EP0334272B1 - Hydraulische Ventilöffnungseinheit im Zylinderkopf einer Brennkraftmaschine - Google Patents

Hydraulische Ventilöffnungseinheit im Zylinderkopf einer Brennkraftmaschine Download PDF

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Publication number
EP0334272B1
EP0334272B1 EP89104989A EP89104989A EP0334272B1 EP 0334272 B1 EP0334272 B1 EP 0334272B1 EP 89104989 A EP89104989 A EP 89104989A EP 89104989 A EP89104989 A EP 89104989A EP 0334272 B1 EP0334272 B1 EP 0334272B1
Authority
EP
European Patent Office
Prior art keywords
valve
opening unit
piston
hydraulic
stroke
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.)
Expired - Lifetime
Application number
EP89104989A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0334272A1 (de
Inventor
Jurij Gartner
Anton Schollweck
Peter Langen
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0334272A1 publication Critical patent/EP0334272A1/de
Application granted granted Critical
Publication of EP0334272B1 publication Critical patent/EP0334272B1/de
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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/08—Shape of cams
    • 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 hydraulic valve opening unit of the type specified in the preamble of the first claim and is based on the generic DE-OS 36 21 402.
  • Hydraulic valve opening units are known in various designs.
  • a cam actuates a master piston, which acts on a working piston via a hydraulic chamber, the latter resting on the stem of a lift valve.
  • the master piston and the working piston are usually arranged coaxially with one another.
  • this arrangement requires a large amount of space and is very tall.
  • the disadvantages with regard to the hydraulic transmission behavior are evident. Therefore, in the above scripture of the master piston arranged at right angles to the working piston or to the stroke valve actuated by it.
  • the master piston is arranged spatially between the inlet and outlet valve and its axis not only angled, but also offset from the axis of the inlet valve. This makes it possible to supply the hydraulic fluid acting on the working piston to it from the side, that is to say tangentially.
  • the cross section of the master piston is larger than the cross section of the working piston, there is a hydraulic ratio. High valve or working piston strokes can be achieved with significantly lower strokes of the master piston. The space requirement is thus reduced in the axial direction of the master piston; the cross-sectional area of the cam that determines the maximum master piston stroke can also be kept smaller.
  • braking devices are often provided which influence the speed of the valve closing movement caused by the removal of hydraulic fluid.
  • the hydraulic fluid discharged usually flows through a throttle gap.
  • braking device concentrically with the working piston and in particular within it.
  • Claim 4 advantageously develops the cam actuating the master piston.
  • the cam can be designed such that the closing movement of the valve is always brought about in all operating points of the internal combustion engine by the removal of hydraulic fluid. This reduces the mechanical load on the master piston and allows it to be simplified or made correspondingly small. The mechanical load on the cam and master piston therefore only has to be taken into account in the initial phase of the valve opening movement. If a hydraulic transmission ratio is integrated in the hydraulic valve opening unit according to the invention, a rapid valve opening movement which is desired with regard to the dynamics of charge change can be achieved even with relatively little acceleration of the master piston, which means low mechanical loads and thus small size.
  • An intake valve 2 is arranged in a cylinder head 1 of an internal combustion engine, and an exhaust valve 3 is arranged at an angle thereto. While the latter is actuated by a cam 5, as is generally the case with the interposition of a hydraulic lash adjuster 4, a hydraulic valve opening unit, designated as a whole by 6, is provided for the inlet valve 2.
  • This consists essentially of a housing 7, a piston 8 actuating the inlet valve 2, one with this in hydraulic Ver binding master piston 9, and a cam acting on the master piston 9. 10
  • the axis of the master piston 9 is angled and offset from the axis of the working piston 8 or the inlet valve 2.
  • the master piston 9 is arranged within the V-space spanned by the inlet valve 2 and the outlet valve 3, an extremely space-saving arrangement is created. This can also be seen from FIG. 2, two valve opening units according to the invention being shown here in mirror image next to one another.
  • the hydraulic valve opening unit 6 operates as follows: Hydraulic fluid enters a hydraulic chamber 16 via an inlet channel 14 and a check valve 12.
  • the hydraulic chamber 16 also has a control channel 18 which opens into a storage space 20 and can be closed by means of a slide 22.
  • This slide 22 is actuated by an eccentric shaft 26 acting against a tappet 24.
  • the hydraulic chamber 16 is further delimited by the master piston 9, the effective cross section of which is larger than the effective cross section of the working piston 8. If the master piston 9 is now moved by rotation of the cam 10, it displaces hydraulic fluid from the hydraulic chamber 16 via a valve with a check valve 27 provided channel 28 in a pressure chamber 30 (see in particular. Fig. 2). As a result, the working piston 8 is moved and thus causes the opening valve 2 to open. This process is ended when either the stroke of the master piston 9 becomes smaller or the control channel 18 is released. For this purpose, the slide 22 can be moved in or against the direction of arrow 32 by rotation of the eccentric shaft 26.
  • throttle gap 34 is determined by one within the Working piston 8 provided, designated in its entirety with 36 braking device (see in particular. Fig. 2).
  • that braking device 36 consists of a tapered longitudinal groove 37 provided in the outer surface of the working piston 8 and the non-return valve 28 already explained thus narrowing in the course of the valve closing movement, formed together with a projection 35 of the housing 7, throttle gap 34.
  • Fig. 3 shows an exemplary elevation curve of the master piston depending on the cam angle ⁇ . That curve is divided into three main phases. In the first phase designated I, a maximum elevation ⁇ h per cam angle change ⁇ is aimed for. That maximum valve lift increase is determined in particular by the mechanical strength of the cam 10 and the master piston 9. Since, according to the invention, a hydraulic transmission ratio is built into the hydraulic valve opening unit 6, the cross-section of the master piston 9 is therefore larger than the cross-section of the working piston 8, is sufficient to achieve one desired rapid valve opening movement a relatively slower stroke course of the master piston 9. Thus, the master piston 9 can be made light and in particular compact.
  • phase II following that first phase represents a transition area to phase III, which in turn has a decreasing master piston stroke h.
  • Phase II also covers a relatively wide cam angle range ⁇ p * , since that phase represents the usual working range for intake valve 2.
  • the valve closing movement is initiated in the entire operating range of the internal combustion engine by actuating the slide 22 and discharging hydraulic fluid into the storage space 20.
  • This has the advantage that the stroke of the master piston 9 can be designed in phase III taking mechanical aspects into account. With this cam contour, an optimal filling process of the pressure chamber 30 can be achieved in interaction with the design of the working piston 8 and the check valve 27.

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)
EP89104989A 1988-03-24 1989-03-21 Hydraulische Ventilöffnungseinheit im Zylinderkopf einer Brennkraftmaschine Expired - Lifetime EP0334272B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3809953 1988-03-24
DE3809953A DE3809953C1 (enrdf_load_stackoverflow) 1988-03-24 1988-03-24

Publications (2)

Publication Number Publication Date
EP0334272A1 EP0334272A1 (de) 1989-09-27
EP0334272B1 true EP0334272B1 (de) 1991-07-24

Family

ID=6350591

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89104989A Expired - Lifetime EP0334272B1 (de) 1988-03-24 1989-03-21 Hydraulische Ventilöffnungseinheit im Zylinderkopf einer Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP0334272B1 (enrdf_load_stackoverflow)
DE (2) DE3809953C1 (enrdf_load_stackoverflow)
ES (1) ES2024058B3 (enrdf_load_stackoverflow)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5127375A (en) * 1991-04-04 1992-07-07 Ford Motor Company Hydraulic valve control system for internal combustion engines
PL1674673T3 (pl) * 2004-12-23 2007-08-31 Fiat Ricerche Silnik spalinowy z hydraulicznie zmiennymi zaworami

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH243908A (de) * 1944-11-27 1946-08-15 Schweizerische Lokomotiv Flüssigkeitsbremse mit Rückschlagventil am Passivkolben von hydraulisch gesteuerten Ventilen von Brennkraftmaschinen.
DE2840445C2 (de) * 1978-09-16 1984-10-04 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Hydraulische Vorrichtung zum Betätigen eines Gaswechselventils für Brennkraftmaschinen
DE3611476A1 (de) * 1986-04-05 1987-10-08 Irm Antriebstech Gmbh Verfahren zur betaetigung von ventilen zum ladungswechsel bei brennkraftmaschinen mit direkter hydraulischer uebertragung
DE3621402A1 (de) * 1986-06-26 1988-01-14 Kloeckner Humboldt Deutz Ag Hydraulisch betaetigter stoessel
DE3625664A1 (de) * 1986-07-29 1988-02-04 Bayerische Motoren Werke Ag Vorrichtung zur beeinflussung des von einem nocken gesteuerten ventilhubes

Also Published As

Publication number Publication date
DE3809953C1 (enrdf_load_stackoverflow) 1989-08-24
EP0334272A1 (de) 1989-09-27
DE58900184D1 (de) 1991-08-29
ES2024058B3 (es) 1992-02-16

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