18 are formed integrally with the hub member 17.
  • a sprocket 21 is formed, via which by means of a chain drive, not shown, torque can be transmitted from the crankshaft 2 to the drive element 12.
  • the output element 14 is connected by means of a central screw 22 with the camshaft 6, 7.
  • the central screw 22 passes through a central bore 22a of the output element 14 and is screwed to the camshaft 6, 7.
  • each of the side covers 15, 16 is arranged on one of the axial side surfaces of the housing 13 and rotatably attached thereto.
  • fasteners are provided, each pass through a projection 20 and both side cover 15, 16 and fix each other.
  • a pressure chamber 24 is formed between each two circumferentially adjacent projections 20.
  • Each of the pressure chambers 24 is circumferentially opposed, substantially radially extending boundary walls of adjacent projections 20, in the axial direction of the side covers 15, 16, radially inwardly of the hub element 17 and radially outwardly bounded by the peripheral wall 19.
  • In each of the pressure chambers 24 protrudes a wing 18, wherein the wings 18 are formed such that they rest against both the side covers 15, 16, and on the peripheral wall 19.
  • Each vane 18 thus divides the respective pressure chamber 24 into two counteracting pressure chambers 26a, 26b, the position of which is indicated in FIG.
  • the output element 14 is rotatably arranged in a defined Winkeibreich to the drive element 12.
  • the angular range is limited in one direction of rotation of the driven element 14 in that the wings 18 come into contact with a respective boundary wall (early stop) of the pressure chambers 24.
  • the angular range in the other direction of rotation is limited by the fact that the wings 18 come to rest on the other boundary walls of the pressure chambers 24, which serve as a late stop.
  • the output element 14 has a centering collar 25, which is formed on a cam shaft-facing axial side surface 37.
  • the centering collar 25 is formed by a recess 27 of the output member 14 in the region around its axis of rotation.
  • the centering collar 25 runs along the circumferential direction of the output element 14, wherein its diameter is adapted to the outer diameter of the end region of the camshaft 6, 7.
  • a receptacle for the camshaft 6, 7 on the camshaft side axial side surface 37 of the output element 14 for centering the camshaft 6, 7 is formed in the radial direction.
  • centering collars, which from the axial Side surface 37 protrude and have, for example, in the circumferential direction interruptions.
  • the centering collar 25 has a form-locking element 28 which cooperates with a formed on the camshaft 6, 7 GegenformQueryelement 29 ( Figure 4).
  • the interlocking element 28 and the counter-form-locking element 29 are designed and arranged such that the camshaft 6, 7 can be inserted into the centering collar 25 only in a specific orientation relative to the output element 14, namely when the interlocking element 28 and the counter-form-locking element 29 axially directly opposite.
  • the form-fitting element 28 is formed integrally with the output element 14. In the illustrated embodiment, this is designed as a bulge of the centering collar 25 radially inward and the counter-form-locking element 29 as a recess on an outer circumferential surface of the camshaft 6, 7.
  • a bulge on the outer circumferential surface of the camshaft 6, 7 and a corresponding bulge of the centering collar 25 may be provided radially outward.
  • the form-locking element 28 is formed as an axial recess in the region of the contact surface of the camshaft 6, 7 on the output element 14, while the symbolsform gleich- element 29 is formed as a depression on a driven element side side surface 36 of the camshaft 6, 7.
  • the reverse case may be present.
  • first pressure medium lines 30 are formed, which extend substantially in the axial direction and open at the axial side surface 36 of the camshaft 6, 7 via first openings 31.
  • the first pressure medium lines 30 communicate via first radial tap holes 35 with a pressure medium transmitter, not shown, which is arranged on the outer circumferential surface of the camshaft 6, 7.
  • second pressure medium lines 32 are formed, which open on the one hand in one of the first pressure chambers 26 a and on the other hand have a second opening 33 which are formed on the axial side surface 37 of the output element 14.
  • first and second openings 31, 33 in the axial direction opposite.
  • the flow area (cross-sectional area) of the first openings 31 corresponds to the flow area of the first pressure medium lines 30.
  • FIG. 3 shows several possibilities for forming the second openings 33 of the second pressure medium lines 32 shown. These can be formed, for example, as grooves 34, in the present case grooves 34 in the circumferential direction of the output element 14, wherein two adjacent first pressure medium lines 30 and two adjacent second pressure medium lines 32 do not communicate with the same groove 34. It is also conceivable to form the second openings 33 with a funnel-shaped enlargement 38, the funnel-shaped enlargement 38 tapering continuously from the axial side surface 37 of the output element 14 to the second pressure medium line 32 until it assumes its cross-sectional area.
  • each second opening 33 is formed larger than the flow area of the first pressure medium lines 30.
  • the extent of each second opening 33 is formed both in the radial direction and in the circumferential direction greater than the korrespondie - rende extension of the corresponding first opening 31. The greater extent in the radial direction ensures that tolerances are compensated. Due to the greater extent in the circumferential direction, orientation errors of the output element 14 to the camshaft 6, 7 in the circumferential direction can be compensated. As a result, greater tolerances can be tolerated in the form-fit element 28 and this does not have to be reworked after the forming process.
  • first openings 31 may also be formed with an increased cross-sectional area.
  • the second pressure medium lines 32 in addition to the radial bore tion, additionally formed as a blind hole axial bore which opens on the one hand in the radial bore and on the other hand as a second opening 33 on the axial side surface 37 of the output member 14.
  • the first openings 31 are formed enlarged as described above ( Figure 4).
  • misalignments of the camshaft 6, 7 to the output member 14 in the circumferential direction for the operation of the device 11 harmless.
  • the extended area of the respective openings 31, 33 guarantees a sufficient overlapping area between each first and second pressure medium line 30, 32.
  • the camshaft 6, 7 further has second tap holes 42, which open into an annular space 43 which is arranged between a camshaft bore 44 of the camshaft 6, 7 and the central screw 22.
  • the annular space 43 opens into the central bore 22a of the output element 14 and communicates via third pressure medium lines 45 with the second pressure chambers 26b.
  • control valve 46 During operation of the internal combustion engine 1, the pressure medium flow to and from the pressure chambers 26 a, 26 b controlled by means of a control valve 46.
  • the control valve 46 has an inlet port P a drain port T and two working ports A, B on.
  • the control valve 46 is supplied with pressure medium from a pressure medium pump 47 via the feed port P, while the drain port T is connected to a pressure medium reservoir 48.
  • the first working port A communicates with the first tap holes 35, the second working port B communicates with the second tap holes 42.
  • the control valve 46 can assume three control positions. In a first control position, the inlet connection P is connected to the second working connection B and the first working connection A is connected to the outlet connection T. Thus, pressure medium passes from the pressure medium pump 47 via the second tap holes 42, the annular space 43 and the third pressure medium lines 45 to the second pressure chambers 26b. At the same time, pressure medium from the first pressure chambers 26a via the second pressure medium lines 32, the openings 31, 33, the first pressure medium lines 30, the first tap holes 35 and the first working port A of the control valve 46 to the pressure medium reservoir 48 derived. Thus, the second pressure chambers 26b expand at the expense of the first pressure chambers 26a, whereby the output member 14 in the illustration of Figure 3 is rotated counterclockwise relative to the drive member 12.
  • a first working connection B second working connection

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

Abstract

L'invention concerne un dispositif (11) servant à effectuer le réglage variable de la périodicité de soupapes d'échange de gaz (9, 10) d'un moteur à combustion interne (1) comportant un élément de commande (12), un élément de sortie (14) et un arbre à cames (6, 7), l'élément de commande (12) pouvant être accouplé à un vilebrequin (2) du moteur à combustion interne (1), l'élément de sortie (14) étant relié à l'arbre à cames (6, 7) sans effectuer de rotation et disposé rotatif par rapport à l'élément de commande (12). L'invention prévoit au moins une première chambre de pression (26a), le rapport de phase entre l'élément de sortie (14) et l'élément de commande (12) pouvant être modifié par introduction d'un moyen de pression dans ladite première chambre de pression (26a) ou par évacuation dudit moyen de ladite chambre, une surface latérale axiale (36) de l'arbre à cames (6, 7) étant contiguë à une surface latérale axiale (37) de l'élément de sortie, l'arbre à cames (6, 7) présentant au moins une première conduite (30) de moyen de pression comportant une première ouverture (31) au niveau de sa surface latérale axiale (36), l'élément de sortie (14) présentant au moins une deuxième conduite (32) de moyen de pression comportant une deuxième ouverture (33) au niveau de sa surface latérale axiale (37) et débouchant dans la première chambre de pression (26a), la première ouverture (31) étant placée en face de la deuxième ouverture (33) sur un axe commun.
PCT/EP2009/057165 2008-07-12 2009-06-10 Dispositif de réglage variable de la périodicité de soupapes d'échange de gaz d'un moteur à combustion interne Ceased WO2010006856A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP09779705A EP2313619A1 (fr) 2008-07-12 2009-06-10 Dispositif de réglage variable de la périodicité de soupapes d'échange de gaz d'un moteur à combustion interne
US13/003,640 US20110120400A1 (en) 2008-07-12 2009-06-10 Device for variably adjusting the valve timing of gas exchange valves of an internal combustion engine
CN200980127280XA CN102089503A (zh) 2008-07-12 2009-06-10 用于对内燃机的换气阀配气相位进行可变调整的装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008032948A DE102008032948A1 (de) 2008-07-12 2008-07-12 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102008032948.7 2008-07-12

Publications (1)

Publication Number Publication Date
WO2010006856A1 true WO2010006856A1 (fr) 2010-01-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/057165 Ceased WO2010006856A1 (fr) 2008-07-12 2009-06-10 Dispositif de réglage variable de la périodicité de soupapes d'échange de gaz d'un moteur à combustion interne

Country Status (5)

Country Link
US (1) US20110120400A1 (fr)
EP (1) EP2313619A1 (fr)
CN (1) CN102089503A (fr)
DE (1) DE102008032948A1 (fr)
WO (1) WO2010006856A1 (fr)

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JP5669999B2 (ja) * 2012-11-12 2015-02-18 三菱電機株式会社 バルブタイミング調整装置及びその組立て方法

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US20110120400A1 (en) 2011-05-26
EP2313619A1 (fr) 2011-04-27
CN102089503A (zh) 2011-06-08

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