EP0510327B1 - Vorrichtung zur Änderung der Ventilsteuerzeiten einer mehrzylindrigen Brennkraftmaschine - Google Patents

Vorrichtung zur Änderung der Ventilsteuerzeiten einer mehrzylindrigen Brennkraftmaschine Download PDF

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Publication number
EP0510327B1
EP0510327B1 EP92103128A EP92103128A EP0510327B1 EP 0510327 B1 EP0510327 B1 EP 0510327B1 EP 92103128 A EP92103128 A EP 92103128A EP 92103128 A EP92103128 A EP 92103128A EP 0510327 B1 EP0510327 B1 EP 0510327B1
Authority
EP
European Patent Office
Prior art keywords
rotary piston
oil
recess
combustion engine
setting
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
EP92103128A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0510327A2 (de
EP0510327A3 (en
Inventor
Herbert Ampferer
Willi Schultz
Imre Dr. Szodfridt
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche 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 Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0510327A2 publication Critical patent/EP0510327A2/de
Publication of EP0510327A3 publication Critical patent/EP0510327A3/de
Application granted granted Critical
Publication of EP0510327B1 publication Critical patent/EP0510327B1/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 invention relates to a device on an internal combustion engine according to the features specified in the preamble of claim 1.
  • a generic device with an oil-hydraulic phase converter which has a coupling member designed as an adjusting piston and axially displaceable in two end positions.
  • the coupling member engages with helical gears in a camshaft and in a ring gear driving the camshaft, so that an axial displacement of the actuating piston rotates the camshaft relative to the crankshaft driving it, thereby causing a change in the valve timing.
  • the supply of pressure oil from the oil circuit of the internal combustion engine into the phase converter is controlled by an axially electromagnetically displaceable piston depending on parameters of the internal combustion engine, which is held in a hollow flange shaft screwed to the camshaft.
  • the piston has several bores or circumferential grooves and must be manufactured with high accuracy to avoid leaks, since only short sealing surfaces are available between the oil supply and discharge bores arranged in the flange shaft.
  • DE 36 16 234 A1 discloses a further device for changing the valve timing of a multi-cylinder internal combustion engine, in which a hydraulic double-acting cylinder / piston unit can be controlled by means of a valve device.
  • This valve device can be controlled according to a map of the internal combustion engine in order to achieve an operating point-dependent adjustment of the camshaft. Neither the valve device nor the map of the internal combustion engine are further developed.
  • the invention has for its object a generic device for changing the valve timing with an oil-hydraulic phase converter in one To create internal combustion engine in which the supply and discharge of oil in the phase converter is carried out in a simplified manner.
  • Oil is supplied and discharged into the phase converter in a simple manner via a valve device which has a housing connected to the oil circuit of the internal combustion engine and a rotary piston mounted therein in a cylindrical receptacle.
  • This rotary lobe is can be pivoted into a first or a second position and thereby connects the oil circuit supplying pressure oil to the coupling element of the phase converter via oil-carrying lines in such a way that it is displaced into its first or second end position.
  • the change in the valve timing of the internal combustion engine can thus be triggered by a simple pivoting movement of the rotary piston.
  • Sufficiently large sealing surfaces are available between the rotary piston and the receptacle arranged in the housing. The effort for tolerances is therefore comparatively low.
  • the rotary piston and the connection diagram of the oil-carrying lines opening into the receptacle of the housing are designed in such a way that the rotary piston is relieved of radial pressure and that sufficiently large sealing surfaces are available.
  • a second embodiment provides an axially pressure-relieved rotary piston which has only one bore and is kept small in diameter.
  • Both versions are with e.g. formed as an actuator, engaging in a groove of the rotary piston from one to the other position.
  • the positions are precisely determined, for example, by a pin which is fixed in the housing and slides in a guide slot of the rotary pistons.
  • the servomotor or a clock valve which is arranged in front of an actuator designed as a pressure cell, is controlled by a control unit of the internal combustion engine as a function of one or more parameters, such as load, speed, oil temperature. controlled.
  • the switching characteristics of the valve device can be determined by the position of control edges. Closely adjacent control edges of recesses in the rotary lobes produce a "hard" switching characteristic which operates with little or no coverage of the oil supply and discharge lines, while a "soft" operating with greater coverage can be achieved with a greater distance.
  • each of the two camshafts 1 serving the inlet is assigned a phase converter 2 at the drive end 3.
  • Each camshaft 1 is held in several bearings 4 which are connected to a lubrication circuit 5.
  • the oil circuit of the internal combustion engine comprises the lubrication circuit 5, an actuation circuit for adjusting the phase converter 2 and a lubrication circuit of the crankshaft 6.
  • a pump 8 pumps oil from a reservoir 9 through a filter 10. From there, a branch 11 leads to the crankshaft 6 of the internal combustion engine and via an oil-supplying channel 12 to a valve device 13 and to the lubrication circuit 5.
  • the valve device 13 has a housing 14 with a cylindrical receptacle 15 in which a rotary piston 16 is pivotally mounted.
  • a first and a second line 17 and 18 are connected to the housing 14 and are each connected to the camshafts 1.
  • the lines 17 and 18 open into ring channels 19 of a bearing 20.
  • Radial bores 21 and 22 lead from the ring channels 19 to channels 23 and 24 formed in the interior of the camshafts 1.
  • channels 23 and 24 are shown in a manner not shown with two in the phase changers 2 formed chambers 25 and 26 in connection.
  • the chambers 25 and 26 are arranged on both sides of a coupling member designed as an axially displaceable piston 27 in a phase converter housing 28.
  • the phase converters 2 are driven from the crankshaft 6 via an endless drive, not shown.
  • the rotary piston 16 consists of an upper or lower circular cover plate 30 or 31 and a distributor piece 32 arranged between them.
  • Continuous drain bores 33 and 34 are arranged on both sides and symmetrically to an axis of rotation A-A of the rotary piston 16.
  • a connection bore 35 extends perpendicularly to the axis A-A in the center of the distributor piece 32.
  • Connections 36 and 37, respectively, opening into the outlet bores 33 and 34 are made from a cylindrical outer surface F of the rotary piston 16.
  • the upper cover plate 30 has a groove 38 and a curved guide slot 39 between the drain holes 33, 34.
  • the distributor piece 32 is cut symmetrically to the axis A-A through recesses 40 in the form of a segment of a circle, control edges 41 being formed. The distance between the control edges 41 is determined by the radius R of the recesses 40.
  • the housing 14 receiving the rotary piston 16 is held on the internal combustion engine by means of screw connections 42.
  • a step receptacle 43 of the housing 14 accommodates an actuator, which is designed as an actuator 44 and is only indicated, which engages in the groove 38.
  • a fitting bore 45 corresponding to the guide slot 39 serves to receive a pin 46.
  • Blind holes 48 and 49 run from the underside 47 of the housing 14, which pass through transverse bores 50 to the cylindrical receptacle 15 are connected.
  • the oil-supplying channel 12 is connected to the blind hole 48, the first and second lines 17 and 18 to the blind holes 49.
  • the housing 14 is provided with an oil-removing return 51, which opens into the reservoir 9.
  • the pump 8 pumps oil from the reservoir 9 through the filter 10 into the channel 12.
  • the branching 11 leads part of the oil flow to the crankshaft 6 and to further lubrication points of the internal combustion engine as well as to the lubrication circuit 5 and to the blind hole 48 of the Housing 14.
  • the rotary piston 16 In a first operating state of the internal combustion engine, for example a low speed range, the rotary piston 16 is in a first position S1 according to FIG. 1.
  • the pressure oil passes from the blind hole 48 via the transverse bore 50 into one of the recesses 40 which is connected to the opposite recess 40 via the connecting bore 35. From there, the oil flows through the first line 17 to the ring channels 19 of the bearing points 20.
  • the bores 21 and the channels 23 guide the oil into the chambers 25 and move the pistons 27 into a first end position E1, which corresponds to the position S1 of the rotary piston 16 corresponds.
  • the intake valves (not shown) actuated by the camshafts 1 have a slight overlap with the exhaust valves.
  • the control unit 52 If during operation of the internal combustion engine the parameters load L and / or speed n of the internal combustion engine recorded by an electronic control unit 52 change into a further operating state, for example a medium speed range, the control unit 52 outputs a corresponding signal U to the servomotor 44 and pivots it the rotary piston 16 counterclockwise into a second position S2, which is indicated by dashed lines in Fig. 1.
  • the positions S1 and S2 are defined by the length of the guide slot 39 sliding on the pin 46.
  • In the Position S2 reaches pressure oil through the second lines 18 and the channels 24 into the chambers 26 and move the pistons 27 into a second end position E2, which corresponds to the position S2 of the rotary piston 16.
  • the phase changers 2 change in a known manner the relative rotational position of the camshafts 1 with respect to the camshafts used for the exhaust such that there is a relatively large overlap between intake and exhaust valves.
  • valve device 13 is relieved of radial pressure due to the symmetrical arrangement of the recesses 40, i.e. there are no forces pressing the outer surface F into the receptacle 15 on one side.
  • the seal of the rotary piston 16, not shown here, is therefore unproblematic. Sufficiently large sealing surfaces exist between the oil flows to be separated from one another on the outer surface F, so that relatively coarse tolerances between the receptacle 15 and the rotary piston 16 can be used.
  • FIGS. 9 to 11b A second embodiment of the invention is shown in FIGS. 9 to 11b. Parts or positions that correspond to those of the first embodiment are provided with identical reference numerals.
  • the valve device 13 has a housing 140 with a rotary piston 160 mounted in a cylindrical receptacle 150. Depending on the parameters, this can be pivoted by a servomotor 44 from a first position S1 shown in FIGS. 10a and 11a to a second position S2 shown in FIGS. 10b and 11b. Both positions S1 and S2 in turn correspond to the end positions E1 and E2 of the pistons 27.
  • the rotary piston 160 has a connecting bore 350 running along its axis of rotation AA, which is closed at its lower end with a plug 53.
  • a semicircular recess 400 which intersects the connecting bore 350.
  • a further recess 401 is arranged, which also intersects the connecting bore 350.
  • the rotary piston 160 has a drainage groove 402.
  • the return line 51 opens into the receptacle 150 between the lines 17 and 18.
  • the housing 140 has a circumferential groove 403 at the level of the channel 12, so that oil flows into the connecting bore 350 from the channel 12 in each position of the rotary piston 160 via a recess 400 designed as a bore.
  • the valve device 13 is radially relieved of pressure at the level of the channel 12.
  • valve device 13 is additionally radially depressurized at the level of the lines 17 and 18.
  • the two lines 17, 18 are arranged in a plane at an angle of 90 ° to one another and the recess 401 penetrates the rotary piston 160 radially.
  • the drain groove 402 extends parallel to the axis of rotation A-A up to the outlet 51 lying in a parallel plane.

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)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP92103128A 1991-04-26 1992-02-25 Vorrichtung zur Änderung der Ventilsteuerzeiten einer mehrzylindrigen Brennkraftmaschine Expired - Lifetime EP0510327B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4113663 1991-04-26
DE4113663A DE4113663C1 (enrdf_load_stackoverflow) 1991-04-26 1991-04-26

Publications (3)

Publication Number Publication Date
EP0510327A2 EP0510327A2 (de) 1992-10-28
EP0510327A3 EP0510327A3 (en) 1993-05-05
EP0510327B1 true EP0510327B1 (de) 1996-04-17

Family

ID=6430414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92103128A Expired - Lifetime EP0510327B1 (de) 1991-04-26 1992-02-25 Vorrichtung zur Änderung der Ventilsteuerzeiten einer mehrzylindrigen Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP0510327B1 (enrdf_load_stackoverflow)
JP (1) JPH0666165A (enrdf_load_stackoverflow)
DE (2) DE4113663C1 (enrdf_load_stackoverflow)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6158404A (en) * 1997-02-26 2000-12-12 Aft Atlas Fahrzeugtechnik Gmbh Apparatus for regulating the operation of an adjusting device
WO2001049978A1 (de) * 1999-12-30 2001-07-12 Krupp Presta Ag Welle als maschinenbauteil mit integrierten leitungen
DE10315594A1 (de) * 2003-04-05 2004-10-14 Daimlerchrysler Ag Nockenwellenverstellvorrichtung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3616234A1 (de) * 1986-05-14 1987-11-19 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehlagenaenderung zweier in antriebsverbindung stehender wellen, insbesondere zwischen in einem maschinengehaeuse einer brennkraftmaschine gelagerten kurbelwelle und nockenwelle

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB538169A (en) * 1940-01-20 1941-07-23 Dehavilland Aircraft Improvements relating to fluid valves
EP0141874A1 (de) * 1983-11-14 1985-05-22 Hans Hermes Steuerungstechnik Wegeventilvorrichtung
US4658859A (en) * 1984-12-07 1987-04-21 South Bend Lathe, Inc. Valve spool with cross drill ports
DE3942400A1 (de) * 1989-12-21 1991-06-27 Audi Ag Antriebsvorrichtung fuer die nockenwelle einer brennkraftmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3616234A1 (de) * 1986-05-14 1987-11-19 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehlagenaenderung zweier in antriebsverbindung stehender wellen, insbesondere zwischen in einem maschinengehaeuse einer brennkraftmaschine gelagerten kurbelwelle und nockenwelle

Also Published As

Publication number Publication date
EP0510327A2 (de) 1992-10-28
EP0510327A3 (en) 1993-05-05
DE4113663C1 (enrdf_load_stackoverflow) 1992-06-11
DE59205989D1 (de) 1996-05-23
JPH0666165A (ja) 1994-03-08

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