EP0761936A2 - 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
EP0761936A2
EP0761936A2 EP96112593A EP96112593A EP0761936A2 EP 0761936 A2 EP0761936 A2 EP 0761936A2 EP 96112593 A EP96112593 A EP 96112593A EP 96112593 A EP96112593 A EP 96112593A EP 0761936 A2 EP0761936 A2 EP 0761936A2
Authority
EP
European Patent Office
Prior art keywords
pressure
connection
actuating unit
valve piston
valve
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
EP96112593A
Other languages
German (de)
English (en)
Other versions
EP0761936A3 (fr
EP0761936B1 (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 ANTRIEBS- und STEUERUNGSTECHNIK GmbH
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 ANTRIEBS- und STEUERUNGSTECHNIK GmbH, Hydraulik Ring GmbH filed Critical HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK 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 actuation unit for an 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 the coupling element, which, if necessary, is displaced hydraulically in such a way that an adjusting element forming a fixed component, which is assigned to a second cam of the camshaft, is coupled to a control element.
  • the corresponding valve lifter of the motor vehicle performs a modified stroke, as a result of which the opening cross section is changed, so that a particularly metered amount of the fuel-air mixture can flow into the cylinder space of the engine.
  • the hydraulic medium must be pressurized by means of a pump. There is a brief drop in pressure within the system until the pump has built up the required hydraulic pressure. Then there is a risk that the coupling element is not pushed far enough into the locking hole and there is frequent wear on the bolt edge with increased surface pressure and increased wear.
  • the invention has for its object to design the generic actuating unit so that the coupling element is suddenly moved into its coupling position, without the risk that there is power transmission on a narrow edge area of the coupling element.
  • the actuation unit according to the invention has two tank connections, one of which is pressure-relieved and the other is pressure-loaded.
  • the hydraulic medium When moving the valve piston, the hydraulic medium is discharged via the pressure-relieved tank connection until shortly before the end position is reached, since it is connected to the work connection.
  • the hydraulic medium can be displaced quickly in this way.
  • the pressure relief valve of the pressure-loaded tank connection ensures that a residual pressure determined by the pressure relief valve remains in the entire system, thereby reliably preventing the system from running dry. If the coupling process is to be triggered, a correspondingly large amount of hydraulic medium can thus be made available suddenly, so that a drop in pressure at the start of the coupling process is reliably avoided.
  • the coupling element is therefore suddenly moved into its coupling position. It doesn't happen a power transmission on a narrow edge area of the coupling element.
  • the actuation unit is preferably provided for the valve lift adjustment of motor vehicles.
  • cams of a camshaft interact with rocker arms or hydraulic cups as control elements, which act directly on the respective valve tappet.
  • the valves are opened and closed controlled by the corresponding cams.
  • the actuation unit can be used in the low-pressure range in systems with residual pressure.
  • FIG. 2 schematically shows a valve lift adjustment device which is operated with the actuation unit according to FIG. 1 becomes.
  • a coupling element 1 designed as a piston is slidably mounted in a fixed component 2.
  • a movable component 3 is provided adjacent to this, in which a piston 4 is slidably mounted. 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 to one another, the coupling element 1 is acted upon hydraulically, as a result of which it is shifted to the right in FIG. 2 and pushes the piston 4 back against the force of the spring 5. The coupling element 1 is displaced until it engages in a bore 6 receiving the piston 4. Then both parts are positively connected to one another transversely to the axis of the coupling element 1 and the piston 4.
  • the actuating unit according to FIG. 1 is used for hydraulic loading of the coupling element 1. It is designed as a switching valve and has a housing 7 in which a valve piston 8 is displaceably mounted. It is slidably mounted in a bore 9 into which a pressure connection 10, a working connection 11, a pressure-relieved tank connection 12 and a pressure-loaded tank connection 13 open.
  • the working connection 11 is connected to the pressure connection 10 via a throttle point 14.
  • the diameter play of the valve piston 8 in the bore 9 could also be used as the throttle point 14a. In this case, the throttle point 14 would not be required.
  • the hydraulic medium could also get from the pressure connection 10 to the working connection 11.
  • the pressure-loaded tank connection 13 is closed against the tank (not shown) by a pressure relief valve 15 which opens in the direction of the tank.
  • the valve piston 8 can be axially displaced by a plunger 16 of an electromagnet 26 against the force of at least one spring 18 in the bore 9.
  • the valve piston 8 has two annular grooves 20 and 21 which are separated from one another by an annular web 19.
  • the annular groove 20 is connected by a radial bore 22 to a bore 23 axially penetrating the valve piston 8. These bores 22 and 23 serve to hydraulically relieve the space 24 and 25 located in front of and behind the valve piston 8.
  • the resulting leakage oil is discharged via the bores 22, 23, the annular groove 21 and the tank connections 12 and 13.
  • valve piston 8 In Fig. 1 the valve piston 8 is shown in the upper half in its open position, in which the electromagnet 26 is energized and the plunger 16 is extended, so that the valve piston 8 is displaced against the force of the compression spring 18.
  • the pressure connection 10 and the working connection 11 are connected to the annular groove 20, while the working connection 11 is separated from the pressure-relieved tank connection 12 and from the pressure-loaded tank connection 13 by the ring web 19 of the valve piston 8.
  • the working connection 11 is also connected to the pressure connection 10 via the throttle point 14.
  • valve piston 8 In the lower half of FIG. 1, the valve piston 8 is shown in its closed position, in which the electromagnet 26 is not energized.
  • the plunger 16 is retracted while the valve piston 8 has been pushed back into its closed position by the force of the spring 18.
  • the working connection 11 In this switching position, the working connection 11 is connected to the pressure-loaded tank connection 13 via the annular groove 21.
  • the hydraulic medium can 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 compensates for leaks, for example caused by lubrication points. From the working connection 11, the hydraulic medium can flow back to the tank via the annular groove 21 of the valve piston 8 and the tank connection 13.
  • a working line 30 (FIG. 2) of the fixed component 2 is connected to the working connection 11, so that the coupling element 1 is also under this prestressing pressure of the hydraulic medium.
  • this pressure is less than the counterforce exerted by the compression spring on the piston 4 and thus on the coupling element 1.
  • the coupling element 1 remains in its stop position shown in FIG. 2, in which it bears against the bottom 31 of a bore 32 which receives the coupling element.
  • the valve piston 8 has at its end facing the compression spring 18 a further annular web 27 which, together with the annular web 19, axially delimits the annular groove 21.
  • the ring web 27 closes the pressure-relieved tank connection 12.
  • the tank connection 12 is only partially closed by the ring web 27.
  • the valve piston 8 moves back from the open position into the closed position, the hydraulic medium is displaced freely via the pressure-relieved tank connection 12 until the valve piston 8 has almost completely reached its end position (lower half in FIG. 1). Only then is the pressure-relieved tank connection 12 separated from the annular groove 21 by the ring web 27, while the pressure-loaded one Tank connection 13 is connected via the annular groove 21 to the working connection 11.
  • valve piston 8 Since the hydraulic medium is displaced freely when returning via the pressure-relieved tank connection 12, the valve piston 8 can be reliably moved back into its closed position by the compression spring 18, in which it separates the pressure connection 10 from the working connection 11 with its annular web 19.
  • valve piston 8 has an axially penetrating end bore 28, which acts as a throttle point and is designed as a nozzle. It opens into the central axial bore 23.
  • the throttle point 28 can of course be of any other suitable design, for example formed by reducing the diameter of the bore 23.
  • control edges 33, 34 and 35 which interact with corresponding control edges 33a to 35a of the housing 7.
  • These control edges 33a to 35a are provided on the working connection 11 and on the pressure-relieved tank connection 12.
  • the control edges 33 to 35 and 33a to 35a are designed with respect to one another in such a way that the overlap is very slight and is therefore referred to as a zero cut.
  • valve piston 8 If the valve piston 8 is in its closed position (lower half in FIG. 1), then the working connection 11 is connected to the pressure-loaded tank connection 13 via the annular groove 21.
  • the pressure relief valve 15 ensures that the entire system even in this non-switched state of the actuating unit has corresponding residual pressure. This prevents the system from running dry in the closed position of the valve piston 8.
  • valve piston 8 If the valve piston 8 is pushed back into its open position by the tappet 16, the annular web 27 releases the pressure-relieved tank connection 12 after the shortest displacement path, so that the hydraulic medium can be discharged to the tank immediately via this tank connection 12. In the end position, the ring web 19 then separates the working connection 11 from the tank connection 12.
  • the actuation unit is designed as a cartridge valve.
  • the electromagnet 26 is firmly connected to the housing 7 and is used as a unit in a corresponding component 36.
  • the actuating 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 is seated, and the Throttle point 14.
  • the valve piston 8 is moved by the plunger 16 of the electromagnet 26 from its closed position (right half in FIG. 3) against the force of the compression spring 18 into the open position, which is shown in FIG. 3 in the left half. In this open position of the valve piston 8, the pressure connection 10 is connected via the annular groove 20 to the working connection 11, which is separated from the two tank connections 12, 13 by the annular webs 19, 27 of the valve piston 8.
  • the pressure-loaded tank connection 13 lies in the axial direction of the valve piston 8 and of the electromagnet 26. However, this does not change the mode of operation of the actuating unit. Otherwise, this embodiment works the same as the embodiment of FIG. 1.
  • the valve piston 8 If the electromagnet 26 is switched off and the plunger 16 is retracted, the valve piston 8 is pushed back into its closed position under the force of the compression spring 18.
  • the ring land 27 of the valve piston 8 does not initially close the pressure-relieved tank connection 12 when the valve piston 8 is pushed back, so that the displaced hydraulic medium can be rapidly discharged to the tank via this tank connection 12. Only shortly before the valve piston 8 reaches its closed position (right half in Fig. 3), the pressure-relieved tank connection 12 is closed by the ring web 27.
  • the pressure relief valve 15 ensures that the system has a corresponding residual pressure even when the electromagnet 26 is not energized, so that the system is prevented from running dry.
  • Fig. 3 an embodiment is shown with dashed lines, in which the throttle point between the pressure port 10 and the working port 11 is not provided in the housing 7, but in the component 36.
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 true EP0761936A2 (fr) 1997-03-12
EP0761936A3 EP0761936A3 (fr) 1998-01-21
EP0761936B1 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

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPS60240813A (ja) * 1984-05-14 1985-11-29 Honda Motor Co Ltd バルブ休止機能付動弁装置
US5537963A (en) * 1994-09-02 1996-07-23 Honda Giken Kogyo Kabushiki Kaisha Valve operating system for multi-cylinder internal combustion engine

Family Cites Families (6)

* 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
US4525695A (en) * 1984-04-04 1985-06-25 Parker Hannifin Corporation Force motor with ball mounted armature
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 Gmbh Elektroproportionalmagnet-Ventileinheit
US5598871A (en) * 1994-04-05 1997-02-04 Sturman Industries Static and dynamic pressure balance double flow three-way control valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPS60240813A (ja) * 1984-05-14 1985-11-29 Honda Motor Co Ltd バルブ休止機能付動弁装置
US5537963A (en) * 1994-09-02 1996-07-23 Honda Giken Kogyo Kabushiki Kaisha Valve operating system for multi-cylinder internal combustion engine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 109 (M-472), 23.April 1986 & JP 60 240813 A (HONDA GIKEN KOGYO KK), 29.November 1985, *
PATENT ABSTRACTS OF JAPAN vol. 9, no. 235 (M-415), 21.September 1985 & JP 60 090906 A (HONDA GIKEN KOGYO KK), 22.Mai 1985, *

Also Published As

Publication number Publication date
DE19531444A1 (de) 1997-02-27
EP0761936A3 (fr) 1998-01-21
DE59606295D1 (de) 2001-02-15
US5732612A (en) 1998-03-31
EP0761936B1 (fr) 2001-01-10
JPH09105302A (ja) 1997-04-22
ES2153064T3 (es) 2001-02-16

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