EP0600381A1 - Hydraulische Antriebsvorrichtung, insbesondere für Ventilsteuerung in einer Brennkraftmaschine - Google Patents

Hydraulische Antriebsvorrichtung, insbesondere für Ventilsteuerung in einer Brennkraftmaschine Download PDF

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Publication number
EP0600381A1
EP0600381A1 EP93119034A EP93119034A EP0600381A1 EP 0600381 A1 EP0600381 A1 EP 0600381A1 EP 93119034 A EP93119034 A EP 93119034A EP 93119034 A EP93119034 A EP 93119034A EP 0600381 A1 EP0600381 A1 EP 0600381A1
Authority
EP
European Patent Office
Prior art keywords
chamber
valve
cavity
unit according
outlet opening
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
EP93119034A
Other languages
English (en)
French (fr)
Other versions
EP0600381B1 (de
Inventor
Francesco Cuniberti
Giancarlo Dellora
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.)
Iveco SpA
Original Assignee
Iveco Fiat SpA
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Filing date
Publication date
Application filed by Iveco Fiat SpA filed Critical Iveco Fiat SpA
Publication of EP0600381A1 publication Critical patent/EP0600381A1/de
Application granted granted Critical
Publication of EP0600381B1 publication Critical patent/EP0600381B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length

Definitions

  • the present invention relates to a hydraulic actuating unit; advantageously, said unit can be used in a valve control assembly for an internal-combustion engine, in particular for the actuation of an auxiliary decompression valve.
  • hydroaulic tappets which essentially comprise two members which are telescopically interconnected and which define a chamber connected with a supply of pressurised operating fluid through a non-return valve; the operating fluid, which is substantially incompressible, transmits the actuating forces from one member to the other. Any possible loosening between the two members, caused by an increase in play, is automatically compensated for by the admission of fresh fluid into said chamber through the non-return valve.
  • the aforementioned devices can transmit actuating forces between a driving member, for example a rocker arm of a valve control assembly, and a driven member for example, a valve stem, thus taking up the relevant play in the manner described above.
  • a driving member for example a rocker arm of a valve control assembly
  • a driven member for example, a valve stem
  • These devices essentially behave like rigid elements and do not enable the transmission of actuating forces between the driving member and the driven member to be eliminated, in the event of this function being required; therefore, the known devices can be effectively used, for example, for controlling the inlet and exhaust valves of an engine, which have to be actuated in all operating conditions, but not for controlling an auxiliary decompression valve which has to be actuated only in particular operating conditions.
  • the object of the present invention is to devise a hydraulic actuating unit which does not have the drawbacks associated with the above-described known devices.
  • the unit comprises a rocker arm having one end attached to the second member, the other end attached to the valve and a central portion adapted to co-operate with a respective cam of a camshaft.
  • the reference numeral 1 generally designates an internal-combustion engine, only part of which is shown, comprising a crankcase 2 and a head 3.
  • the crankcase defines a plurality of cylinders 4, only one of which is partly illustrated; each cylinder is associated with respective inlet and exhaust valves 4', only one of which is partly illustrated in dashed line in Figure 1.
  • the valves 4' are controlled by a camshaft 5 accommodated in the head 3.
  • Each cylinder 4 is additionally associated with an auxiliary decompression valve 6 normally co-operating in a fluidtight manner, under the action of a spring 6a, with a decompression port 7 connecting a combustion chamber 8 of the cylinder itself to an auxiliary exhaust duct 9.
  • the valve 6 is adapted to be opened at the end of the compression stroke of the associated cylinder 4, when required by the operating conditions of the vehicle, so as to dissipate the compression energy before the subsequent expansion (working) stroke and, therefore, to provide a braking action.
  • the auxiliary valve 6 is controlled by the camshaft 5, to which it can be selectively connected by means of an hydraulic actuating unit 10 which will be described in detail below.
  • the unit 10 essentially comprises a control member 11 and a rocker 12, one end 13 of which is attached to a movable member 14 of the control member 11 and the opposite end 15 of which co-operates with a stem 16 of the valve 6.
  • An intermediate part 17 of the rocker arm 12 is maintained in contact with a respective cam 18 of the camshaft 5 and is of arcuate shape, with its convexity facing the shaft 5.
  • control member 11 is illustrated in Figures 2 and 3, to which reference will be made in the following.
  • Said member 11 comprises a fixed outer casing 19 accommodated in a seating 20 provided in the head 3.
  • the casing 19 comprises an outer tubular body 24 and a cup-shaped body 25 provided with a base wall 26 and with a cylindrical wall 27 defining an inner cavity 28 and having an end opening 29; the cup-shaped body 25, the axial length of which is smaller than that of the body 24, is securely accommodated inside the body 24 so that the base wall 26 defines an intermediate transverse wall of the casing 19 and so that an end section of the wall 27 is coplanar with an end section of the body 24 itself.
  • the wall 26 axially separates the cavity 28 from a cavity 33 defined by the portion of the body 24 not occupied by the body 25.
  • the above-mentioned movable element 14 is slidably mounted inside the cavity 33 and essentially comprises a hollow piston 30 provided with a spherical head 31 integral therewith and extending axially to project towards the outside of the cylindrical body 24; said spherical head engages a corresponding seating 32 provided in the end 13 of the rocker arm 12 and forms a ball joint therewith.
  • the piston 30 axially delimits with the wall 26 of the body 25 a chamber 34 and is urged towards the end of the body 24 by a helical spring 35 accommodated in the chamber 34 itself, the stiffness of which is much lower than the spring 6a of the valve 6; a resilient ring 36 mounted inside the body 24 serves as an axial stop for the movable member 14.
  • the position of the movable member 14 is indicated in solid line in the absence of external loads or constraints, whereas there is indicated in dashed line the position effectively assumed in operation, when the head 31 is connected with the rocker arm 12.
  • Two radial holes 37, 38 are provided in the cylindrical wall 27 of the body 25 and are respectively disposed a lesser and greater distance from the end opening 29 in the body 25 itself.
  • the hole 37 communicates with a corresponding outlet hole 39 provided in the cylindrical body 24; an outer longitudinal slot 40 extends from the hole 39 and is extended to the outside of the seating 20.
  • the hole 38 communicates through an outer longitudinal slot 41 of the body 25 with the above-mentioned chamber 34.
  • the interior of the cavity 28 of the body 25 accommodates a cylindrical member 43 so that it can slide axially therein; said cylindrical member is urged by a spring 44 compressed between itself and the wall 26 of the body 25 towards the end opening 29 of the cavity 38; a resilient ring 45 mounted inside the wall 27 in the vicinity of the opening 29 forms an axial stop for the member 43.
  • Said member 43 has an axial cavity 46 communicating with the opening 29 through a non-return valve 47, and an intermediate circumferential slot 48 which communicates with the axial cavity 46 by means of a plurality of radial holes 49.
  • the cavity 46 has two sections 46a, 46b of different diameter, of which the section of larger diameter (46b) opens towards the wall 26, and forming between them an axial shoulder 51, the sections 46a, 46b of the cavity are separated from one another by a disc 52 clamped against the shoulder 51 and forming a support for the above-mentioned spring 44.
  • the section 46a is connected with the slot 40 by a radial through-hole 50 of the casing 19.
  • the non-return valve 47 comprises a ball 53 urged by a spring 56 into contact with a conical seating 54 provided between the cavity 46 and an axial hole 55 of the member 43 communicating with the opening 29; the spring 56 is compressed between the ball 53 and said disc 52.
  • the member 43 is movable under the pressure of a hydraulic fluid, as will be described below, and against the action of the spring 44 from a first rest position, shown in Figure 2, in which it is in contact with the ring 45, and a second position, shown in Figure 3, in which it is contact with the wall 26.
  • the circumferential slot 48 of the member 43 communicates with both the holes 37 and 38 and, therefore, the chamber 34 and the cavity 46a are connected with the outlet hole 39; in the second position, the slot 48 communicates with the hole 38 but not with the hole 37.
  • the opening 29 of the body 25 of the member 11 communicates with a duct 60 provided in the engine head 3 and connected to a lubricating circuit of the engine itself by a solenoid valve, which is normally closed. Therefore, the engine oil constitutes the operating fluid for the control member 11.
  • the mode of operation of the actuating unit 10 is the following.
  • the member 43 When the duct 60 is not pressurised, the member 43 is situated in the rest position shown in Figure 2, under the action of the spring 44.
  • the movable member 14 maintains the rocker arm 12 in contact with the camshaft 5 under the action of the spring 35, with a suitably reduced contact load defined by the low stiffness of the spring itself.
  • the movable member 14 is free to oscillate along the tubular body 24 under the pressure of the rocker arm 12, since the chamber 34 communicates, as indicated above, with the outlet hole 39.
  • the valve 6 remains closed, since the stiffness of the associated spring is much greater than that of the spring 35.
  • the cam 18 is timed so that the opening of the valve 6 takes place at the end of the compression stroke in the cylinder, so as to discharge the air compressed during said stroke and thus prevent the compression energy from being returned during the expansion stroke, thus producing engine work.
  • FIG 4 illustrates schematically an actuating unit 10 used in an engine 1' provided with a camshaft 5' in the crankcase.
  • the unit 10 is substantially equal to that described but is mounted inverted and the end 15 of the rocker arm actuates a transmission rod 61 which controls in known manner a rocker arm 62 of conventional type which, in turn, actuates the valve 6.
  • the mode of operation of the unit 10 is entirely analogous to that described.
  • control member 11 not only performs all the controlled of a conventional hydraulic tappet, in particular the automatic take-up of play, but can also be operated hydraulically in such a way so to activate or deactivate selectively the actuation of the valve; moreover, the use of a rocker arm 12, the member 11 of which, when activated, constitutes a rigid fulcrum, enables the actuating loads to be transmitted mechanically and, therefore, to obtain an optimum dynamic response, particularly in an embodiment using an overhead camshaft.
  • rocker arm 12 may be omitted or replaced with another suitable transmission member and the control member can be interposed directly between a driving member and a driven member.
  • the unit 10 and, in particular, the control member 11 can be used not only to control a valve of an engine but also in any other engineering application, in which there is the requirement of interconnecting a driving member and a driven member in a selective manner and of automatically taking up the play between said members.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP93119034A 1992-11-30 1993-11-25 Hydraulische Antriebsvorrichtung, insbesondere für Ventilsteuerung in einer Brennkraftmaschine Expired - Lifetime EP0600381B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITTO920972 1992-11-30
ITTO920972A IT1257926B (it) 1992-11-30 1992-11-30 Unita' di azionamento idraulica, particolarmente per il comando di unavalvola di un motore a combustione interna.

Publications (2)

Publication Number Publication Date
EP0600381A1 true EP0600381A1 (de) 1994-06-08
EP0600381B1 EP0600381B1 (de) 1997-03-26

Family

ID=11410895

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93119034A Expired - Lifetime EP0600381B1 (de) 1992-11-30 1993-11-25 Hydraulische Antriebsvorrichtung, insbesondere für Ventilsteuerung in einer Brennkraftmaschine

Country Status (4)

Country Link
EP (1) EP0600381B1 (de)
DE (1) DE69309229T2 (de)
ES (1) ES2100428T3 (de)
IT (1) IT1257926B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1612376A1 (de) * 2004-06-29 2006-01-04 Eaton S.R.L. Offenens Mini-Ventilspielausgleichselement

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4050435A (en) * 1975-12-02 1977-09-27 Harold L. Fuller, Jr. Valve control for cylinder cutout system
US4337739A (en) * 1980-03-24 1982-07-06 Jordan Edgar R Valve control mechanism for internal combustion engines
DE4000531A1 (de) * 1990-01-10 1990-06-13 Roland Schmidt Verstellvorrichtung zur veraenderung von ventilsteuerzeiten und ventilhub

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4050435A (en) * 1975-12-02 1977-09-27 Harold L. Fuller, Jr. Valve control for cylinder cutout system
US4337739A (en) * 1980-03-24 1982-07-06 Jordan Edgar R Valve control mechanism for internal combustion engines
DE4000531A1 (de) * 1990-01-10 1990-06-13 Roland Schmidt Verstellvorrichtung zur veraenderung von ventilsteuerzeiten und ventilhub

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1612376A1 (de) * 2004-06-29 2006-01-04 Eaton S.R.L. Offenens Mini-Ventilspielausgleichselement
WO2006003514A1 (en) * 2004-06-29 2006-01-12 Eaton Corporation Open ended mini lash adjuster
US7644693B2 (en) 2004-06-29 2010-01-12 Eaton Corporation Open ended mini lash adjuster

Also Published As

Publication number Publication date
DE69309229T2 (de) 1997-07-31
DE69309229D1 (de) 1997-04-30
ITTO920972A1 (it) 1994-05-30
ITTO920972A0 (it) 1992-11-30
EP0600381B1 (de) 1997-03-26
ES2100428T3 (es) 1997-06-16
IT1257926B (it) 1996-02-19

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