EP0572578A1 - Hydraulic control device. - Google Patents

Hydraulic control device.

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)
French (fr)
Other versions
EP0572578B1 (en
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/en
Application granted granted Critical
Publication of EP0572578B1 publication Critical patent/EP0572578B1/en
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)
  • Reciprocating Pumps (AREA)
  • Valve Device For Special Equipments (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).Hydraulic control system for the rotation of the camshaft (10) of an internal combustion engine. The chain wheel (15) driven by the internal combustion engine is connected to the camshaft (10) by means of a coupling element (20), of a helical toothing (25, 26) and straight teeth (22, 23). The movement of the coupling element (20) generates a relative rotation between the chain wheel (15) and the camshaft (10). The displacement of the coupling element takes place by means of a hydraulic piston (29) actuated by an axial piston pump (36) to (40), housed in the control system. This axial piston pump draws the pressure liquid from a reservoir located in the internal combustion engine and routes it through outlet valves (50) to the pressure chamber (32) at the piston (29). The latter is connected to a proportional discharge valve (65) which can be actuated electromagnetically and which is controlled by the appropriate actuation of the electromagnet, thereby increasing or reducing the pressure inside the pressure chamber (32). Piloting the pressure in the pressure chamber causes the coupling element (20) and the camshaft (10) to rotate relative to the chain wheel (15).

Description

Hydraulische SteuereinrichtungHydraulic control device
Stand der TechnikState of the art
Die Erfindung geht aus von einer hydraulischen Steuereinrichtung zum Verdrehen der Nockenwelle einer Brennkraftmaschine nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten Steuereinrichtung sind insbesondere die Pumpe und das Magnetventil extern angeordnet, was verhältnismäßig umständlich ist, insbesondere hinsichtlich der notwendigen Druckmittelverbindungen, aber auch einen erheblichen Bauaufwand bedingt (DE-OS 32 47 916).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. In such a known control device, in particular 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).
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäß hydraulische Steuereinrichtung mit den kenn¬ zeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vor¬ teil, daß sie sehr kompakt baut und sehr einfach in eine Brennkraft¬ maschine bzw. in deren Motorraum zu installieren ist. Weitere Vor¬ teile der Erfindung ergeben sich aus den Unteransprüchen. ZeichnungIn contrast, 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
Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Be¬ schreibung und Zeichnung näher erläutert. Letztere zeigt einen Längsschnitt in Figur 1 eines ersten Ausführungsbeispiels einer hy¬ draulischen Steuereinrichtung zum Verdrehen der Nockenwelle einer Brennkraftmaschine, in. Figur 2 eine Abwandlung dieses Ausführungs¬ beispiels und in Figur 3 eine Einzelheit.An embodiment of the invention is explained in more detail in the following description and drawing. The latter 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.
Beschreibung des AusführungsbeispielesDescription of the embodiment
In der Zeichnung ist mit 10 die Nockenwelle einer Brennkraftmaschine bezeichnet, welche im Nockenwellenlagerbock 11 der Brennkraftma¬ schine gelagert ist. Die Nockenwelle hat eine durchgehende Längs— bohrung 12, in welche der hülsenförmige Fortsatz 13 eines etwa becherförmig ausgebildeten Flanschteils 14 hineinragt. An die Stirn¬ seite des Flanschteils schließt sich ein Kettenrad 15 für den An¬ trieb der Nockenwelle 12 an, auf dieses folgt ein Zylinde förmiger Hydraulikkörper 16. Die Teile 12 bis 16 sind durch Schrauben 17 drehfest zusammengehalten. Die genannten Teile bilden einen innen¬ liegenden Hohlraum 18, in dem ein Koppelglied 20 angeordnet ist. Dieses hat einen Schaft 21, welcher in den Fortsatz 13 des Flansch¬ teils 14 hineinragt. Am Außenumfang des Schafts 21 ist eine Gerad¬ verzahnung 22 ausgebildet, welche mit einer eben solchen Geradver¬ zahnung 23 am Innenumfang des hülsenförmigen Fortsatzes in Eingriff steht. Auf den Schaft 21 des Koppelgliedes 20 folgt als integrales Teil ein becherförmiges Ringteil 24, das an seinem Außenumfang eine Schrägverzahnung 25 aufweist, die mit einer eben solchen Schrägver¬ zahnung 26 am Innenumfang des Kettenrades 15 in Eingriff steht. In die Höhlung 28 des Koppelgliedes bzw. dessen Ringteiles 24 taucht ein Kolben 29, welcher sich stets gegen den Boden 30 des Koppel¬ gliedes legt. Der Kolben 29 ist in einer mittigen, durchgehenden Bohrung 31 des Hydraulikkörpers 16 gelagert und begrenzt dort einen Druckraum 32. Im Ringteil 24 des Koppelgliedes 20 ist noch eine tiefe, axial verlaufende Ringnut 34 ausgebildet, in welcher eine Druckfeder 35 angeordnet ist, welche sich am Boden des Flanschteiles 14 abstützt und das Koppelglied 20 stets in Berührung mit dem Kolben 29 bringt.In the drawing, 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. In the ring part 24 of the coupling member 20, 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.
Im Hydraulikkörper 16 sind mehrere außermittige, aber konzentrische und axial verlaufende Bohrungen 36 ausgebildet, in denen Pumpen¬ k rper 37 angeordnet sind, die in ihren Bohrungen 38 Kolben 39 auf¬ nehmen. Diese stützen sich mit ihren Kuppen auf einer schräg liegen¬ den Taumelscheibe 40 ab, die an einer schräg verlaufenden, ring¬ förmigen Stegfläche 41 einer gehäusefesten Platte 42 anliegt. Daraus ist zu erkennen, daß es sich hier um eine Axialkolbenpumpe 43 han¬ delt. Jeder Pumpenkörper 37 hat zwei stegartige Fortsätze 44 45, die in entsprechende Ausnehmmungen 46, 47 der Taumelscheibe 40 hinein¬ greifen. Wenn also der Hydraulikkörper 16 beim Antrieb durch das Kettenrad 15 rotiert, führt auch die Taumelscheibe 40 eine taumelnde Rotationsbewegung aus. An der Stegfläche 41 sind zweckmäßigerweise weiter nicht dargestellte Schmiernuten ausgebildet.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. Thus, when the hydraulic body 16 rotates when driven by the chain wheel 15, the swash plate 40 also performs a wobbling rotational movement. Lubrication grooves, not shown, are expediently formed on the web surface 41.
An die den Kolben 39 aufnehmende Bohrung 38 schließt sich eine Bohrung 49 mit geringerem Durchmesser an, in welcher ein Ausla߬ ventil 50 angeordnet ist, auf dessen Aufbau nicht näher eingegangen ist, da üblich. Von einer Stelle hinter dem Auslaßventil führt ein Kanal 51 in den Druckraum 32.At the bore 38 receiving the piston 39 there is a bore 49 with a smaller diameter, in which an outlet valve 50 is arranged, the construction of which has not been discussed in detail, since it is common. A channel 51 leads into the pressure chamber 32 from a point behind the outlet valve.
An der Kolbenbohrung 38 mündet eine Ringnut 53, in welche eine im Pumpenkörper 37 angeordnete Querbohrung 54 mündet, diese wiederum in eine Längsnut 55 am Außenumfang des Pumpenkörpers und angrenzend an den Hydraulikkörper 16 liegend. Die Längsnut 55 mündet wiederum in einen abgewinkelten Kanal 56, der Verbindung hat zu einem Ringraum 57 im Hydraulikkörper 16. Vom Ringraum 57 besteht über die Schräg¬ verzahnung 25, 26 und einen sich anschließenden Kanal 58 Verbindung zur Geradverzahnung 22, 23 am Koppelglied 20. Am Innenumfang des Fortsatzes 13 des Flanschteiles 14 ist eine Ringnut 59 ausgebildet, in welche eine in der Nockenwelle 10 angeordnete Querbohrung 60 mün¬ det, welche wiederum Verbindung zu einer Querbohrung 61 im Nocken- wellenlagerbock 11 hat. Von der Querbohrung 61 besteht über eine im Zylinderkopf ausgebildete Bohrung 62 Verbindung zu einem Ölbehälter 63.At the piston bore 38 an 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. On the inner circumference of the extension 13 of the flange part 14, 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.
An den Druckraum 32 schließt sich ein Magnetventil 65 an, das strom¬ proportional arbeitet und damit ein Proportionaldrucksteuerventil bildet. Dieses weist eine Spule 66 auf, die in einem Spulenkörper 67 angeordnet ist, der gleichzeitig einen Deckel 68 bildet. Innerhalb des Spulenkörpers 67 befindet sich der Anker 69, in dem ein Stößel 70 fest angeordnet ist. Dieser gleitet in einer Polscheibe 71, die wiederum an einer die Bohrung 31 verschließenden Platte 72 anliegt. In dieser ist eine durchgehende Bohrung 73 ausgebildet, die vom kugeligen Ventilkörper 74 des Elektromagnetventils 65 überwacht bzw. vom Stößel 70 betätigt wird. Zwischen Platte 72 und Polplatte 61 be¬ findet sich ein quer verlaufender Kanal 77 - er ist also am Ausgang des Elektromagnetventils angeordnet - und mündet in die Ausnehmung 78 im Hyraulikkörpers 16. Von dem dort gelegenen Raum 79 besteht ebenfalls Verbindung zum Behälter 63. Weiter nicht bezeichnete Bohrungen und Kanäle, zum Beispiel im Schaft 21 des Koppelgliedes, haben keine erfindungsgemäße Bedeutung.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. Between plate 72 and pole plate 61 there is a 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. There is also a connection to the container 63 from the space 79 located there designated bores and channels, for example in the shaft 21 of the coupling member, have no meaning according to the invention.
Es ist noch zu erwähnen, daß die Pumpenkörper 37 fesgehalten werden durch Schrauben 76, welche das Flanschteil 14, das Kettenrad 15 und den Hydraulikkörper 16 durchdringen. Damit sich die Nockenwelle 10 relativ gegenüber dem Kettenrad 15 verdrehen kann, sind an den Durchgängen der Schrauben 17, 76 durch das Kettenrad von diesen Schrauben durchdrungene Buchsen 75 angeordnet, welche in entsprech¬ enden bogenförmigen Schlitzen 75 A des Kettenrades liegen.It should also be mentioned that 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.
Die hydraulische Steuereinrichtung arbeitet wie folgt: wenn die Nockenwelle 10 durch das Kettenrad 15 in Rotation versetzt wird, drehen sich auch das Flanschteil 14 und der Hydraulikkörper 16 mit. Die Kolben 39 der Axialkolbenpumpe führen nun durch ihre Anlage an der Taumelscheibe 40 Hubbewegungen aus. Sie saugen Druckmittel aus dem Behälter 63 an über die folgende Verbindung: Querbohrungen 62, 61, 60, Ringnut 59, Geradverzahnung 22, 23, Kanal 58, Schrägver¬ zahnung 25, 26, Ringraum 57 im Hydraulikkörper 16, Kanal 56, Längs¬ nut 55, Querbohrung 54 und Ringnut 53 an der Kolbenbohrung 38.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.
Bei stromlosem Magnetventil 65 wird der Ventilkörper 74 von seinem Ventilsitz abgehoben, und das von den Kolben 39 über das Ausla߬ ventil 50 in den Druckraum 32 geförderte Druckmittel wird über das Magnetventil, die Querbohrung 77 und die Ausnehmung 78 drucklos zum Raum 79 bzw. zum Behälter 63 ausgeschoben.When the solenoid valve 65 is de-energized, the valve body 74 is lifted from its valve seat, and the pressure medium conveyed into the pressure chamber 32 by the piston 39 via the outlet valve 50 is depressurized to the chamber 79 and / or to the chamber 79 and the recess 78 via the solenoid valve Container 63 pushed out.
Die Druckfeder 35 verschiebt das Koppelglied 20 nach links (in Richtung zum Magnetventil 65), wobei über die beschriebenen Ver¬ zahnungen die Nockenwelle 10 gegenüber dem Kettenrad 15 verdreht wird. Sie nimmt eine erste Stellung ein. Bei maximal bestromtem Magnetventil wird der Ventilkörper 74 durch die Wirkung des Ankers 69 und des Stößels 70 auf seinen Ventilsitz gedrückt. Daraufhin er¬ reicht der Druck im Druckraum 32 seinen Maximalwert und verschiebt den Kolben 29 nach rechts, dieser wiederum das Koppelglied 20. Durch die oben beschriebenen Verzahnungen wird nun die Nockenwelle 10 gegenüber dem Kettenrad 15 in eine zweite Position verdreht. Bei Teilbestrohmung des Magnetventils kann das Koppelglied in beliebige Zwischenstellungen gebracht werden und damit auch die Nockenwelle.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.
Das Ausführungsbeispiel nach Figur 2 unterscheidet sich von dem vor¬ herigen im wesentlichen dadurch, daß der Hydraulikkörper etwas an¬ ders ausgebildet ist. Er besteht nun aus zwei Teilen 80, 81, wovon sich der Teil 81 unmittelbar an die Nockenwelle anschließt und mit dieser verschraubt ist, und das Teil 80 - hier als Pumpenkörper be¬ zeichnet - ebenfalls mit der Nockenwelle verschraubt ist. (Hier liegen jedoch die Schrauben anders herum, was jedoch überhaupt nicht erfindungswesentlich, ist.)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.)
Der Pumpenkörper 80 ist nicht drehsymmetrisch ausgebildet und be¬ steht aus einer Hülse, die - wie oben ausgeführt - durch Schrauben mit der Nockenwelle verschraubt ist. Auf den Pumpenkörper ist nur kurz eingegangen, da er in seinem inneren Aufbau wieder weitgehend dem— jenigen nach dem vorigen Ausführungsbeispiel gleicht. Gleiche Teile wie dort sind auch hier mit den selben Ziffern bezeichnet. Was unterschiedlich ist, ist die Zu- und Abführung des Druckmittels zum Pumpenkörper.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.
Zwischen dem Pumpenkörper 80 und dem Teil 81 ist eine Federscheibe 82 angeordnet, wie sie in Figur 3 in Draufsicht dargestellt ist. Sie bildet gleichzeitig das Auslaßventil in Form einer Federzunge 83, welche an ihrem Ende eine Verdickung 84 hat, die an der Ausla߬ bohrung 85 der Kolbenbohrung 86 anliegt. Die Federscheibe ist durch einen nicht weiter dargestellten Fixierstift festgehalten. In der Federscheibe befindet sich auch eine Bohrung 87 A. Im Pumpenkörper 80 verläuft die Saugbohrung 87, in welcher sich noch eine Saug¬ drossel 88 befindet, welche mit der Bohrung 87 A in der Federscheibe 82 verbunden ist. Die Saugbohrung 87 führt bis zum Raum 57, der mit dem Druckmittelreservoir in Verbindung steht. Die Auslaßbohrung 85 hat über einen Kanal 89 Verbindung zum Druckraum 32. Um den oder die Pumpenkörper 80 leicht montieren zu können, ist eine Drahtklammer 91 vorgesehen, welche die Taumelscheibe mit den unter Federdruck stehenden Pumpenkolben in der vormontierten Ver¬ stelleinheit festhält. Hierauf ist aber weiter nicht eingegangen.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. There is also a bore 87 A in the spring washer. 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. In order to be able to easily mount the pump body (s) 80, 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.
Auch das Elektromagnetventil - bezeichnet mit 93 - ist geringfügig modifiziert gegenüber dem Ausführungsbeispiel nach Figur 1. Neben dem Anker 69 ist im Spulenkörper 94 eine Längsnut 95 ausgebildet. Dadurch werden bei Drehung von Nockenwelle und Anker in dem erregten Elektromagneten in ersterem Wirbelströme induziert, die ein Brems¬ moment auf den Anker ausüben. Die Aufhängung des Ankers am Stößel 70 und die Kraftweiterleitung auf den Ventilkörper 74 lassen eine Drehung von Anker und Magnetkern zu. Der sich drehende Stößel hat bei axialer Bewegung fast keine Reibkraft. Dadurch wird das Elektro¬ magnetventil hysteresearm, wodurch sich der Druck im Druckraum 32 besonders genau einstellen läßt.The solenoid valve - designated 93 - is also slightly modified compared to the exemplary embodiment according to FIG. 1. In addition to the armature 69, a longitudinal groove 95 is formed in the coil former 94. As a result, when the camshaft and armature rotate, eddy currents are induced in the excited electromagnet and exert a braking torque on the armature. The suspension of the armature on the plunger 70 and the transmission of force to the valve body 74 allow the armature and the magnetic core to rotate. The rotating plunger has almost no friction when moving axially. As a result, the solenoid valve becomes low in hysteresis, as a result of which the pressure in the pressure chamber 32 can be set particularly precisely.
An die in beiden Ausführungsbeispielen beschriebenen Magnetventile kann auch mit einer Frequenz von etwa hundert Hertz und variierbarem Tastverhältnis Spannung angelegt werden. Unter Tastverhältnis ver¬ steht man das Verhältnis von Bestromungsdauer des Elektromagneten zur Gesamtperiodendauer der angelegten Spannung. Bei kleinem Tast¬ verhältnis wird das Magnetventil jeweils nur kurz geschlossen. Der zeitlich ge ittelte Öffnungsquerschnitt fällt mit dem Tastverhältnis. 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.

Claims

Ansprüche Expectations
1. Hydraulische Steuereinrichtung zum Verdrehen der Nockenwelle (10) einer Brennkraftmaschine mittels eines durch Druckkraft längsver- schieblichen Koppelgliedes (20), das an einer ersten Stelle an seinem Außenumfang eine Verzahnung (22) aufweist, die mit einer ebensolchen Verzahnung (23) am Innenumfang der Nockenwelle (10) in Eingriff steht und das mit einem Ende in einem von der Brennkraft¬ maschine angetriebenen, hohlzylindrischen Kettenrad (15) gelagert ist, das eine mittige Bohrung aufweist, die an ihrem Innenumfang eine Verzahnung (25) hat, welche mit einer ebensolchen Verzahnung (26) an einer zweiten Stelle des Außenumfanges des Koppelgliedes (20) in Eingriff steht, wobei eine der Verzahnungspaarungen eine Schrägverzahnung ist, die andere eine Geradverzahnung und wobei das Koppelglied durch einen von einem Magnetventil (65) gesteuerten Flüssigkeitsdruck axial verschiebbar ist und dadurch eine relative Verdrehung der Nockenwelle (10) gegenüber dem Kettenrad (15) hervor¬ ruft, dadurch gekennzeichnet, daß der Flüssigkeitsdruck einen auf das Koppelglied (20) einwirkenden Kolben (29) beaufschlagt, daß an das An- triebsrad (15), an das auch die Nockenwelle (10) angeschlossen ist, ein Hydraulikkörper (16) angeflanscht ist, in dem eine Axialkolben- pumpe (43) angeordnet ist, die mehrere in axialen Bohrungen (38) gleitende Kolben (39) aufnimmt, deren außenliegende Kuppen an einer Taumelscheibe (40) anliegen, daß an der Auslaßsseite der Bohrungen (38) Auslaßventile (50) angeordnet sind, von denen eine Verbindung (51) besteht zu dem vom Kolben (29) begrenzten Druckraum (32), dessen Druck vom Magnetventil (65) gesteuert wird, und daß auf das Koppelglied (20) eine entgegen der Krafteinwirkung des Kolbens (29) eine mechanische Kraft einwirkt.1. Hydraulic control device for rotating the camshaft (10) of an internal combustion engine by means of a coupling member (20) which is longitudinally displaceable by pressure force and which has a toothing (22) at a first point on its outer circumference, which has such toothing (23) on the inner circumference the camshaft (10) is in engagement and is supported at one end in a hollow cylindrical sprocket (15) driven by the internal combustion engine, which has a central bore which has a toothing (25) on its inner circumference which is connected to a the same toothing (26) is engaged at a second location on the outer circumference of the coupling member (20), one of the toothing pairs being a helical toothing, the other a straight toothing and the coupling member being axially displaceable by a fluid pressure controlled by a solenoid valve (65) and this results in a relative rotation of the camshaft (10) relative to the chain wheel (15) uft, characterized in that the liquid pressure acts on a piston (29) acting on the coupling member (20), that a hydraulic body (16) is flanged to the drive wheel (15) to which the camshaft (10) is also connected , in which an axial piston pump (43) is arranged, which receives several pistons (39) sliding in axial bores (38), the outer ones Bumps rest on a swash plate (40) that outlet valves (50) are arranged on the outlet side of the bores (38), of which there is a connection (51) to the pressure chamber (32) delimited by the piston (29), the pressure from the solenoid valve (65) is controlled, and that a mechanical force acts on the coupling member (20) against the force of the piston (29).
2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die die Kolben (39) aufnehmenden Bohrungen (38) in Pumpenkörpern (37) gleiten, welche in axial verlaufenden Bohrungen (36) des Hydraulik¬ körpers (16) ausgebildet sind und konzentrisch zu dessen Längsachse verlaufen.2. Device according to claim 1, characterized in that the pistons (39) receiving bores (38) slide in pump bodies (37) which are formed in axially extending bores (36) of the Hydraulik¬ body (16) and concentric to it Longitudinal axis.
3. Einrichtung nach Anspruch 1 und 2, dadurch gekennzeichnet, daß die Pumpenkörper (37) stegartige Verlängerungen (44, 45) aufweisen, mit welchen sie in Ausnehmungen (46, 47) der Taumelscheibe ein¬ tauchen.3. Device according to claim 1 and 2, characterized in that the pump body (37) have web-like extensions (44, 45) with which they dip into recesses (46, 47) of the swash plate.
4. Einrichtung nach einem der Ansprüche 1 bis 3, dadurch gekenn¬ zeichnet, daß zwischen die Nockenwelle (10) und das Kettenrad (15) ein Zwischenteil (14) eingeschaltet ist, das einen in eine Längs¬ bohrung (12) der Nockenwelle (10) tauchenden Fortsatz (13) hat, an dessen Innenumfang die Geradverzahnung (22) ausgebildet ist.4. Device according to one of claims 1 to 3, characterized gekenn¬ characterized in that between the camshaft (10) and the sprocket (15), an intermediate part (14) is switched on, one in a longitudinal bore (12) of the camshaft ( 10) has a diving extension (13), on the inner circumference of which the straight toothing (22) is formed.
5. Einrichtung nach einem der Ansprüche 1 bis 4, dadurch gekenn¬ zeichnet, daß die Nockenwelle (10) ein erweitertes, flanschartiges Endteil (10 A) aufweist, an welchen sich das Zwischenteil (14) an¬ schließt, achsgleich dazu das Kettenrad (15) und ebenfalls achs¬ gleich dazu der Hydraulikkörper (16) und daß diese Teile durch Schrauben (17, 76) miteinander verbunden sind. - 10 -5. Device according to one of claims 1 to 4, characterized gekenn¬ characterized in that the camshaft (10) has an expanded, flange-like end part (10 A), to which the intermediate part (14) connects, coaxially with the sprocket ( 15) and likewise axially the hydraulic body (16) and that these parts are connected to one another by screws (17, 76). - 10 -
6. Einrichtung nach, einem der Ansprüche 1 bis 5, dadurch, gekenn¬ zeichnet, daß das Elektromagnetventil (65) achsgleich zum Hydraulik¬ körper (16) angeordnet ist und teilweise innerhalb desselben liegt.6. Device according to, one of claims 1 to 5, characterized, gekenn¬ characterized in that the electromagnetic valve (65) is arranged coaxially with the hydraulic ¬ body (16) and is partially within the same.
7. Einrichtung nach Anspruch 1, dadurch gekennzeichnet,, daß der Hydraulikkörper aus zwei Teilen besteht, nämlich einem unmittelbar sich an das Kettenrad (15) anschließenden ersten Körper (81), an welchen wenigstens ein Pumpenkörper (80) angeschlossen ist, der mittels einer das erweiterte Endteil der Nockenwelle, das Kettenrad und den ersten Körper (81) durchdringenden Schraube festgehalten ist, und daß zwischen dem Pumpenkörper (80) und dem ersten Körper (81) eine Federscheibe (82) angeordnet ist, welche ein zungenartiges Ventilteil (83) mit einer Verdickung (84) aufweist, welche an der Auslaßbohrung (85) liegt.7. Device according to claim 1, characterized in that the hydraulic body consists of two parts, namely a directly to the sprocket (15) adjoining the first body (81) to which at least one pump body (80) is connected, which by means of a the extended end part of the camshaft, the sprocket and the first body (81) penetrating screw is held, and that between the pump body (80) and the first body (81) a spring washer (82) is arranged, which a tongue-like valve part (83) has a thickening (84) which lies on the outlet bore (85).
8. Einrichtung nach Anspruch 7, dadurch gekennzeichnet, daß an dem den Anker (69) aufnehmenden Spulenkörper eine Längsnut (95) ausge¬ bildet ist.8. Device according to claim 7, characterized in that a longitudinal groove (95) is formed on the coil body receiving the armature (69).
9. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die mechanische Kraft durch, eine Feder (35) erzeugt wird.9. Device according to claim 1, characterized in that the mechanical force is generated by a spring (35).
10. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die mechanische Kraft durch die Schrägverzahnung am Koppelglied (20) er¬ zeugt wird, deren Steigungswinkel etwa 30 - 45° beträgt. 10. The device according to claim 1, characterized in that the mechanical force is generated by the helical teeth on the coupling member (20) er¬ whose pitch angle is about 30 - 45 °.
EP92918639A 1991-10-26 1992-09-04 Hydraulic control device Expired - Lifetime EP0572578B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4135378 1991-10-26
DE4135378A DE4135378A1 (en) 1991-10-26 1991-10-26 HYDRAULIC CONTROL DEVICE
PCT/DE1992/000741 WO1993008378A1 (en) 1991-10-26 1992-09-04 Hydraulic control device

Publications (2)

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

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US (1) US5311846A (en)
EP (1) EP0572578B1 (en)
JP (1) JP3342869B2 (en)
DE (2) DE4135378A1 (en)
WO (1) WO1993008378A1 (en)

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DE59202093D1 (en) * 1991-02-20 1995-06-08 Teves Gmbh Alfred HYDRAULIC SYSTEM.
IT1259099B (en) * 1992-05-19 1996-03-11 Carraro Spa PHASE VARIATOR
DE4237193A1 (en) * 1992-11-04 1994-05-05 Bosch Gmbh Robert Method for controlling a device for the relative rotation of a shaft and device for the relative rotation of the shaft of an internal combustion engine
DE4240075C2 (en) * 1992-11-28 2002-08-29 Bosch Gmbh Robert Hydraulic actuator
DE10038354C2 (en) * 2000-08-05 2003-03-20 Atlas Fahrzeugtechnik Gmbh Control device for adjusting the angle of rotation of a camshaft
DE10236507A1 (en) * 2002-08-09 2004-02-19 Aft Atlas Fahrzeugtechnik Gmbh Controller for adjusting camshaft rotation angle relative to crankshaft, has mechanical arrangement for limiting adjustment of rotation angle arranged between crankshaft and camshaft
US6883479B2 (en) * 2002-11-04 2005-04-26 Borgwarner Inc. VCT phaser having an electromagnetic lock system for shift and lock operation
DE102004041232B4 (en) * 2004-08-26 2017-07-13 Schaeffler Technologies AG & Co. KG Method for operating a camshaft adjuster
DE102009037260B4 (en) 2009-08-12 2018-05-17 Schaeffler Technologies AG & Co. KG Device for changing the relative angular position of a camshaft relative to a crankshaft of an internal combustion engine
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Also Published As

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

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