EP0573622B1 - Hydraulische steuereinrichtung - Google Patents

Hydraulische steuereinrichtung Download PDF

Info

Publication number
EP0573622B1
EP0573622B1 EP92923271A EP92923271A EP0573622B1 EP 0573622 B1 EP0573622 B1 EP 0573622B1 EP 92923271 A EP92923271 A EP 92923271A EP 92923271 A EP92923271 A EP 92923271A EP 0573622 B1 EP0573622 B1 EP 0573622B1
Authority
EP
European Patent Office
Prior art keywords
pressure
coupling element
camshaft
central body
piston pump
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
EP92923271A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0573622A1 (de
Inventor
Helmut Rembold
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0573622A1 publication Critical patent/EP0573622A1/de
Application granted granted Critical
Publication of EP0573622B1 publication Critical patent/EP0573622B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

Definitions

  • the invention relates to a hydraulic control device for rotating the camshaft of an internal combustion engine according to the preamble of the main claim.
  • a hydraulic control device for rotating the camshaft of an internal combustion engine according to the preamble of the main claim.
  • the pump and the solenoid valve are arranged externally, which is relatively cumbersome, in particular with regard to the necessary line connections, but also requires a considerable amount of construction work (DE-OS 32 47 116).
  • a hydraulic control device for rotating a camshaft is known, with a coupling member which is longitudinally displaceable by means of a compressive force and which, by means of helical teeth when shifting, effects a relative rotation of the camshaft and drive sprocket of the control device.
  • the liquid pressure controlled by a solenoid valve which serves as the working pressure
  • the known control device has the disadvantage that the pressure medium source is formed by a pump located outside the control device, so that this control device also has a relatively large construction.
  • the hydraulic control device according to the invention with the characterizing features of claim 1 has the advantage that it is very compact and is very easy to install in an internal combustion engine or in its engine compartment. Further advantages of the invention emerge from the subclaims.
  • FIG. 1 a longitudinal section of a first embodiment, in Figure 2 a section along 2/2 of Figure 1, in Figure 3, a second embodiment, also in longitudinal section, in Figure 4 a modification of the previous embodiment, in Figure 5, a third embodiment, but only partially and shown in longitudinal section, in Figure 6 is a view of a detail.
  • 10 denotes the end of a camshaft, which serves to actuate the valves of an internal combustion engine.
  • An elongated, cylindrical central body 11 is firmly screwed into the end of the camshaft, the axis of which extends coaxially with that of the camshaft.
  • a coupling member 12 is slidably mounted on the outside thereof, which has helical teeth 13 on the outside at its end facing away from the camshaft and also has helical teeth 14 on its inside in the same plane.
  • the helical teeth 14 are in engagement with a helical toothing 15 on the outside of the central body 11, while the helical toothing 13 is in engagement with a helical toothing 16 on the inside of the extension 17 of a hollow cylindrical sprocket 18.
  • the camshaft 10 is supported in a camshaft bearing 20, which is formed, for example, at a suitable location on the internal combustion engine. From the above it can be seen that the central body 11 rotates with the camshaft, that of course the chain wheel 18 also rotates, which is driven by the crankshaft of the internal combustion engine, and that the coupling member 13 also rotates.
  • the coupling member has a deep, longitudinal groove 21, in which a compression spring 22 is arranged, which is supported on the one hand on the bottom of the coupling member, and on the other hand on a cover 23 which closes the extension 17 of the sprocket 18.
  • a radial piston pump 26 is arranged in a recess 25 within the chain wheel 18.
  • This has a stator 27 which is fixedly connected to the camshaft bearing 20 via bolts 28.
  • a plurality of approximately radially extending bores 29 are formed in the stator, in which pistons 30 slide, which bear with their outer tips on a race 31, which is likewise arranged in the recess 25.
  • the cylindrical recess 25 is formed eccentrically with respect to the axis of the central body 11 or the camshaft 10.
  • the ring 31 is arranged non-rotatably by means of a radially inwardly extending bolt 32, which projects into a suitable slot 33 of the stator 27, see FIG. 2, from which the eccentricity of the recess 25 can also be clearly seen.
  • the end of the central body 11 lying in the plane of the pistons 30 is designed as a control pin for the radial piston pump 26 and has two mutually opposite control slots 36, 37 for the high-pressure or low-pressure side, which extend on its outer circumference.
  • a small bore 38 which is connected to a transverse blind bore 39 in the central body, which likewise opens into a longitudinal channel 40 in the central body.
  • a second transverse bore 41 extends from the longitudinal bore 40 and opens into a pressure chamber 43 which is formed between the coupling member 12 and the chain wheel 18.
  • a cylindrical extension 44 is formed, in which the tappet 45 of a valve body 46 is located, which can close or open the channel 40.
  • the plunger 45 has two collars 47, 48 in the area of the extension 44, on the outside of which longitudinal grooves (not shown) are formed.
  • the end of the valve body facing away from the The plunger is held in the armature 50 of an electromagnet 51, which consists in a known manner of a magnetic coil 52 and the associated iron circle 53.
  • the plunger 45 penetrates through a central bore 55 in the cover 23.
  • the central body 11 and the coupling member 12 When the sprocket 18 is driven - of course the camshaft 10, the central body 11 and the coupling member 12 also rotate - the pistons 30 perform a lifting movement. They are pressurized with engine oil pressure via a bore or a space 56 in the end of the camshaft, in which an oblique bore 57 also opens into the end face of the central body 11.
  • the suctioned-in pressure medium is displaced by the piston into the blind bore 39, the channel 40 and the transverse bore 41. This pressure medium enters the pressure chamber 43 at the end of the coupling member 12.
  • the delivery flow lifts the valve body 46 from its seat, so that the pressure medium can flow out to the oil container via the extension 44 and a cross-bore 59, which is only shown in broken lines.
  • the pressure chamber 43 is depressurized, so that the compression spring 22 moves the coupling member 12 to the right.
  • the sprocket 18 is now rotated relative to the camshaft 10 so that it now occupies a first position. This means “late intake closing" of the engine valves.
  • the electromagnet 51 is excited, the valve body 56 now approaches its valve seat, and the delivery flow is throttled, as a result of which a corresponding pressure builds up in the pressure chamber 43 analogously to the magnetic force.
  • the coupling member 12 is displaced to the left against the force of the compression spring 22 via the pressure that is now generated. This in turn results in a relative rotation of the sprocket 18 with respect to the camshaft 10, so that new positions now continuously take place in the direction of "early opening" of the intake valves.
  • pressure i.e. Energization of the electromagnet 51, any position in the stroke range of the internal combustion engine can now be set.
  • the exemplary embodiment according to FIG. 3 differs from that according to FIG. 1 in that here the coupling element - designated by 12A - is acted upon twice, i.e. on both sides of the same are pressure chambers, which are designated 63 and 64. This requires a somewhat different design of the radial piston pump - designated by 26A - of the central body 11A and of the electromagnetic valve, designated overall by 65.
  • an oblique bore 81 (suction channel) leads to the suction slots 82 in the central body, opposite which the pressure slots 84, 85 are located on the central body. It is essential with this radial piston pump that it must have two pistons located opposite one another.
  • the valve body 74 has a central part, on which slots 87 are formed on the outer circumference, via which connection there is from the space 77 to an opposite space 88, to which a bushing 89 connects, which has a continuous transverse bore 90, via which there is a connection to the pressure space 63, via the helical gears.
  • a plunger 92 which is fastened in the armature 50, in turn connects to the valve body 74.
  • the pressure spaces 63, 64 are loaded or relieved.
  • the coupling member 12 A is shifted, which in turn causes a relative rotation of the camshaft with respect to the sprocket 18 via its helical gears, as described in the exemplary embodiment according to FIG. 1.
  • the pressure in the pressure chamber 63 is relieved, for example, when the valve cone 76 rests on its valve seat, thereby creating a connection from the chamber 88 via the valve seat on the cone 75 and the longitudinal slide 87 to the low-pressure channel 78 an electronic control unit.
  • FIG. 4 again relates to a modification of that according to FIG. 1, but is similar to that according to FIG. 3, since it in turn has a coupling element acted upon twice. - Only the radial piston pump is modified - now designated with 26B -. This construction is more compact than the one described above, since the essential parts are nested, i.e. lie in a radial plane. For this reason, this embodiment is only partially shown, since the valve control is the same.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
EP92923271A 1991-12-28 1992-11-12 Hydraulische steuereinrichtung Expired - Lifetime EP0573622B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4143153A DE4143153A1 (de) 1991-12-28 1991-12-28 Hydraulische steuereinrichtung
DE4143153 1991-12-28
PCT/DE1992/000937 WO1993013301A1 (de) 1991-12-28 1992-11-12 Hydraulische steuereinrichtung

Publications (2)

Publication Number Publication Date
EP0573622A1 EP0573622A1 (de) 1993-12-15
EP0573622B1 true EP0573622B1 (de) 1996-01-31

Family

ID=6448225

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92923271A Expired - Lifetime EP0573622B1 (de) 1991-12-28 1992-11-12 Hydraulische steuereinrichtung

Country Status (5)

Country Link
EP (1) EP0573622B1 (ko)
JP (1) JP3450007B2 (ko)
KR (1) KR930703525A (ko)
DE (2) DE4143153A1 (ko)
WO (1) WO1993013301A1 (ko)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2988101B2 (ja) * 1992-01-30 1999-12-06 アイシン精機株式会社 弁開閉時期制御装置
DE10002512A1 (de) 2000-01-21 2001-07-26 Porsche Ag Zylinderkopf für eine ventilgesteuerte Brennkraftmaschine
CN101539178B (zh) 2008-03-19 2010-12-08 李礼然 偏传式离合器
CN102459827B (zh) * 2009-06-05 2014-01-22 日锻汽门株式会社 发动机的相位可变装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1152959B (it) * 1982-05-17 1987-01-14 Alfa Romeo Spa Dispositivo per la variazione automatica della fasatura di un albero a camme
DE3929621A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehwinkelverstellung einer welle zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine

Also Published As

Publication number Publication date
JP3450007B2 (ja) 2003-09-22
DE4143153A1 (de) 1993-07-01
WO1993013301A1 (de) 1993-07-08
EP0573622A1 (de) 1993-12-15
DE59205255D1 (de) 1996-03-14
KR930703525A (ko) 1993-11-30
JPH06506518A (ja) 1994-07-21

Similar Documents

Publication Publication Date Title
DE4227619C2 (de) Vorrichtung zur Änderung der Ventilsteuerzeiten einer Brennkraftmaschine
EP0564609B1 (de) Hydraulische steuereinrichtung
EP2386731A1 (de) Hydraulikventil
DE4023853C2 (ko)
EP1212517B1 (de) Nockenwellenversteller für brennkraftmaschinen
WO2010139522A1 (de) Steuerventil zum steuern von druckmittelströmen mit integriertem rückschlagventil
EP0564610B1 (de) Hydraulische steuereinrichtung
DE4121435C2 (de) Motorbremse für eine mehrzylindrige Brennkraftmaschine
DE60301312T2 (de) Treibstoffpumpenanordnung
EP0455763B1 (de) Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine
EP0573622B1 (de) Hydraulische steuereinrichtung
EP0572578B1 (de) Hydraulische steuereinrichtung
DE4240075C2 (de) Hydraulische Stelleinrichtung
EP2920436B1 (de) Schwenkmotorversteller mit einem elektromagnetisch betätigten hydraulikventil
DE102006053703A1 (de) Vorrichtung zur Steuerung von Gaswechselventilen von Brennkraftmaschinen
DE4229201C2 (de) Vorrichtung zum Verstellen der Nockenwellen-Steuerzeiten
DE4133526A1 (de) Hydraulische stelleinrichtung
DE4037089C2 (de) Hydraulische Einrichtung zum Verdrehen der Nockenwelle einer Brennkraftmaschine
DE4210742A1 (de) Hydraulische Steuereinrichtung
DE2654526B2 (de) Hydrostatische Radialkolbenmaschine
DE3817554C2 (ko)
DE19523578C2 (de) Rotationsverteiler-Kraftstoffeinspritzpumpe
DE4440749A1 (de) Kraftstoffeinspritzpumpe
DE4423133C2 (de) Betätigungseinheit für eine Verstellvorrichtung, vorzugsweise für eine Ventilhubverstelleinrichtung von Kraftfahrzeugen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19930723

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR IT SE

17Q First examination report despatched

Effective date: 19941021

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT SE

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59205255

Country of ref document: DE

Date of ref document: 19960314

ITF It: translation for a ep patent filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20031119

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20031124

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20031215

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050601

EUG Se: european patent has lapsed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050729

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051112