EP0902169A1 - Mechanische Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einem Antriebsrad in einer Brennkraftmaschine - Google Patents

Mechanische Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einem Antriebsrad in einer Brennkraftmaschine Download PDF

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Publication number
EP0902169A1
EP0902169A1 EP98203013A EP98203013A EP0902169A1 EP 0902169 A1 EP0902169 A1 EP 0902169A1 EP 98203013 A EP98203013 A EP 98203013A EP 98203013 A EP98203013 A EP 98203013A EP 0902169 A1 EP0902169 A1 EP 0902169A1
Authority
EP
European Patent Office
Prior art keywords
toothed
piston
toothed portion
component
camshaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98203013A
Other languages
English (en)
French (fr)
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EP0902169B1 (de
Inventor
Renzo Tortul
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.)
Carraro SpA
Original Assignee
Carraro SpA
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Filing date
Publication date
Application filed by Carraro SpA filed Critical Carraro SpA
Publication of EP0902169A1 publication Critical patent/EP0902169A1/de
Application granted granted Critical
Publication of EP0902169B1 publication Critical patent/EP0902169B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley

Definitions

  • the present invention relates to a mechanical device for varying the phase between a drive shaft and a camshaft of an internal combustion engine according to the preamble of the main claim.
  • the piston member is stopped in the stop positions by engaging in the toothed portions of the coaxial components in such a manner as to eliminate the play existing between the mutually coupled toothed portions and consequently to limit the noise induced by the relative movement of the coupled toothed portions. That movement is the result of the reversal of the load acting on the camshaft brought about principally by the timing dynamics.
  • the piston member has to assume more advanced positions in the stop positions.
  • the pressure forces between the sides of the mutually contacting toothed portions, which are generated by the engaging action of the piston member may cause the formation of small localised impressions on the sides of the toothed portions of the coaxial components.
  • those impressions may reach depths sufficient to form a step on the sides of the toothed portions which impedes, to the extent of preventing, the sliding of the piston member relative to the coupled coaxial component. If the advance of the piston member is prevented, the play between the toothed portions can no longer be recovered by the movement of the piston member and there is consequently an undesired increase in the noise of the device.
  • the problem underlying the present invention is to provide a mechanical device for varying the phase between a drive shaft and a camshaft of an internal combustion engine, which device has structural and functional characteristics such as to overcome the disadvantages discussed with reference to the mentioned prior art.
  • a mechanical device according to the invention for varying the phase between the drive shaft and a camshaft 3 of an internal combustion engine is generally indicated 1.
  • the device 1 is of the type described in patent application no. PD95A000094, the content of which is incorporated in the present description by reference.
  • the present invention will be described with reference to one of the embodiments referred to in the above-mentioned patent application, it being understood, however, that the invention can also relate in principle to the other embodiments described.
  • the mechanical device 1 comprises a first component constituted by a hollow annular body 5, a second component constituted by a hollow shaft 2 which is rotatably supported in coaxial manner in the body 5, and an annular piston member 4 which is interposed between the body 5 and the shaft 2 and which is likewise coaxial with the body 5.
  • the body 5 is formed by an inner semi-body and an outer semi-body which are indicated 5a and 5b, respectively, and which are fixedly joined to one another by means of a screw and nut coupling.
  • the outer semi-body 5b has a flange 7 formed on it for securing, by means of screws, a toothed wheel (not shown in the drawing) designed to be connected to the drive shaft by means of a toothed belt drive.
  • One end 8a of the body 5 has an inner shoulder 9 and the opposite end 8b has a base 10 welded to the body 5.
  • the base 10 comprises a cover 11 which is connected thereto by a screw and nut coupling.
  • One end 2a of the shaft 2 has a flange 12 which is supported against the shoulder 9, while the opposite end 2b is supported on the base 10 of the body 5.
  • a tie rod 13 connects the shaft 2 axially to the camshaft 3, thus rendering them integral in rotation.
  • the tie rod 13 comprises a shank inserted in the central hole of the shaft 2 and in a central hole of the camshaft, a head accommodated in a cylindrical seat of the shaft 2 and a threaded end 13a connected to a corresponding threaded portion of the central hole of the camshaft 3.
  • the shank of the tie rod 13 has a smaller diameter than that of the holes in which it is inserted, so that an annular duct 14 is defined inside the camshaft 3 and the shaft 2.
  • the piston member 4 comprises, on the outside, a helicoidal toothed portion 15 in engagement with a corresponding inner toothed portion 16 of the inner semi-body 5a, and, on the inside, a toothed portion 17, preferably of the rectilinear type, in engagement with a corresponding outer toothed portion 18 of the shaft 2.
  • the toothed portions 15, 17 are defined between axially opposing end edges 19, 20 of the piston 4 (with reference to a hypothetical axial section through the piston).
  • the piston 4 has a head 21 having a front surface of larger diameter than that of the remaining portion having the helicoidal toothed portion 15.
  • the head 21 constitutes an axially mobile baffle which divides an annular chamber 22, defined inside the mechanical device 1 by the inner semi-body 5a, by the outer semi-body 5b and by the shaft 2, into a first and a second half-chamber facing the base 10 and the end 8a of the body 5, respectively.
  • the volume of the above-mentioned half-chambers is a function of the position of the head 21 in the annular chamber 22.
  • a helical spring 24 is arranged in the above-mentioned first half -chamber and acts on the head 21 of the piston, urging the piston towards the end 2a of the shaft 2.
  • a plurality of radial ducts 25 formed in the shaft 2 bring the first half-chamber into fluid communication with the annular duct 14 which is in turn in fluid communication with a first pressurised fluid hydraulic circuit of the camshaft 3.
  • a further duct 26 formed in the shaft 2 brings the second half-chamber into fluid communication with a duct 27 which is in turn in fluid communication with a second pressurised fluid hydraulic circuit of the camshaft 3.
  • a solenoid valve is controllable from an electronic control unit to pass from a first operating position, in which it brings the first hydraulic circuit into fluid communication with a main pressurised fluid circuit of the engine and at the same time discharges the second hydraulic circuit, to a second operating position in which it discharges the first hydraulic circuit and at the same time brings the second hydraulic circuit into fluid communication with the main circuit.
  • the mechanical device 1 also comprises an auxiliary annular element 30 interposed coaxially between the body 5 and the shaft 2 and having, like the piston 4, an outer helicoidal toothed portion 31 in engagement with the corresponding toothed portion 16 of the inner half-body 5a and an inner rectilinear toothed portion 32 in engagement with the corresponding toothed portion 18 of the shaft 2.
  • the auxiliary annular element 30 is arranged axially between the base 10 and the piston 4, at a predetermined distance from the latter.
  • the mechanical device 1 also comprises a plurality of pins 33 interposed between the auxiliary annular element 30 and the piston 4 and arranged circumferentially with uniform spacing around the shaft 2.
  • the pins 33 are preferably accommodated in seats formed axially in the piston 4.
  • An axial shoulder 34 which limits the axial sliding of the pins 33 towards the end 2a of the shaft 2 is formed in the shaft 2.
  • the pressurised fluid flows into the second half-chamber, causing a sliding of the piston 4 and the auxiliary annular element 30 towards the base 10 counter to the action of the spring 24, and also a relative angular rotation of the components 2, 5.
  • the sliding causes the auxiliary annular element 30 to abut the base 10 in a first stop position ( Figure 1), causing the piston 4 to stop by engagement in the toothed portions 16 and 18, which prevents further relative rotation of the components 2, 5.
  • the pins 33 are axially free to move between the piston 4 and the auxiliary element 30.
  • a gap is provided in the axial profile of the sides of the toothed portions 16 and 18, respectively, of the body 5 and the shaft 2.
  • the above-mentioned gap comprises a first and a second groove 36, 38.
  • the grooves are formed circumferentially on the body 5 and on the shaft 2 in such a manner that they affect each tooth of the toothed portions 16 and 18.
  • the first and the second groove 36, 38 are formed in a position such that they straddle the edge 19 of the piston 4 when the piston is in the first stop position.
  • each groove 36, 38 extends axially for a distance adjacent to the respective toothed portion 15, 17 of the piston and for a further distance beyond the toothed portion 15, 17 in the direction of further travel beyond the first stop position (in the direction towards the base 10).
  • the grooves 36, 38 are defined by surfaces 36a, b and 38a, b which face one another and which extend from the base of the corresponding groove.
  • each surface 36b, 38b that is to say, that adjacent to the toothed portion of the piston in the first stop position, extends from the groove base, diverging from the other surface 36a, 38a.
  • the inclined surfaces 36b, 38b facilitate the fitting of the toothed portions 31, 32 of the auxiliary element 30 in the respective toothed portions 16, 18 during the actuating stroke of the auxiliary element.
  • the above-mentioned gap in the toothed portions also comprises a third groove 40 formed in a position such that it straddles the edge 20 of the piston when the piston is in the second stop position.
  • the third groove 40 may be constituted by the discharge groove provided for the production of the toothed portion of the shaft 2 in the area of the shoulder 34.
  • the third groove 40 also extends, relative to the second stop position of the piston, for a distance adjacent to the toothed portion 17 of the piston and for a further distance beyond that toothed portion 17 in the direction of further travel beyond the second stop position (in the direction towards the shoulder 34).
  • the piston In operation, the piston is locked in each stop position by engagement in the toothed portions 16 and 18, as described above.
  • the pressure forces exerted between the sides of the mutually contacting toothed portions are such that, as the hours of operation increase, they can cause wear on the sides of the toothed portions with the formation of small cavities or impressions, especially along the sides of the toothed portions 16 and 18.
  • the play between the coupled toothed portions tends to increase owing to the wear and the piston 4 is urged to move axially beyond the corresponding end position in order to recover the above-mentioned play.
  • That axial movement is not impeded by any cavities or steps, caused by wear and present on the side of the toothed portions 16, 18, because the corresponding edge 19, 20 of the piston is not in contact with the side of the toothed portions 16, 18 but straddles the corresponding groove 36, 38, 40.
  • the edge 19, 20 is therefore not impeded in its axial movement and the piston 4 can be moved axially, under the action of the pressurised fluid (and of the spring 24 in the second stop position), beyond the corresponding stop position in order to recover the play and to be locked again by engagement in the toothed portions 16 and 18.
  • the gap in the axial profile of the sides of the toothed portions 16 and 18 is in the form of an impression 41 obtained by a reduction in height of the side of the toothed portion, as shown in Figure 5.
  • the axial extent of the gap portion extending adjacent to the toothed portions 15, 17 of the piston is smaller than the axial extent of the toothed portions of the piston, so that the sides of the toothed portions 15, 17 of the piston are always in contact with the respective sides of the coupled toothed portions 16, 18 without ever falling into the grooves 36, 38, 40 or the impressions 41.
  • Figure 6 shows a further variant of the invention which differs from the preceding examples in that the third groove 40 is not provided as a discharge groove in the production of the toothed portion 18 of the shaft 2.
  • the shaft 2 is in this case produced in two portions 2c, 2d of which the portion 2c having the toothed portion 18 is forced onto the flange portion 2d and the production of the toothed portion is carried out before the operation of forcing the portions 2c, 2d one onto the other, the provision of a discharge groove therefore being dispensed with. Consequently the groove 40 should be appropriately formed for the purposes of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
EP19980203013 1997-09-11 1998-09-09 Mechanische Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einem Antriebsrad in einer Brennkraftmaschine Expired - Lifetime EP0902169B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPD970198 1997-09-11
ITPD970198 IT1294653B1 (it) 1997-09-11 1997-09-11 Dispositivo meccanico per variare la fase fra albero motore ed un albero a camme di un motore a combustione interna

Publications (2)

Publication Number Publication Date
EP0902169A1 true EP0902169A1 (de) 1999-03-17
EP0902169B1 EP0902169B1 (de) 2002-06-26

Family

ID=11391901

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980203013 Expired - Lifetime EP0902169B1 (de) 1997-09-11 1998-09-09 Mechanische Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einem Antriebsrad in einer Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP0902169B1 (de)
DE (1) DE69806211T2 (de)
IT (1) IT1294653B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107923273A (zh) * 2015-09-10 2018-04-17 舍弗勒技术股份两合公司 凸轮轴调节器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007023617B4 (de) * 2007-05-18 2020-06-04 Herbert Naumann Nockenwellenversteller

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0702132A2 (de) * 1994-09-16 1996-03-20 Nippondenso Co., Ltd. Drehmoment übertragende Vorrichtung
EP0711238A1 (de) 1994-06-08 1996-05-15 LOSI, Bruno VERFAHREN UND VORRICHTUNG ZUr TRENNUNG EINER ABFALLSCHICHT VON KLEBENDEN ETIKETTEN
EP0742350A2 (de) * 1995-05-11 1996-11-13 Carraro S.P.A. Eine mechanische Vorrichtung zur Veränderung der Phasenbeziehung zwischen der Antriebswelle und einer Nockenwelle einer Brennkraftmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0711238A1 (de) 1994-06-08 1996-05-15 LOSI, Bruno VERFAHREN UND VORRICHTUNG ZUr TRENNUNG EINER ABFALLSCHICHT VON KLEBENDEN ETIKETTEN
EP0702132A2 (de) * 1994-09-16 1996-03-20 Nippondenso Co., Ltd. Drehmoment übertragende Vorrichtung
EP0742350A2 (de) * 1995-05-11 1996-11-13 Carraro S.P.A. Eine mechanische Vorrichtung zur Veränderung der Phasenbeziehung zwischen der Antriebswelle und einer Nockenwelle einer Brennkraftmaschine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107923273A (zh) * 2015-09-10 2018-04-17 舍弗勒技术股份两合公司 凸轮轴调节器
US20180298790A1 (en) * 2015-09-10 2018-10-18 Schaeffler Technologies AG & Co. KG Camshaft adjuster
US10385740B2 (en) 2015-09-10 2019-08-20 Schaeffler Technologies AG & Co. KG Camshaft adjuster
CN107923273B (zh) * 2015-09-10 2020-06-02 舍弗勒技术股份两合公司 凸轮轴调节器

Also Published As

Publication number Publication date
DE69806211D1 (de) 2002-08-01
ITPD970198A1 (it) 1999-03-11
EP0902169B1 (de) 2002-06-26
IT1294653B1 (it) 1999-04-12
DE69806211T2 (de) 2003-02-27

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