EP2322769B1 - Entraînement d'arbre à cames avec arbre à cames et insert d'arbre à cames - Google Patents

Entraînement d'arbre à cames avec arbre à cames et insert d'arbre à cames Download PDF

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Publication number
EP2322769B1
EP2322769B1 EP10189470.7A EP10189470A EP2322769B1 EP 2322769 B1 EP2322769 B1 EP 2322769B1 EP 10189470 A EP10189470 A EP 10189470A EP 2322769 B1 EP2322769 B1 EP 2322769B1
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EP
European Patent Office
Prior art keywords
camshaft
pressure
pressure accumulator
rotor
insert
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
EP10189470.7A
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German (de)
English (en)
Other versions
EP2322769A1 (fr
Inventor
Marc Hohmann
Dietmar Schulze
Andreas Knecht
André Selke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
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Hilite Germany GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP2322769A1 publication Critical patent/EP2322769A1/fr
Application granted granted Critical
Publication of EP2322769B1 publication Critical patent/EP2322769B1/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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a camshaft drive with a, camshaft with a camshaft insert which is rotatably connected to a rotor of a Schwenkmotorverstellers according to claim 1, as it is known from WO 2008/140 897 is known.
  • An electro-hydraulic valve for a Schwenkmotorversteller a camshaft is already known. This valve is inserted into a valve housing in which channels are provided with working ports A, B, which lead to the pressure chambers of the Schwenkmotorversteller. A plunger of the electro-hydraulic valve abuts a piston rod which is integrally connected to a piston. This piston is displaceable against a spring force within a pressure chamber in the valve housing.
  • the DE 10 2004 038 252 A1 shows a Schwenkmotorversteller with a so-called central valve.
  • the valve for actuating the Schwenkmotorverstellers is arranged radially inside the rotor on the rotor hub.
  • the object of the invention is to provide a Schwenkmotorversteller, in which space-saving a pressure accumulator is provided.
  • a pressure accumulator is integrated in a camshaft insert, which carries the rotor according to claim 1.
  • the camshaft insert and a threaded pin for rotationally fixed attachment of the rotor to the camshaft are made in one piece.
  • the camshaft insert can be made very thick-walled, whereby a longitudinal bore introduced into this can be.
  • This longitudinal bore can, in particular, guide the hydraulic fluid coming from the accumulator-in particular engine oil-to the central valve.
  • the central valve can be designed such that is supplied from the longitudinal bore via a small transverse bore Hyraulikfluid an annular groove in the valve piston, which is limited by annular webs. At these ring webs are the edges. If these annular webs have the same outer diameter, then the central valve is pressure-balanced.
  • a check valve may be provided that reduces leakage losses at the rotary feedthrough for the fluid, in particular engine oil.
  • the camshaft drive comprises a camshaft 5, which is mounted on both sides in non-illustrated camshaft bearings.
  • This camshaft 5 has cam, not shown, with which gas exchange valves of an internal combustion engine can be actuated.
  • the camshaft 5 is designed as a built-up camshaft.
  • the main body of the camshaft 5 is a hollow tube, are shrunk or pressed onto the cam.
  • a fit 7 is rotated in the interior of the hollow shaft, which receives an inner pin 8 of a camshaft insert 9.
  • the camshaft insert 9 is formed as a rotor carrier 10, which has a larger diameter than the inner pin 8.
  • the camshaft insert 9 has a threaded pin 11 whose thread diameter is smaller than the diameter of the rotor carrier 10.
  • a nut 12 is screwed, which rotatably clamped the rotor 6 against a shoulder 13 of the rotor carrier 10.
  • a radially projecting from a rotor hub 14 radially inwardly annular shoulder 15 is clamped axially between the nut 12 and the shoulder 13 of the camshaft insert 9.
  • This paragraph 13 delimits the rotor carrier 10 from the threaded pin 11.
  • the rotor hub 14 is placed on the rear portion of the rotor carrier 10.
  • the front region of the rotor carrier 10 protrudes through a bearing eye 16 of a cylinder head part 17, which receives this rotor carrier 10 in stock.
  • an annular groove 18 is incorporated in the cylinder head part 17, which is supplied by an oil pump, not shown engine oil, so that this annular groove 18 forms a pressure port P.
  • a band-shaped Check valve 50 is used, which prevents the engine oil can flow back into the oil pump due to camshaft alternating torques.
  • the pressurized engine oil is fed into a transverse bore 19 of the rotor carrier 10. From this continuous transverse bore 19, the flow of engine oil is divided on a pressure accumulator 20 and a longitudinal bore 21 leading to the valve in the rotor arm 10. This longitudinal bore 21 is closed at its end facing the engine compartment with a pressed ball 22.
  • the pressure accumulator 20 is aligned in a front region of the camshaft insert 9 coaxially with its central axis 23.
  • a pressure chamber 24 of the pressure accumulator 20 is formed by a blind hole 25, which is worked from the front into the camshaft insert 9.
  • a hydraulic piston 26 is guided axially displaceable, which is connected immovably with a direction away from the pressure chamber 24 direction piston rod 27.
  • This piston rod 27 protrudes with radial clearance through a ring 28 which is pressed firmly into the inner pin 8 in the entry region of the blind hole 25.
  • one end of a helical compression spring 29 is supported, the other end is supported on the hydraulic piston 26.
  • a hydraulic part 2 is arranged in the camshaft insert 9.
  • a partition wall 30 lies between the pressure accumulator 20 and the hydraulic part 2.
  • An end of a further helical compression spring 31 is supported on this partition wall 30, the other end of which is supported on a bottom 32 of a valve piston 33.
  • this other end projects into a guide recess 34 of the valve piston 33 up to the recess bottom, in which the bottom 32 lies.
  • the valve piston 33 is axially guided in a central blind hole 35.
  • the blind hole 35 is opened in the region of the threaded pin 11. In this case, the inlet region of this blind hole 35 forms the first tank outlet T1.
  • the valve piston 33 has a wide annular groove 36, so that on both sides of the annular groove 36 annular webs 37, 38 remain, each of which forms on both sides of the discharge edges 39, 40, 41, 42.
  • the mutually facing outlet edges 40, 41 serve the inlet to a working port A and B.
  • the mutually remote flow edges 39, 42 form the outlet to a tank drain T1 or T2.
  • the annular groove 36 can be supplied via a transverse bore 43 engine oil.
  • This transverse bore 43 is provided in the wall 44 of the rotor carrier 10 and thereby forms the storage port S.
  • the transverse bore 43 intersects the longitudinal bore 21.
  • the storage port S is connected via the foremost transverse bore 19 both to the pressure chamber 24 and to the pressure port P.
  • valve piston 33 On the valve piston 33 is on the outside -. coming from the inlet area - a dashed line shown plunger 47 of an electromagnetic linear actuator, which is otherwise not shown in detail.
  • the engine oil coming from the annular groove 36, is conducted via the working port A into the pressure chambers of the swivel motor adjuster 1 associated with one direction of rotation.
  • the engine oil is transferred from the pressure chambers assigned to the opposite direction of rotation the working port B to the first tank discharge T1 passed.
  • the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the one direction of rotation.
  • the plunger 47 is retracted to the maximum, the engine oil, coming from the annular groove 36, is conducted via the working port B into the pressure chambers of the swivel motor adjuster 1 assigned to the other rotational direction.
  • the engine oil from the opposite direction of rotation to this opposite direction of rotation pressure chambers is passed through the working port A to the second tank outlet T2.
  • the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the other direction of rotation.
  • valve piston 33 and the blind hole 35 are dimensioned in relation to the axial distances between the working ports A, B and the trailing edges 39 to 42 that given in a central position of the valve piston 33 pressure on the two rotational directions associated pressure chambers becomes. In the central position, therefore, the hydraulic pressure is controlled with a slight overlap.
  • the hydraulic piston 26 in the pressure accumulator 20 does not necessarily have a piston rod 27. If the guide length of the hydraulic piston 26 is sufficient, the entire diameter in the ring 28 can also be used for a large volume flow.
  • the longitudinal bore and the transverse bores in the camshaft insert may be distributed circumferentially such that the imbalance is only slight.
  • the blind hole 35 can also be closed, so that in both directions the discharge takes place against the tank only via the one tank outlet T2, which thus forms the single tank outlet.
  • the plunger protrudes through a sealed opening in the camshaft insert 9.
  • the hydraulic piston 26 can also be performed directly in the camshaft 5, if this is carried out according to the drawing with a hollow tube as the main body.
  • the ring 28 may also be axially supported directly in the camshaft 5.
  • the band-shaped check valve 50 may also be inserted into an annular groove in the camshaft insert 9. This can prevent leakage losses at the transfer point from bearing lug 16 to camshaft insert 9.
  • a possible embodiment of a band-shaped check valve is in the US 7,600,531 B2 shown.

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

Claims (8)

  1. Entraînement d'arbre à cames avec un arbre à cames doté d'un insert d'arbre à cames (9) relié solidairement en rotation à un rotor (6) d'un élément de réglage de moteur oscillant (1), un accumulateur de pression (20) pouvant être chargé à l'aide d'une force de ressort étant disposé à l'intérieur de l'entraînement d'arbre à cames ;
    une partie hydraulique (2) d'une soupape (3 et/ou 55) étant disposée à l'intérieur du rotor (6) dans le plan radial ;
    la partie hydraulique (2) étant disposée en alignement par rapport à l'accumulateur de pression (20 et/ou 58) ;
    l'accumulateur de pression (20) comportant une chambre de pression (24) alimentée en fluide par un raccord de pression (P) ;
    l'accumulateur de pression (20) étant délimité par un piston hydraulique (26) pouvant être coulissé dans le plan axial s'appuyant contre une partie fixe de l'arbre à cames dans le plan axial (bague 28), sur son côté orienté vers la chambre de pression (24), à l'aide d'un ressort de pression à vis (29) ;
    le fluide étant amené à l'accumulateur de pression (20) par un canal (19) ;
    caractérisé en ce que :
    l'accumulateur de pression (20) est disposé à l'intérieur de l'insert d'arbre à cames (9) ;
    le fluide sortant d'une rainure annulaire (18) prévue dans une partie de culasse (17) étant amené au canal (19) ;
    un raccord de réservoir (T2) reposant dans le plan axial entre le raccord de pression (P) conduisant dans la chambre de pression (24) de l'accumulateur de pression (20) et les raccords de travail (A, B).
  2. Entraînement d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'accumulateur de pression (20) est séparé de la partie hydraulique (2) avant à l'aide d'une paroi (30) contre laquelle une première extrémité d'un ressort de pression à vis (31) s'appuie au moins de façon indirecte, la deuxième extrémité s'appuyant contre un piston de soupape (33).
  3. Entraînement d'arbre à cames selon la revendication 3, caractérisé en ce qu'un maillon de réglage électromagnétique s'appuie sur un côté du piston de soupape (33) sur l'autre côté duquel la deuxième extrémité du ressort de pression à vis (31) s'appuie, le fluide étant amené au piston de soupape (33) par le biais d'un raccord d'accumulateur (S) provenant de l'accumulateur de pression (20), ledit fluide se divisant alternativement en deux raccords de travail (A, B) via deux arêtes d'évacuation (40, 41) par le biais d'un élément de commande d'intersection conduisant dans des chambres de pression opposées des deux côtés d'au moins une pale (49) du rotor (6).
  4. Entraînement d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'insert d'arbre à cames (9) comporte un tenon intérieur (8) introduit par compression dans l'arbre à cames creux (5).
  5. Entraînement d'arbre à cames selon la revendication 5, caractérisé en ce que l'arbre à cames (5) est un arbre à cames (5) monté.
  6. Entraînement d'arbre à cames selon la revendication 6, caractérisé en ce que l'insert d'arbre à cames (9) et un tenon fileté (11) sont réalisés d'un seul tenant pour fixer solidairement en rotation le rotor (6) à l'arbre à cames (5).
  7. Entraînement d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'insert d'arbre à cames (9) comporte un tenon fileté (11) sur lequel un écrou est vissé, ledit écrou serrant solidairement en rotation le rotor (6) contre un épaulement (13) de l'insert d'arbre à cames (9).
  8. Entraînement d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une soupape de retenue (63) est prévue dans le flux hydraulique entre une pompe à huile (60) et l'accumulateur de pression (20).
EP10189470.7A 2009-11-13 2010-10-29 Entraînement d'arbre à cames avec arbre à cames et insert d'arbre à cames Not-in-force EP2322769B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009052841A DE102009052841A1 (de) 2009-11-13 2009-11-13 Nockenwelleneinsatz

Publications (2)

Publication Number Publication Date
EP2322769A1 EP2322769A1 (fr) 2011-05-18
EP2322769B1 true EP2322769B1 (fr) 2013-07-24

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Family Applications (1)

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EP10189470.7A Not-in-force EP2322769B1 (fr) 2009-11-13 2010-10-29 Entraînement d'arbre à cames avec arbre à cames et insert d'arbre à cames

Country Status (4)

Country Link
US (1) US20110114047A1 (fr)
EP (1) EP2322769B1 (fr)
CN (1) CN102061953B (fr)
DE (1) DE102009052841A1 (fr)

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US20110114047A1 (en) 2011-05-19
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EP2322769A1 (fr) 2011-05-18
CN102061953A (zh) 2011-05-18

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