EP2536925B1 - Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne - Google Patents

Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne Download PDF

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Publication number
EP2536925B1
EP2536925B1 EP11701237.7A EP11701237A EP2536925B1 EP 2536925 B1 EP2536925 B1 EP 2536925B1 EP 11701237 A EP11701237 A EP 11701237A EP 2536925 B1 EP2536925 B1 EP 2536925B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
fastening element
central screw
housing
adjusting device
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.)
Not-in-force
Application number
EP11701237.7A
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German (de)
English (en)
Other versions
EP2536925A1 (fr
Inventor
Mathias BÖGERSHAUSEN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2536925A1 publication Critical patent/EP2536925A1/fr
Application granted granted Critical
Publication of EP2536925B1 publication Critical patent/EP2536925B1/fr
Not-in-force 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
    • 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 a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine with a hydraulic phase adjusting device, a camshaft, a volume accumulator, a separately formed to the camshaft fastener and a central screw, the central screw passes through the phase adjusting device and wherein one end of the central screw on an axial Side surface of the phase adjusting device is present and at the other end a first thread is formed.
  • phase adjusting device In modern internal combustion engines devices for variable adjustment of the timing of gas exchange valves are used to adjust the phase relation between the crankshaft and the camshaft in a defined angular range, between a maximum early and a maximum late position variable.
  • the device is integrated in a drive train via which torque is transmitted from the crankshaft to the camshaft.
  • This drive train can be realized for example as a belt, chain or gear drive.
  • the device has, in addition to the camshaft on a phase adjusting device and a central screw, by means of which the phase adjusting device is rotatably connected to the camshaft.
  • the phase adjusting device can be designed, for example, as a vane-type pivoting motor with a plurality of pressure chambers acting against one another.
  • the phase relation of the impeller relative to the cellular wheel and thus the camshaft relative to the crankshaft can be variably adjusted.
  • the pressure medium flow to and from the pressure chambers is usually controlled by means of a hydraulic directional proportional valve, which may be received, for example, within the central screw.
  • Such a device is for example from the DE 10 2005 060 111 A1 known.
  • the central screw is screwed to a solid camshaft to realize the rotationally fixed connection between the phase-adjusting device and the camshaft.
  • the phasing means is mounted on a built camshaft consisting of a tube and cam mounted thereon.
  • the phase adjusting device by means of a welded connection rotatably mounted on the camshaft.
  • Another device is from the DE 102 28 354 A1 known.
  • a cavity is provided within the solid camshaft, which serves as a volume storage.
  • the volume accumulator fills with pressure medium. If the pressure medium requirement of the phase adjusting device rises above the volume flow provided by the pressure medium pump, the volume memory supports the phase adjusting device.
  • the DE 10 2008 029 692 A1 shows a built camshaft with a vane positioner. This creategelzellenversteller is by means of a screw axially braced against an abutment sleeve of the camshaft, so that the rotor is fixed against rotation with respect to the camshaft.
  • the WO 2008/140897 A1 shows a camshaft adjuster with a camshaft, wherein within the camshaft, a spring-loaded piston is arranged. The piston can be moved against the spring force by the supply of hydraulic fluid.
  • the present invention has for its object to provide a device with high response and low production cost.
  • the interior of the camshaft has a cavity in which the fastener is received stationary, wherein on the fastener, a second thread is formed, which cooperates with the first thread of the central screw such that a rotationally fixed connection between the Device and the camshaft is produced and wherein in the cavity a volume accumulator is arranged with a housing, wherein an axial end of the housing rests against a contact surface of the fastening element.
  • the device has a hydraulic phase adjusting device, a camshaft, a central screw and a first fastening element.
  • the phase adjusting device is in drive connection with a crankshaft and is rotatably connected by means of the central screw with the camshaft.
  • the central screw passes through the phase adjusting device wherein one end of the central screw, for example, a collar, rests against an axial side surface of the phase adjusting device and at the other end a first thread, usually an external thread is formed.
  • the phase adjusting device may be a phase of the camshaft be set variably relative to the crankshaft.
  • the camshaft has a cavity in which the separately manufactured to the camshaft fastener stationary, that is immovable in the axial direction and in the circumferential direction at normal load, is added.
  • the fastening element can be screwed, for example, with the lateral surface of the cavity. Also conceivable is a frictional connection.
  • the fastening element has a second thread, usually an internal thread into which the central screw is screwed, so that the phase adjusting device is non-rotatably connected to the camshaft.
  • the device has a volume accumulator which is arranged in the camshaft. The volume accumulator is filled with pressure medium in phases in which sufficient pressure medium is available for operating the phase adjusting device.
  • the volume memory has a housing in which the pressure medium can be stored.
  • a displaceable, spring-loaded piston, a flexible membrane or a gas-filled bubble can be arranged, which serve as energy storage. It is provided that an axial end of the housing bears against a contact surface, as a rule an axial side surface, of the fastening element.
  • the housing may be connected to the fastening element.
  • the fastening element thus serves, on the one hand, for producing the non-rotatable connection between the phase-adjusting device and the camshaft by means of the central screw, wherein this connection method can also be used with relatively thin-walled, built-in camshafts due to the use of the fastening element. Furthermore, the fastening element serves for the axial positional fixing of the housing of the volume accumulator.
  • the fastening element is first positioned and fixed in the cavity of the camshaft. Subsequently, the phase adjusting device by means of the central screw rotatably connected to the camshaft and introduced the volume storage in the camshaft of the phase adjusting device remote end. Subsequently, will this end of the camshaft is closed with a second fastening element, wherein the second fastening element urges the volume accumulator against the first fastening element, so that the volume accumulator is fixed in the axial direction.
  • the contact surface in the direction of the housing conical.
  • the housing of the volume accumulator undergoes a centering during assembly of the second fastening element, so that the housing is automatically aligned coaxially with the axis of rotation of the camshaft.
  • a conical contact surface is advantageously also provided on the second fastening element. The centering of the housing in the cavity of the camshaft creates an annular gap between the housing and the lateral surface of the cavity, which can be used to supply lubricant to camshaft bearing points.
  • the first fastening element or the central screw has a pressure medium channel extending in the axial direction, which opens into the cavity, for example the annular gap, on the side of the fastening element facing away from the phase adjusting device.
  • the pressure medium channel can be formed for example as a bore within the central screw or on an outer circumferential surface of the fastening element.
  • the pressure medium channel communicates with the volume accumulator or with a camshaft bearing point.
  • the fastener assumes not only the functionalities of attaching the phase adjusting device with the camshaft and the volume accumulator with the camshaft, but realized in a simple, cost-neutral manner also parts of the pressure medium supply within the device and adjacent assemblies. This considerably reduces the number of components required and the complexity of the device.
  • FIG. 1 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 Auslassgas scaffoldventile 10.
  • it may be provided only one of the camshafts 6, 7 with a device 11, or provide only a camshaft 6, 7, which with a Device 11 is provided.
  • FIG. 2 shows a first embodiment of a device 11 according to the invention in longitudinal or in cross section.
  • the device 11 has a phase adjusting device 12, a camshaft 6, 7, a central screw 13 and a first fastening element 14.
  • the phase adjusting device 12 is designed as a hydraulic actuator, which is offset by means of a Glasstoff- or gear drive 5 of the crankshaft 2 in rotation and rotationally fixed to the camshaft 6, 7 is connected.
  • pressure medium supply to a group of pressure chambers, not shown, of the hydraulic actuator of the phase adjusting device 12 with simultaneous pressure medium discharge from a second Group of pressure chambers, also not shown the phase angle of the camshaft 6, 7 can be variably adjusted relative to the crankshaft 2 in a defined angular interval.
  • Such phase adjusting devices 12 are known in the art and, for example, in the DE 42 18 082 A1 or the DE 10 2005 060 111 A1 disclosed.
  • the phase adjusting device 12 is arranged at one axial end of the camshaft 6, 7 and is located in the axial direction on an axial stop formed on the camshaft 6, 7.
  • the central screw 13 By means of the central screw 13, the phase adjusting device 12 rotatably connected to the camshaft 6, 7.
  • the central screw 13 passes through the phase adjusting device 12, wherein one end of the central screw 13 is formed with a radially extending collar. The collar abuts on one of the camshaft 6, 7 facing away from side surface of the phase adjusting device 12.
  • a first thread 15 is formed.
  • the camshaft 6, 7 is formed as a hollow shaft and has a cavity 16 which extends along the entire camshaft 6, 7.
  • the first fastener 14 is disposed and fixed, i. in the axial and radial directions immovably fixed to the camshaft 6, 7. In the illustrated embodiment, this is realized by means of a press fit between an outer circumferential surface of the first fastening element 14 and a lateral surface 16 a of the cavity 16.
  • the first fastening element 14 has, in a central through-bore, a second thread 17 into which the first thread 15 of the central screw 13 engages, so that the phase-adjusting device 12 is connected in a rotationally fixed manner to the camshaft 6, 7.
  • the volume accumulator 18 has a housing 19, a separating element 20, which is designed as a piston 20, and a spring element 21.
  • the housing 19 is substantially hollow cylindrical, each having an opening 22 formed on each axial end face, wherein the housing 19 at its axial ends 23 extends radially inwardly.
  • the outer diameter of the housing 19 is formed smaller than the diameter of the cavity 16.
  • the piston 20 is formed as a thin-walled, cup-shaped sheet metal component and mounted axially displaceable within the housing 19. In this case, the piston 20 separates the interior of the housing 19 in a storage space 24 and a complementary space 25th
  • the spring element 21 is arranged in the complementary space 25 and is supported on the one hand on the side facing away from the reservoir 24 of the piston 20 and on the other hand on the radially inwardly extending portion of the housing 19 from.
  • the axial ends 23 of the housing 19 in each case abut against a conical contact surface 26 (FIG. FIGS. 2 and 3 ).
  • the first conical contact surface 26 is formed on the side facing away from the phase adjusting device 12 side of the first fastening element 14 as an inner cone.
  • the second contact surface 26 is formed on a second fastening element 27 which is fixedly connected to the camshaft 6, 7 and arranged at the end of the camshaft 6, 7 facing away from the phase adjusting device 12.
  • the second contact surface 26 is formed as an outer cone.
  • the volume accumulator 18 is fixed by the abutment of the housing 19 on the conical contact surfaces 26 in the cavity 16 in the axial direction and centered to the longitudinal axis of the camshaft 6, 7.
  • the annular gap 28 extends from the first fastening element 14 along the entire camshaft 6, 7 and covers in particular a plurality of camshaft bearing points 29. In the area of the camshaft bearing points 29 are each a plurality of holes 30 formed on the camshaft 6, 7, on the one hand with the annular gap 28 and on the other hand communicate with the respective camshaft bearing point 29.
  • the annular gap 28 is sealed by the second fastening element 27 in the axial direction.
  • the first fastening element 14 has on its outer lateral surface first pressure medium channels 31 in the form of grooves extending in the axial direction (FIG. FIG. 4 ), so that the annular gap 28 communicates with a receiving region 13a of the cavity 16, in which the central screw 13 is arranged.
  • pressure medium which is conveyed by a pressure medium pump, not shown, via bores 30, which are formed in the region of the first camshaft bearing point 29a on the camshaft 6, 7, the receiving portion 13a.
  • the pressure medium reaches the camshaft bearing points 29 via the first pressure medium channels 31, the annular gap 28 and the bores 30.
  • the second fastening element 27 prevents the escape of pressure medium at the side of the camshaft 6, 7 facing away from the phase adjusting device 12.
  • the pressure medium passes through screw holes 32 into the interior of the hollow central screw 13.
  • the pressure medium passes on the one hand via a arranged in the interior of the central screw 13, not shown, hydraulic directional proportional valve to the phase adjusting device 12.
  • proportional valves are for example from DE 10 2005 052 481 A1 known.
  • excess pressure medium passes through a second pressure medium channel 33 formed in the central screw 13 to the reservoir side opening 22 of the housing 19 of the volume memory 18 and is supplied to the reservoir space 24.
  • the piston 20 is displaced against the force of the spring element 21, whereby the volume of the storage space 24 at the expense of the volume of the Complementary space 25 increases.
  • phase adjusting device 12 If the pressure medium volume required by the phase adjusting device 12 exceeds the pressure medium volume conveyed by the pressure medium pump, the piston 20 is displaced in the opposite direction due to the force exerted by the spring element 21 and thus the pressure medium stored in the volume memory 18 via the second pressure medium channel 33 Phase adjusting device 12 is supplied.
  • the second fastening element 27 has an axially extending, central passage opening 34, via which the complementary space 25 communicates with the interior of the internal combustion engine 1. Thus, air and pressure medium escape from the complementary space 25.

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

Claims (7)

  1. Dispositif (11) de réglage variable des temps de commande de soupapes d'échange de gaz (9, 10) d'un moteur à combustion interne (1) comprenant
    - un déphaseur hydraulique (12), un arbre à cames (6, 7), un premier élément de fixation (14) réalisé de manière séparée de l'arbre à cames (6, 7) et une vis centrale (13),
    - la vis centrale (13) venant en prise à travers le déphaseur (12) et
    - une extrémité de la vis centrale (13) s'appliquant contre une surface latérale axiale du déphaseur (12) et un premier filetage (15) étant réalisé sur l'autre extrémité,
    - l'intérieur de l'arbre à cames (6, 7) comprenant un espace creux (16) dans lequel le premier élément de fixation (14) est reçu de manière fixe,
    - un deuxième filetage (17) étant réalisé sur le premier élément de fixation (14), lequel deuxième filetage coopère avec le premier filetage (15) de la vis centrale (13) de telle sorte qu'une liaison solidaire en rotation soit produite entre le dispositif (11) et l'arbre à cames (6, 7), caractérisé en ce qu'un accumulateur volumétrique (18) comprenant un boîtier (19) est disposé dans l'espace creux (16), une extrémité axiale (23) du boîtier (19) s'appliquant contre une surface d'appui (26) du premier élément de fixation (14).
  2. Dispositif (11) selon la revendication 1, caractérisé en ce que la surface d'appui (26) est réalisée de manière conique en direction du boîtier (19).
  3. Dispositif (11) selon la revendication 1, caractérisé en ce que le premier élément de fixation (14) ou la vis centrale (13) comprend un canal de fluide sous pression (31, 33) s'étendant dans la direction axiale, lequel débouche dans l'espace creux (16) du côté du premier élément de fixation (14) opposé au déphaseur (12).
  4. Dispositif (11) selon la revendication 3, caractérisé en ce que le canal de fluide sous pression (31, 33) est réalisé sous forme d' alésage (33) à l'intérieur de la vis centrale (13).
  5. Dispositif (11) selon la revendication 3, caractérisé en ce que le canal de fluide sous pression (31, 33) est réalisé sur une surface d'enveloppe extérieure du premier élément de fixation (14).
  6. Dispositif (11) selon la revendication 3, caractérisé en ce que le canal de fluide sous pression (31, 33) est en communication avec l'accumulateur volumétrique (16).
  7. Dispositif (11) selon la revendication 3, caractérisé en ce que le canal de fluide sous pression (31, 33) est en communication avec un point d'appui d'arbre à cames (29).
EP11701237.7A 2010-02-15 2011-01-20 Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne Not-in-force EP2536925B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010008002A DE102010008002A1 (de) 2010-02-15 2010-02-15 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2011/050745 WO2011098330A1 (fr) 2010-02-15 2011-01-20 Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2536925A1 EP2536925A1 (fr) 2012-12-26
EP2536925B1 true EP2536925B1 (fr) 2014-12-10

Family

ID=43807094

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11701237.7A Not-in-force EP2536925B1 (fr) 2010-02-15 2011-01-20 Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne

Country Status (6)

Country Link
US (1) US8662041B2 (fr)
EP (1) EP2536925B1 (fr)
CN (1) CN102762822B (fr)
BR (1) BR112012020001A2 (fr)
DE (1) DE102010008002A1 (fr)
WO (1) WO2011098330A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009042202A1 (de) * 2009-09-18 2011-04-14 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102011082591A1 (de) 2011-09-13 2013-03-14 Schaeffler Technologies AG & Co. KG Axiallagerung bei Doppelnockenwellen, Nockenwellenverstellvorrichtung und Verbrennungskraftmaschine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4218082C5 (de) * 1992-06-01 2006-06-29 Schaeffler Kg Vorrichtung zur kontinuierlichen Winkelverstellung zwischen zwei in Antriebsverbindung stehenden Wellen
DE10125498A1 (de) 2001-05-23 2002-12-19 Salzgitter Antriebstechnik Gmb Nockenwelle und Verfahren zur Herstellung einer Nockenwelle
DE10134320A1 (de) * 2001-07-14 2003-01-23 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE10228354B4 (de) 2002-06-25 2017-06-22 Daimler Ag Vorrichtung zur Druckversorgung einer Nockenwellen-Verstelleinrichtung
DE10362023A1 (de) 2003-12-24 2005-07-28 Ina-Schaeffler Kg Vorrichtung zur hydraulischen Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102005052481A1 (de) * 2005-11-03 2007-05-24 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102005060111A1 (de) 2005-12-16 2007-07-05 Schaeffler Kg Nockenwellenverstellerzuleitung
DE102006033425A1 (de) 2006-07-19 2008-02-21 Schaeffler Kg Gruppe mehrerer Nockenwellen mit Nockenwellenverstellern
WO2008140897A1 (fr) 2007-05-14 2008-11-20 Borgwarner Inc. Accumulateur monté sur came
DE102008029692B4 (de) 2008-06-24 2016-02-11 Hilite Germany Gmbh Gebaute Nockenwelle mit einem Flügelzellenversteller und Herstellungsverfahren
DE102008032412A1 (de) 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller

Also Published As

Publication number Publication date
US8662041B2 (en) 2014-03-04
US20120304947A1 (en) 2012-12-06
CN102762822A (zh) 2012-10-31
WO2011098330A1 (fr) 2011-08-18
EP2536925A1 (fr) 2012-12-26
CN102762822B (zh) 2014-06-11
DE102010008002A1 (de) 2011-08-18
BR112012020001A2 (pt) 2019-09-24

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