EP0572578A1 - Systeme de commande hydraulique. - Google Patents

Systeme de commande hydraulique.

Info

Publication number
EP0572578A1
EP0572578A1 EP92918639A EP92918639A EP0572578A1 EP 0572578 A1 EP0572578 A1 EP 0572578A1 EP 92918639 A EP92918639 A EP 92918639A EP 92918639 A EP92918639 A EP 92918639A EP 0572578 A1 EP0572578 A1 EP 0572578A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
toothing
coupling member
hydraulic
pressure
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
EP92918639A
Other languages
German (de)
English (en)
Other versions
EP0572578B1 (fr
Inventor
Martin Mueller
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 EP0572578A1 publication Critical patent/EP0572578A1/fr
Application granted granted Critical
Publication of EP0572578B1 publication Critical patent/EP0572578B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

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 pressure medium connections, but also requires considerable construction effort (DE-OS 32 47 916).
  • the hydraulic control device according to the invention with the characterizing features of the main claim has the advantage that it has a very compact construction and is very easy to install in an internal combustion engine or in its engine compartment. Further advantages of the invention result from the subclaims. drawing
  • FIG. 1 shows a longitudinal section in FIG. 1 of a first exemplary embodiment of a hydraulic control device for rotating the camshaft of an internal combustion engine, in FIG. 2 a modification of this exemplary embodiment and in FIG. 3 a detail.
  • 10 denotes the camshaft of an internal combustion engine, which is mounted in the camshaft bearing block 11 of the internal combustion engine.
  • the camshaft has a continuous longitudinal bore 12 into which the sleeve-shaped extension 13 of an approximately cup-shaped flange part 14 projects.
  • a sprocket 15 for driving the camshaft 12 connects to the end face of the flange part, followed by a cylinder-shaped hydraulic body 16.
  • the parts 12 to 16 are held together by screws 17 in a rotationally fixed manner.
  • the parts mentioned form an interior cavity 18 in which a coupling member 20 is arranged. This has a shaft 21 which projects into the extension 13 of the flange part 14.
  • a straight toothing 22 is formed on the outer circumference of the shaft 21 and engages with such straight toothing 23 on the inner circumference of the sleeve-shaped extension.
  • the shaft 21 of the coupling member 20 is followed as an integral part by a cup-shaped ring part 24 which has helical teeth 25 on its outer circumference, which engages with such helical teeth 26 on the inner circumference of the chain wheel 15. Dips into the cavity 28 of the coupling member or its ring part 24 a piston 29, which always lies against the bottom 30 of the coupling member.
  • the piston 29 is mounted in a central, continuous bore 31 of the hydraulic body 16 and delimits a pressure space 32 there.
  • a deep, axially extending annular groove 34 is also formed, in which a compression spring 35 is arranged, which is located on the Bottom of the flange part 14 supports and always brings the coupling member 20 into contact with the piston 29.
  • a plurality of eccentric, but concentric and axially running bores 36 are formed in the hydraulic body 16, in which pump bodies 37 are arranged, which receive pistons 39 in their bores 38. These are supported with their tips on an inclined swash plate 40 which bears against an inclined, annular web surface 41 of a plate 42 fixed to the housing. From this it can be seen that this is an axial piston pump 43.
  • Each pump body 37 has two web-like extensions 44 45 which engage in corresponding recesses 46, 47 of the swash plate 40.
  • a channel 51 leads into the pressure chamber 32 from a point behind the outlet valve.
  • annular groove 53 opens into which a transverse bore 54 arranged in the pump body 37 opens, which in turn leads into a longitudinal groove 55 on the outer circumference of the pump body and adjacent the hydraulic body 16 lying.
  • the longitudinal groove 55 in turn opens into an angled channel 56, which has a connection to an annular space 57 in the hydraulic body 16. From the annular space 57 there is a connection to the straight toothing 22, 23 on the coupling member 20 via the helical teeth 25, 26 and a subsequent channel 58.
  • an annular groove 59 is formed, into which a transverse bore 60 arranged in the camshaft 10 opens, which in turn has a connection to a transverse bore 61 in the camshaft bearing block 11. There is a connection from the transverse bore 61 to an oil reservoir 63 via a bore 62 formed in the cylinder head.
  • a solenoid valve 65 connects to the pressure chamber 32 and operates in a flow-proportional manner and thus forms a proportional pressure control valve.
  • This has a coil 66, which is arranged in a coil body 67, which simultaneously forms a cover 68.
  • the armature 69 in which a plunger 70 is fixed, is located within the coil former 67. This slides in a pole disk 71, which in turn rests on a plate 72 closing the bore 31.
  • a through hole 73 is formed in this, which is monitored by the spherical valve body 74 of the electromagnetic valve 65 or actuated by the plunger 70.
  • transverse channel 77 - that is to say it is arranged at the outlet of the solenoid valve - and opens into the recess 78 in the hydraulic body 16.
  • the pump bodies 37 are held in place by screws 76 which penetrate the flange part 14, the chain wheel 15 and the hydraulic body 16. So that the camshaft 10 can rotate relative to the sprocket 15, bushes 75 penetrated by these sprockets through the sprocket 17 are arranged on the passages of the screws 17, 76 and lie in corresponding arcuate slots 75 A of the sprocket.
  • the hydraulic control device works as follows: when the camshaft 10 is set in rotation by the chain wheel 15, the flange part 14 and the hydraulic body 16 also rotate.
  • the pistons 39 of the axial piston pump now carry out stroke movements 40 due to their abutment on the swash plate. They suck in pressure medium from the container 63 via the following connection: transverse bores 62, 61, 60, annular groove 59, straight toothing 22, 23, channel 58, helical toothing 25, 26, annular space 57 in the hydraulic body 16, channel 56, longitudinal groove 55, transverse bore 54 and annular groove 53 on the piston bore 38.
  • the compression spring 35 displaces the coupling member 20 to the left (in the direction of the solenoid valve 65), the camshaft 10 being rotated relative to the sprocket 15 via the toothings described. It takes a first position. With the solenoid valve energized to the maximum, the valve body 74 is pressed onto its valve seat by the action of the armature 69 and the plunger 70. The pressure in the pressure chamber 32 then reaches its maximum value and shifts the piston 29 to the right, which in turn moves the coupling member 20 the toothing described above, the camshaft 10 is now rotated relative to the sprocket 15 in a second position. When the solenoid valve is partially steamed, the coupling element can be brought into any intermediate position and thus also the camshaft.
  • the exemplary embodiment according to FIG. 2 differs from the previous one essentially in that the hydraulic body is designed somewhat differently. It now consists of two parts 80, 81, of which part 81 directly adjoins and is screwed to the camshaft, and part 80 - referred to here as a pump body - is also screwed to the camshaft. (Here, however, the screws are the other way around, but this is not essential to the invention at all.)
  • the pump body 80 is not rotationally symmetrical and consists of a sleeve which - as stated above - is screwed to the camshaft by screws.
  • the pump body has only been dealt with briefly, since its internal structure again largely resembles that of the previous exemplary embodiment. The same parts as there are labeled with the same numbers. What is different is the supply and discharge of the pressure medium to the pump body.
  • a spring washer 82 is arranged between the pump body 80 and the part 81, as is shown in plan view in FIG. 3. At the same time, it forms the outlet valve in the form of a spring tongue 83, which has a thickening 84 at its end, which bears against the outlet bore 85 of the piston bore 86.
  • the spring washer is held by a fixing pin, not shown.
  • the suction bore 87 runs in the pump body 80, in which there is also a suction throttle 88, which is connected to the bore 87 A in the Spring washer 82 is connected.
  • the suction bore 87 leads to the space 57, which is connected to the pressure medium reservoir.
  • the outlet bore 85 has a connection to the pressure chamber 32 via a channel 89.
  • a wire clamp 91 is provided which holds the swash plate with the pump pistons under spring pressure in the preassembled adjusting unit. However, this has not been discussed further.
  • the solenoid valve - designated 93 - is also slightly modified compared to the exemplary embodiment according to FIG. 1.
  • a longitudinal groove 95 is formed in the coil former 94.
  • Voltage can also be applied to the solenoid valves described in both exemplary embodiments with a frequency of approximately one hundred Hertz and a variable pulse duty factor.
  • Duty cycle is understood to mean the ratio of the duration of energization of the electromagnet to the total period of the applied voltage. With a small duty cycle, the solenoid valve is only closed briefly. The opening cross-section at the same time falls with the duty cycle.

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)
  • Reciprocating Pumps (AREA)

Abstract

Système de commande hydraulique pour la rotation de l'arbre à cames (10) d'un moteur à combustion interne. La roue à chaîne (15) entraînée par le moteur à combustion interne est reliée à l'arbre à cames (10) par le biais d'un élément d'accouplement (20), d'une denture hélicoïdale (25, 26) et d'une denture droite (22, 23). Le déplacement de l'élément d'accouplement (20) engendre une rotation relative entre la roue à chaîne (15) et l'arbre à cames (10). Le déplacement de l'élément d'accouplement s'opère par l'intermédiaire d'un piston hydraulique (29) actionné par une pompe à pistons axiaux (36) à (40), logée dans le système de commande. Cette pompe à pistons axiaux aspire le liquide de pression dans un réservoir situé dans le moteur à combustion interne et l'achemine par des soupapes de sortie (50) à la chambre de pression (32) au niveau du piston (29). Ce dernier est raccordé à une soupape de refoulement proportionnelle (65) que l'on peut actionner de manière électromagnétique et qui est commandée par l'actionnement approprié de l'électro-aimant, augmentant ainsi ou réduisant la pression à l'intérieur de la chambre de pression (32). Le pilotage de la pression dans la chambre de pression provoque la mise en rotation relative de l'élément d'accouplement (20) et de l'arbre à cames (10) par rapport à la roue à chaîne (15).
EP92918639A 1991-10-26 1992-09-04 Systeme de commande hydraulique Expired - Lifetime EP0572578B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4135378A DE4135378A1 (de) 1991-10-26 1991-10-26 Hydraulische steuereinrichtung
DE4135378 1991-10-26
PCT/DE1992/000741 WO1993008378A1 (fr) 1991-10-26 1992-09-04 Systeme de commande hydraulique

Publications (2)

Publication Number Publication Date
EP0572578A1 true EP0572578A1 (fr) 1993-12-08
EP0572578B1 EP0572578B1 (fr) 1995-12-06

Family

ID=6443495

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92918639A Expired - Lifetime EP0572578B1 (fr) 1991-10-26 1992-09-04 Systeme de commande hydraulique

Country Status (5)

Country Link
US (1) US5311846A (fr)
EP (1) EP0572578B1 (fr)
JP (1) JP3342869B2 (fr)
DE (2) DE4135378A1 (fr)
WO (1) WO1993008378A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0571472B1 (fr) * 1991-02-20 1995-05-03 ITT Automotive Europe GmbH Systeme hydraulique
IT1259099B (it) * 1992-05-19 1996-03-11 Carraro Spa Variatore di fase
DE4237193A1 (de) * 1992-11-04 1994-05-05 Bosch Gmbh Robert Verfahren zur Ansteuerung einer Einrichtung zum relativen Verdrehen einer Welle und Einrichtung zum relativen Verdrehen der Welle einer Brennkraftmaschine
DE4240075C2 (de) * 1992-11-28 2002-08-29 Bosch Gmbh Robert Hydraulische Stelleinrichtung
DE10038354C2 (de) * 2000-08-05 2003-03-20 Atlas Fahrzeugtechnik Gmbh Steuereinrichtung zum Verstellen des Drehwinkels einer Nockenwelle
DE10236507A1 (de) * 2002-08-09 2004-02-19 Aft Atlas Fahrzeugtechnik Gmbh Steuereinrichtung zum Verstellen des Drehwinkels einer Nockenwelle
US6883479B2 (en) * 2002-11-04 2005-04-26 Borgwarner Inc. VCT phaser having an electromagnetic lock system for shift and lock operation
DE102004041232B4 (de) * 2004-08-26 2017-07-13 Schaeffler Technologies AG & Co. KG Verfahren zum Betrieb eines Nockenwellenverstellers
DE102009037260B4 (de) 2009-08-12 2018-05-17 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
WO2012150077A1 (fr) 2011-05-02 2012-11-08 Magna Powertrain Ag & Co Kg Dispositif de lubrification

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB855582A (en) * 1958-08-27 1960-12-07 Lucas Industries Ltd Plungers for oil pumps or motors of the swash plate type
DE3247916A1 (de) * 1982-12-24 1984-06-28 Robert Bosch Gmbh, 7000 Stuttgart Vorrichtung zur steuerung der ventile einer brennkraftmaschine ueber eine nockenwelle
DE3929623A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Brennkraftmaschine mit nockenwellen und einer drehwinkelverstell-vorrichtung
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
JP2760619B2 (ja) * 1990-01-30 1998-06-04 株式会社ユニシアジェックス 内燃機関のバルブタイミング制御装置
JP2889633B2 (ja) * 1990-02-28 1999-05-10 株式会社ユニシアジェックス 内燃機関のバルブタイミング制御装置
JPH0436004A (ja) * 1990-05-31 1992-02-06 Atsugi Unisia Corp 内燃機関のバルブタイミング制御装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9308378A1 *

Also Published As

Publication number Publication date
DE4135378A1 (de) 1993-04-29
JPH06503629A (ja) 1994-04-21
WO1993008378A1 (fr) 1993-04-29
DE59204606D1 (de) 1996-01-18
US5311846A (en) 1994-05-17
EP0572578B1 (fr) 1995-12-06
JP3342869B2 (ja) 2002-11-11

Similar Documents

Publication Publication Date Title
EP0812390B1 (fr) Systeme de production de haute pression pour systeme d'injection de carburant monte dans un moteur a combustion interne
EP0564609B1 (fr) Systeme de commande hydraulique
DE3930157A1 (de) Einrichtung zur verstellung der drehwinkelzuordnung einer nockenwelle zu ihrem antriebselement
DE4213038C1 (fr)
EP0564610B1 (fr) Systeme de commande hydraulique
EP0572578A1 (fr) Systeme de commande hydraulique.
DE19757871A1 (de) Hubkolbenmaschine, insbesondere Brennkraftmaschine
DE4240075C2 (de) Hydraulische Stelleinrichtung
EP0609233B1 (fr) Organe de reglage hydraulique
EP0573622B1 (fr) Dispositif de commande hydraulique
DE2928584C2 (fr)
DE3138640C2 (fr)
DE69000833T2 (de) Vorrichtung zur verstellung des vorhubs einer kraftstoffeinspritzpumpe.
DE4037089C2 (de) Hydraulische Einrichtung zum Verdrehen der Nockenwelle einer Brennkraftmaschine
EP0543805A1 (fr) Pompe d'injection de carburant pour moteurs a combustion interne.
DE3841382C1 (fr)
DE4210742A1 (de) Hydraulische Steuereinrichtung
DE102016117874A1 (de) Umschaltventil zum Steuern eines Hydraulikflüssigkeitsstroms und Pleuel mit einem Umschaltventil
EP0877163B1 (fr) Pompe d'injection de combustible
DE19960569A1 (de) Pumpe für variable Lieferung mit fester Verdrängung
EP1277955B1 (fr) Pompe haute-pression à plongeur
DE19854766A1 (de) Kraftstoffeinspritzpumpe
DE4137073A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE817226C (de) Brennstoff-Einspritzpumpe
DE1938135C3 (de) Vorrichtung zum stufenlosen Einstellen und Regeln des Hubvolumens von Hydromaschinen

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: 19930911

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19941019

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59204606

Country of ref document: DE

Date of ref document: 19960118

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960213

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
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: FR

Payment date: 20030819

Year of fee payment: 12

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

Ref country code: GB

Payment date: 20030917

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: 20031029

Year of fee payment: 12

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

Ref country code: GB

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

Effective date: 20040904

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: 20050401

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20040904

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: 20050531

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

Effective date: 20050904