EP0761936B1 - Unité d'actionnement pour un dispositif de réglage, de préférence pour un dispositif de variation de la levée des soupapes d'un moteur à combustion interne - Google Patents

Unité d'actionnement pour un dispositif de réglage, de préférence pour un dispositif de variation de la levée des soupapes d'un moteur à combustion interne Download PDF

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Publication number
EP0761936B1
EP0761936B1 EP96112593A EP96112593A EP0761936B1 EP 0761936 B1 EP0761936 B1 EP 0761936B1 EP 96112593 A EP96112593 A EP 96112593A EP 96112593 A EP96112593 A EP 96112593A EP 0761936 B1 EP0761936 B1 EP 0761936B1
Authority
EP
European Patent Office
Prior art keywords
connection
actuating unit
pressure
valve piston
adjusting device
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
EP96112593A
Other languages
German (de)
English (en)
Other versions
EP0761936A3 (fr
EP0761936A2 (fr
Inventor
Katja Schienle
Wolfgang Stephan
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring 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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP0761936A2 publication Critical patent/EP0761936A2/fr
Publication of EP0761936A3 publication Critical patent/EP0761936A3/fr
Application granted granted Critical
Publication of EP0761936B1 publication Critical patent/EP0761936B1/fr
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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to an actuating unit for a Adjustment device, preferably for a valve lift adjustment device of motor vehicles, according to the preamble of claim 1.
  • valve lift adjustment devices of motor vehicles it is known to use a bolt as a coupling element use that hydraulically shifted if necessary is that an adjusting element forming a fixed component, the second cam of the camshaft is associated with a control element.
  • the corresponding valve lifter leads the motor vehicle has a modified stroke, whereby the opening cross section is changed so that a particularly appropriate amount of the fuel-air mixture can flow into the cylinder space of the engine.
  • the hydraulic medium pressurized by means of a pump become. There is a brief drop in pressure inside of the system until the pump reaches the required Has built up hydraulic pressure. Then there is a risk that the coupling element is not far enough into the locking hole is inserted and so it is carried too often on the bolt edge with increased surface pressure and increased Wear comes.
  • An actuation unit according to the preamble of claim 1 is from US-A-5 537 963 known.
  • the invention has for its object the generic Train the actuator so that the coupling element abruptly in its clutch position is moved without the risk of that it is for power transmission on a narrow edge area of the coupling element comes.
  • the actuation unit according to the invention has two tank connections on, one of which relieves pressure and the other is under pressure.
  • the hydraulic medium can be quickly displaced in this way become.
  • Through the pressure relief valve of the pressure-loaded tank connection ensures that in the entire system through the pressure relief valve certain residual pressure remains, causing an idle of the system is safely prevented.
  • Should the coupling process can be triggered accordingly large amount of hydraulic medium suddenly Be made available, so that a drop in pressure Start of the coupling process reliably avoided becomes.
  • the coupling element is suddenly in his clutch position shifted. It doesn't happen a power transmission on a narrow edge area of the coupling element.
  • the actuation unit is preferably for valve lift adjustment provided by motor vehicles.
  • Valve stroke adjustment devices act on cams Camshaft with rocker arms or hydraulic cups as control elements together, directly on the respective Act on valve tappet.
  • the valves are on the corresponding Controlled opening and closing of the cams.
  • the actuator can be in the low pressure range used in systems with residual pressure become.
  • FIG. 2 schematically shows a valve lift adjustment device, which is operated with the actuation unit according to FIG. 1 becomes.
  • a coupling element designed as a piston 1 is slidably mounted in a fixed component 2.
  • a movable component 3 is adjacent to this provided, in which a piston 4 is slidably mounted is. It is under the force of at least one compression spring 5 or a hydraulic pressure.
  • the coupling element 1 In order to couple the two components 2 and 3 together, the coupling element 1 is acted upon hydraulically, whereby it is shifted to the right in Fig. 2 and the Pushes piston 4 back against the force of spring 5. The Coupling element 1 is moved until it is in engages a piston 6 receiving bore 6. Then are both parts transverse to the axis of the coupling element 1 and the piston 4 positively connected to each other.
  • the coupling element 1 serves the actuating unit according to FIG. 1. It is as Switch valve formed and has a housing 7 in which a valve piston 8 is slidably mounted. He is in a bore 9 slidably mounted, in which a pressure connection 10, a working connection 11, a pressure-relieved Tank connection 12 and a pressure-loaded tank connection 13 flow out.
  • the work connection 11 is a Throttle point 14 connected to the pressure port 10.
  • Throttle point 14a could also be the diameter play of the Valve piston 8 can be used in the bore 9. In in this case the throttle point 14 would not be required.
  • the pressure-loaded tank connection 13 is against the tank (not shown) through a pressure relief valve 15 closed that towards the Tank opens.
  • the valve piston 8 can by a plunger 16 Electromagnets 26 against the force of at least one spring 18 are axially displaced in the bore 9.
  • the Valve piston 8 has two through an annular web 19 from each other separate ring grooves 20 and 21.
  • the ring groove 20 is through a radial bore 22 with a valve piston 8 axially penetrating bore 23 connected. These holes 22 and 23 are used for hydraulic relief of the in front of and behind the valve piston 8 space 24 and 25.
  • the leakage oil is discharged through the holes 22, 23, the annular groove 21 and the tank connections 12 and 13 dissipated.
  • valve piston 8 In Fig. 1 the valve piston 8 is in the upper half shown in its open position, in which the Electromagnet 26 excited and the plunger 16 extended is so that the valve piston 8 against the force of Compression spring 18 is moved.
  • the pressure connection 10 and the working connection 11 are connected to the annular groove 20, during the working connection 11 from the pressure-relieved Tank connection 12 and from the pressure-loaded tank connection 13 is separated by the annular web 19 of the valve piston 8.
  • the working connection 11 is located via the throttle point 14 also in connection with the pressure connection 10.
  • the valve piston 8 is in the lower half of FIG. 1 shown in its closed position, in which the Electromagnet 26 is not excited.
  • the plunger 16 is retracted while the valve piston 8 by force the spring 18 pushed back into its closed position has been.
  • the working connection is in this switch position 11 via the annular groove 21 with the pressure load Tank connection 13 connected.
  • the hydraulic medium can be in this closed position via the throttle 14 from the work connection 11 get into the pressure port 10. This Measure prevents the system from idling while the engine is running. This will cause leaks, for example through lubrication points. From the work connection 11 can the hydraulic medium via the annular groove 21 of the valve piston 8 and flow back the tank connection 13 to the tank.
  • a work line 30 is at the work connection 11 (Fig. 2) of the fixed component 2 connected, so that the coupling element 1 under this bias pressure of the hydraulic medium. However, this pressure is less than that of the compression spring on the Piston 4 and thus exerted on the coupling element 1 Drag. As a result, the coupling element 1 remains in its stop position shown in Fig. 2, in the it on the bottom 31 of a receiving the coupling element Bore 32 is present.
  • the valve piston 8 has on its the compression spring 18 facing End another ring land 27 that together with the annular web 19, the annular groove 21 axially limited.
  • the ring web 27 closes the pressure-relieved Tank connection 12.
  • the open position (upper Half in Fig. 1) is the tank connection 12 through the Ring web 27 only partially closed.
  • the hydraulic medium is relieved of pressure Tank connection 12 displaced freely as long as until the valve piston 8 almost reaches its end position (lower Half in Fig. 1) has reached completely. Only is the pressure-relieved tank connection 12 through the ring land 27 separated from the annular groove 21, while the pressure-loaded Tank connection 13 via the annular groove 21 with the Work port 11 communicates.
  • the valve piston has damping during the switching process 8 an axially penetrating end bore 28, which acts as a throttle and designed as a nozzle is. It opens into the central axial bore 23.
  • the throttle point 28 can of course any have other appropriate training, for example through a reduction in the diameter of the bore 23 is formed become.
  • These control edges 33a to 35a are at the work connection 11 and provided on the pressure-relieved tank connection 12.
  • the control edges 33 to 35 and 33a to 35a are like this to each other that the coverage is very low and is therefore referred to as a zero cut.
  • valve piston 8 is in its closed position (lower half in Fig. 1), then the work connection 11 with the pressure-loaded tank connection 13 via the annular groove 21 connected.
  • the pressure relief valve 15 ensures that the entire system in this a not switched state of the actuating unit has corresponding residual pressure. This will make a System idle in the valve piston closed position 8 prevented.
  • valve piston 8 is in again by the plunger 16 the ring bridge gives its open position 27 the pressure relieved after the shortest displacement Tank connection 12 free, so that the hydraulic medium over this tank connection 12 are immediately discharged to the tank can. In the end position, the ring web 19 then separates the Working connection 11 from the tank connection 12.
  • the actuating unit 3 is the actuating unit designed as a cartridge valve.
  • the electromagnet 26 is firmly connected to the housing 7 and will used as a unit in a corresponding component 36.
  • the actuation unit also has the pressure connection 10, the working connection 11, the pressure-relieved Working connection 12, the pressure-loaded tank connection 13, in which the pressure relief valve 15 sits, and the Throttle point 14.
  • the valve piston 8 is through the tappet 16 of the electromagnet 26 from its closed position (right half in Fig. 3) against the force of the compression spring 18 moved to the open position, which in Fig. 3 in the left half is shown. In this open position of the valve piston 8 is the pressure connection 10 via the Annular groove 20 connected to the working connection 11, the through the annular webs 19, 27 of the valve piston 8 of the two tank connections 12, 13 is separated.
  • the pressure-loaded tank connection 13 is different to the previous embodiment in the axial direction of the valve piston 8 and the electromagnet 26. On the mode of operation the actuation unit changes as a result however nothing. Otherwise, this embodiment works the same as the exemplary embodiment according to FIG. 1.
  • valve piston 8 If the electromagnet 26 is switched off and thus the Plunger 16 retracted, the valve piston 8 under pushed back the force of the compression spring 18 in its closed position.
  • the ring web 27 of the valve piston 8 closes the pressure-relieved tank connection 12 when pushing back of the valve piston 8 initially not, so that the displaced hydraulic medium through this tank connection 12 can be quickly discharged to the tank.
  • the pressure-relieved tank connection 12 closed by the ring land 27 Just before the valve piston 8 reaches its closed position (right Half in Fig. 3), the pressure-relieved tank connection 12 closed by the ring land 27.
  • the pressure relief valve 15 ensures that even when not excited Electromagnet 26 the system a corresponding residual pressure has, so that an idling of the system prevents becomes.
  • Fig. 3 is an embodiment with dashed lines shown, in which the throttle point between the Pressure connection 10 and the working connection 11 are not in the housing 7, but is provided in component 36.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Handcart (AREA)

Claims (7)

  1. Unité d'actionnement pour un dispositif de réglage, de préférence pour un dispositif de variation de la levée des soupapes de véhicules automobiles, comportant au moins un élément d'accouplement auquel peuvent être accouplés un composant stationnaire et un composant mobile du dispositif de réglage et qui est réglable par voie hydraulique par l'intermédiaire d'au moins un piston de soupape de l'unité d'actionnement, au moyen duquel au moins un raccord de travail peut être séparé vis-à-vis d'un raccord de pression dans une position de fermeture, caractérisée en ce que l'unité d'actionnement comprend un raccord de réservoir (12) déchargé de pression et un raccord de réservoir (13) chargé en pression et pourvu d'une soupape de limitation de pression (15), en ce que le raccord de réservoir (12) déchargé de pression est relié au raccord de travail (11) lors du déplacement du piston de soupape (8) jusqu'à peu avant d'atteindre la position de fin de course respective, et en ce que dans la position de fermeture, le raccord de travail (11) est relié au raccord de réservoir (13) chargé en pression.
  2. Unité d'actionnement selon la revendication 1, caractérisée en ce que le piston de soupape (8) comprend une portée annulaire (27) qui sépare le raccord de réservoir (12) déchargé de pression vis-à-vis du raccord de travail (11) dans la position de fermeture du piston de soupape (8).
  3. Unité d'actionnement selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que le piston de soupape (8) comprend une autre portée annulaire (19) qui sépare le raccord de pression (10) vis-à-vis du raccord de travail (11) dans la position de fermeture du piston de soupape (8).
  4. Unité d'actionnement selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le raccord de pression (10) est relié au raccord de travail (11) via un étranglement (14).
  5. Unité d'actionnement selon la revendication 4, caractérisée en ce que l'étranglement (14) est prévu dans un carter (7) de l'unité d'actionnement.
  6. Unité d'actionnement selon la revendication 4, caractérisée en ce que l'étranglement (14) est prévu dans un composant (36) recevant le carter (7) de l'unité d'actionnement.
  7. Unité d'actionnement selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le piston de soupape (8) comprend au moins un étranglement (28) qui relie une chambre hydraulique (24) à un perçage axial (23) du piston de soupape (8) en avant du piston de soupape (8).
EP96112593A 1995-08-26 1996-08-03 Unité d'actionnement pour un dispositif de réglage, de préférence pour un dispositif de variation de la levée des soupapes d'un moteur à combustion interne Expired - Lifetime EP0761936B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19531444 1995-08-26
DE19531444A DE19531444A1 (de) 1995-08-26 1995-08-26 Betätigungseinheit für eine Verstelleinrichtung, vorzugsweise für eine Ventilhubverstelleinrichtung von Kraftfahrzeugen

Publications (3)

Publication Number Publication Date
EP0761936A2 EP0761936A2 (fr) 1997-03-12
EP0761936A3 EP0761936A3 (fr) 1998-01-21
EP0761936B1 true EP0761936B1 (fr) 2001-01-10

Family

ID=7770471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96112593A Expired - Lifetime EP0761936B1 (fr) 1995-08-26 1996-08-03 Unité d'actionnement pour un dispositif de réglage, de préférence pour un dispositif de variation de la levée des soupapes d'un moteur à combustion interne

Country Status (5)

Country Link
US (1) US5732612A (fr)
EP (1) EP0761936B1 (fr)
JP (1) JPH09105302A (fr)
DE (2) DE19531444A1 (fr)
ES (1) ES2153064T3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005028805A1 (de) * 2005-06-22 2007-01-04 GM Global Technology Operations, Inc., Detroit Einrichtung zur hydraulischen Ventilhubumschaltung
US10731519B2 (en) * 2018-09-19 2020-08-04 Hyundai Motor Company Control system and control method for hydraulic variable valve
CN110966062B (zh) * 2018-09-30 2022-09-27 现代自动车株式会社 用于液压可变阀的控制系统和控制方法

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3224119A1 (de) * 1982-06-29 1983-12-29 Robert Bosch Gmbh, 7000 Stuttgart Hydraulisches elektromagnetisch betaetigtes schieberventil
JPS6090906A (ja) * 1983-10-25 1985-05-22 Honda Motor Co Ltd エンジンにおけるバルブ作動可変装置
US4525695A (en) * 1984-04-04 1985-06-25 Parker Hannifin Corporation Force motor with ball mounted armature
JPS60240813A (ja) * 1984-05-14 1985-11-29 Honda Motor Co Ltd バルブ休止機能付動弁装置
US4971114A (en) * 1988-11-21 1990-11-20 Diesel Kiki Co., Ltd. Electromagnetic proportional pressure control valve
JP2853237B2 (ja) * 1990-02-09 1999-02-03 住友電気工業株式会社 液圧制御装置
DE9402206U1 (de) * 1994-02-10 1994-05-05 Hydraulik-Ring Antriebs- und Steuerungstechnik GmbH, 72622 Nürtingen Elektroproportionalmagnet-Ventileinheit
US5598871A (en) * 1994-04-05 1997-02-04 Sturman Industries Static and dynamic pressure balance double flow three-way control valve
JP3373947B2 (ja) * 1994-09-02 2003-02-04 本田技研工業株式会社 多気筒内燃機関の動弁装置

Also Published As

Publication number Publication date
US5732612A (en) 1998-03-31
ES2153064T3 (es) 2001-02-16
DE59606295D1 (de) 2001-02-15
JPH09105302A (ja) 1997-04-22
EP0761936A3 (fr) 1998-01-21
EP0761936A2 (fr) 1997-03-12
DE19531444A1 (de) 1997-02-27

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