EP1568851B1 - Hydraulisches Ventilspielausgleichselement - Google Patents

Hydraulisches Ventilspielausgleichselement Download PDF

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Publication number
EP1568851B1
EP1568851B1 EP04100730A EP04100730A EP1568851B1 EP 1568851 B1 EP1568851 B1 EP 1568851B1 EP 04100730 A EP04100730 A EP 04100730A EP 04100730 A EP04100730 A EP 04100730A EP 1568851 B1 EP1568851 B1 EP 1568851B1
Authority
EP
European Patent Office
Prior art keywords
plunger
chamber
oil
lash adjuster
hydraulic lash
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
EP04100730A
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English (en)
French (fr)
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EP1568851A1 (de
Inventor
Axel Berndorfer
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to AT04100730T priority Critical patent/ATE435359T1/de
Priority to EP04100730A priority patent/EP1568851B1/de
Priority to DE602004021767T priority patent/DE602004021767D1/de
Publication of EP1568851A1 publication Critical patent/EP1568851A1/de
Application granted granted Critical
Publication of EP1568851B1 publication Critical patent/EP1568851B1/de
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
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/0005—Deactivating valves

Definitions

  • the present invention generally relates to a hydraulic lash adjuster, in particular the one used as fixedly mounted pivot point in a valve train using rocker arm assemblies with integrated switching function.
  • hydraulic lash adjusters are mainly used to take up clearance within the valve train and to control the actuation of the rocker arms switching function.
  • the HLA comprises a cylindrical body with a plunger chamber and a hollow plunger cap which is reciprocally mounted within this plunger chamber in the body.
  • the upper part of the plunger cap protrudes out of the body and there is an oil bore in this upper part to communicate with the hollow interior of the plunger cap.
  • Oil ports are arranged in side walls of the cap and body to supply oil from the engine to the hollow interior of the plunger cap.
  • the HLA further comprises a high-pressure chamber between the lower end of the plunger cap and the bottom of the plunger chamber. This high-pressure chamber is connected to the hollow interior of the plunger chamber via an oil passage provided with a check valve to prevent the return flow of oil into the hollow plunger cap.
  • the end of the plunger cap engages into a socket in the rocker arm.
  • the lash adjuster will receive pressurized oil from the engine lubricating pump through an oil gallery and this oil will pass through the oil ports in the body and plunger cap to reach the hollow plunger interior.
  • Actuation of the rocker arm switching function is conducted by raising the oil pressure high enough in the oil feed gallery to still maintain lash adjustment but also to actuate the two-step rocker arm by moving a lock mechanism (switching device) within the rocker arm.
  • a problem with such an HLA is linked to the fact that high oil pressure in the engine is limited, especially under hot idle conditions. Therefore, current control schemes only dispose of small pressure variations for the actuating function of the HLA, making the actuation slow, insecure and with lots of variations.
  • US 5,452,694 discloses an HLA comprising a hollow piston, one end of which is hemispherical shaped to engage a rocker arm while its opposite end is sealed by a plug.
  • the piston defines a piston chamber having a lateral oil port and an oil bore in the hemispherical end.
  • the piston is reciprocally mounted in a lash cylinder, and cooperates therein with a separate sleeve-like member to define a chamber.
  • the sleeve-like member features a lateral oil port and comprises a valve port in its lower end.
  • EP 0 899 429 describes an HLA with a single-chamber plunger, wherein the plunger comprises one piece, deep drawn, stamped metal member.
  • the object of the present invention is to provide an improved hydraulic lash adjuster. This object is achieved by a hydraulic lash adjuster as claimed in claim 1.
  • the HLA of the invention allows a separate and independent control of the lash adjustment function and the actuating/switching function.
  • the lash adjustment is achieved by supplying oil to the second chamber in order to fill the high-pressure chamber and thereby move the hollow plunger to adjust the valve lash.
  • controlled oil pressure is fed to the first chamber in order to supply oil at controlled pressure to an associated rocker arm with integrated switching device via the oil bore in the protruding upper plunger part.
  • the pressure in the second chamber may thus typically be that of the engine lubrication circuit, which is susceptible to uncontrolled variations e.g. due to engine temperature, ambient temperature, engine speed, etc.
  • the oil pressure in the first chamber is preferably controlled to vary between predetermined pressures in order to permit switching of the latch (switching device) in the rocker arm assembly. Due to the use of two separate chambers, the oil pressure In the first chamber can be controlled independently from the second chamber, which is typically fed from the engine lubrication circuit. As a result, the present HLA permits an enhanced switching control, that globally leads to improved valve timing control and engine operation
  • the partition wall is formed by an element that is press-fitted inside the hollow plunger. This is a simple way of dividing the interior of the hollow plunger into two chambers. It will however be understood that there are many different ways to design such a partition wall dividing the plunger interior into two chambers.
  • the partition wall could e.g. be integrally formed with the hollow plunger.
  • the partition wall may also be inserted in the plunger and secured therein by any suitable means.
  • the plunger is made from a generally cylindrical tube and the upper part ends by a semi-spherical nose in which the oil bore is provided.
  • the semi-spherical nose may be obtained by roll-forming.
  • the partition wall advantageously is a cup-shaped element that is press-fitted into the hollow plunger interior before roll-forming of the plunger nose.
  • plunger biasing means are provided to bias the hollow plunger in the outward direction for an improved lash adjustment
  • the plunger biasing means preferably comprise a spring arranged in the high-pressure chamber.
  • a check valve is preferably provided to prevent the return flow of oil from the high-pressure chamber into the second chamber.
  • This check valve may comprise a spring loaded ball in the high-pressure chamber case, the partition wall advantageously is a cup-shaped element that is press-fitted into the hollow plunger interior before roll-forming of the plunger nose.
  • plunger biasing means are provided to bias the hollow plunger in the outward direction for an improved lash adjustment.
  • the plunger biasing means preferably comprise a spring arranged in the high-pressure chamber.
  • a check valve is preferably provided to prevent the return flow of oil from the high-pressure chamber into the second chamber.
  • This check valve may comprise a spring loaded ball in the high-pressure chamber that cooperates with the valve seat in the oil passage leading from the high-pressure chamber to the second chamber.
  • the first and second oil ports are arranged in the lateral walls of the hollow plunger.
  • the body is provided for each oil port in the plunger with a respective oil bore in the lateral sides of the body.
  • These cooperating body bores and plunger ports are designed so as to overlap in any position of the plunger.
  • Fig. 1 shows a preferred embodiment of a hydraulic lash adjuster 10 in accordance with the invention that is located in a cylinder head 12 of an internal combustion engine.
  • a HLA 10 is typically provided as a complete assembly ready to be mounted in the cylinder head 12.
  • the HLA's 10 function is to take up clearance within the engine valve train and to control the actuation of switching device of the rocker arms of the valve train. Accordingly, the HLA 10 engages a socket 164 in a rocker arm assembly generally indicated 16, comprising inner and outer arms 162 and 163.
  • the rocker arm assembly 16 typically has an oil channel 161 that is supplied with pressurized oil from the HLA 10 and that leads from the socket 164 to a piston assembly (not shown) in order to actuate a latch (not shown) fixedly connected to the piston assembly.
  • the latch is moveable between two positions, which enables the rocker arm assembly 16 to be operated in a first and a second valve lift capability position.
  • the present HLA 10 comprises a body 18 of preferably cylindrical shape having a plunger chamber 19, in which a hollow plunger 20 is reciprocally mounted.
  • This hollow plunger 20 has an upper part 22 (i.e. the part directed towards the rocker arm assembly 16) that protrudes out of the cylindrical body 18 and that preferably ends by a semi-spherical nose shape.
  • the plunger nose 22 engages the socket 164 in the rocker arm assembly 16 and is provided with an oil bore 24.
  • the plunger 20 is preferably spring loaded by a cylindrical spring 26, which urges the hollow plunger 20 towards the rocker arm assembly 16.
  • the cylindrical spring 26 is located in a high-pressure chamber 28 in the lower part (away from the rocker arm assembly 16) of the HLA 10.
  • the high-pressure chamber 28 is actually defined by the lower end of the hollow plunger 20 and the closed bottom 30 of the cylindrical body 18.
  • a crimped flange 28 is advantageously arranged at the open end of the cylindrical body 18, this crimped flange 28 being typically put in place after the complete HLA has been assembled. This flange 28 also avoids any accidental dismounting of the HLA during handling.
  • the HLA 10 further comprises a partition wall 32 dividing the interior of the hollow plunger 20 into two chambers 34 and 36.
  • the first chamber 34 has a first oil port 38 and is in fluid communication with the oil bore 24 in the protruding plunger nose 22.
  • the second chamber 36 has a second oil port 40 and is connected to the high-pressure chamber via an oil passage 42.
  • Such a structure of the HLA 10 allows to separate the control of the lash adjusting function and the actuating function. Indeed, since the partition wall 32 divides the hollow plunger 20 into two chambers 34 and 36 hydraulically sealed from each other, the pressures in the two chambers 34, 36 can be controlled independently.
  • the body 18 has in its lateral side a first oil bore 44 that coincides with the first oil port 38 in the plunger 20 and is in fluid communication with a first oil gallery 46 in the cylinder head 12.
  • the body 18 further includes in its lateral side a second oil bore 48 that coincides with the second oil port 40 in the plunger 20 and is in fluid communication with a second oil gallery 50 in the cylinder head 12.
  • the coinciding oil ports and bores in plunger 22 and body 18 are designed so as to overlap in any axial position of the plunger 22.
  • each oil bore 44, 48 in the body 18 is in fluid communication with its respective oil gallery 46, resp. 50, via an annular groove 52, resp. 54, on the body's external surface.
  • the lash adjusting function of the HLA 10 is controlled by supplying pressurized oil to the second chamber 36 from the second oil gallery 50.
  • the hollow plunger 20 is urged towards the assembly 16 by the cylindrical spring 26 thereby suppressing any lash between the protruding upper part or nose 22 of the hollow plunger 20 and the assembly 16.
  • the second chamber 36 and the high-pressure chamber 28 are initially filled with pressurized oil from the second gallery 50.
  • a check-valve 56 is preferably provided in the oil passage 42 between the second chamber 36 and the high-pressure chamber 28 to prevent the return flow of oil into the second chamber 36.
  • the check valve 56 comprises a ball 58 urged by a spring (not shown) against an annular seat 60 formed at the beginning of the oil passage 42 when seen from the high-pressure chamber 28.
  • engine oil is fed to the second chamber 36 at standard pressures from the second oil gallery 50, as with conventional HLA, for the purpose of lash adjustment.
  • the oil delivered by the first oil gallery 46 is preferably controlled by means of a control solenoid.
  • the switching of the rocker arm would be performed by varying the pressure in this gallery 46 between a high pressure (e.g. engine oil pressure) and a low pressure (e.g. zero or very low controlled pressure).
  • a high pressure e.g. engine oil pressure
  • a low pressure e.g. zero or very low controlled pressure.
  • the control solenoid could either have a calibrated leak into this gallery or maintain some very low pressure level (e.g. 20kPa).
  • the hollow plunger is typically formed from a tubular body, the end of which is roll-formed so that it ends by the semi-spherical nose. Therefore, the partition wall 32 preferably is a cup-shaped element that is press-fitted into the hollow plunger 20 before the extremity of the latter is roll formed. This is a simple and cost efficient way to arrange the partition wall inside the plunger 20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Sliding Valves (AREA)

Claims (9)

  1. Hydraulischer Ventilspielausgleich für einen Ventiltrieb eines Verbrennungsmotors, der aufweist:
    einen Körper (18) mit einer Kolbenkammer (19);
    einem Hohlkolben (20), der reziprok in der Kolbenkammer (19) des Körpers (18) sitzt, wobei der Kolben (20) einen röhrenförmigen Teil und einen oberen Teil (22) mit einer Öl-Bohrung (24) hat, die aus der Kolbenkammer (19) hervorragt zum Aufnehmen einer Aufnahme (164) eines Kipphebels (16) eines Ventiltriebs;
    eine Hochdruckkammer (28), die zwischen dem unteren Ende des Kolbens (20) und der Unterseite der Kolbenkammer (19) angeordnet ist;
    eine erste Kammer (34) in dem röhrenförmigen Teil, wobei die erste Kammer (34) eine erste Öl-Öffnung (38) in der Wand des röhrenförmigen Teils hat und in Fluid-Kommunikation steht mit der Öl-Bohrung (24) in dem hervorragenden oberen Teil (22) des Hohlkolbens (20);
    dadurch gekennzeichnet, dass
    eine Trennwand (32) in dem röhrenförmigen Teil vorgesehen ist, um darin eine zweite Kammer (36) unter der ersten Kammer (34) zu definieren, wobei die zweite Kammer (36) versehen ist mit einer zweiten Öl-Öffnung (40) in der Wand des röhrenförmigen Teils und mit einem Ventilsitz (60), der einen Öl-Durchfluss (42) umgibt, zur Verbindung mit der Hochdruckkammer (28).
  2. Hydraulischer Ventilspielausgleich gemäß Anspruch 1, dadurch gekennzeichnet, dass die Trennwand (32) durch ein Element gebildet wird, das in den Hohlkolben (20) durch Pressen eingepasst wird.
  3. Hydraulischer Ventilspielausgleich gemäß Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Kolben (20) aus einer im Allgemeinen zylinderförmigen Röhre besteht und der obere Teil (22) in einer halbkugelförmigen Nase endet, in welcher die Öl-Bohrung (24) vorgesehen ist.
  4. Hydraulischer Ventilspielausgleich gemäß Anspruch 3, dadurch gekennzeichnet, dass die halbkugelförmige Nase (22) durch Rollformen eines Endes der Röhre gebildet wird.
  5. Hydraulischer Ventilspielausgleich gemäß einem der vorhergehenden Ansprüche, gekennzeichnet durch Kolben-Biasing-Mittel, um den Hohlkolben in die Richtung nach außen zu bringen.
  6. Hydraulischer Ventilspielausgleich gemäß Anspruch 5, dadurch gekennzeichnet, dass die Kolben-Biasing-Mittel eine Feder (26) aufweisen, die in der Hochdruckkammer angeordnet ist.
  7. Hydraulischer Ventilspielausgleich gemäß einem der vorhergehenden Ansprüche, gekennzeichnet durch ein Rückschlagventil (56) in dem Öl-Durchfluss (42) zwischen der zweiten Kammer (36) und der Hochdruckkammer (28), um einen Rückfluss von Öl in die zweite Kammer (36) zu vermeiden.
  8. Hydraulischer Ventilspielausgleich gemäß Anspruch 7, dadurch gekennzeichnet, dass das Rückschlagventil (56) eine Kugel aufweist, die mittels einer Feder gegen den Ventilsitz (60) gedrückt wird.
  9. Hydraulischer Ventilspielausgleich gemäß einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Körper (18) eine erste Öl-Zufuhr-Bohrung (44) hat, die zu der ersten Öl-Öffnung (38) des Hohlkolbens gehört; und der Körper (18) eine zweite Öl-Zufuhr-Bohrung (48) hat, die zu der zweiten Öl-Öffnung (40) des Hohlkolbens gehört.
EP04100730A 2004-02-25 2004-02-25 Hydraulisches Ventilspielausgleichselement Expired - Lifetime EP1568851B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT04100730T ATE435359T1 (de) 2004-02-25 2004-02-25 Hydraulisches ventilspielausgleichselement
EP04100730A EP1568851B1 (de) 2004-02-25 2004-02-25 Hydraulisches Ventilspielausgleichselement
DE602004021767T DE602004021767D1 (de) 2004-02-25 2004-02-25 Hydraulisches Ventilspielausgleichselement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04100730A EP1568851B1 (de) 2004-02-25 2004-02-25 Hydraulisches Ventilspielausgleichselement

Publications (2)

Publication Number Publication Date
EP1568851A1 EP1568851A1 (de) 2005-08-31
EP1568851B1 true EP1568851B1 (de) 2009-07-01

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Family Applications (1)

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EP04100730A Expired - Lifetime EP1568851B1 (de) 2004-02-25 2004-02-25 Hydraulisches Ventilspielausgleichselement

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EP (1) EP1568851B1 (de)
AT (1) ATE435359T1 (de)
DE (1) DE602004021767D1 (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005053596A1 (de) 2005-11-10 2007-05-16 Schaeffler Kg Schaltbarer Schlepphebel eines Ventiltriebs einer Brennkraftmaschine
DE102005056415A1 (de) * 2005-11-26 2007-05-31 Schaeffler Kg Verfahren zur Entlüftung einer Steuerdruckleitung
US20080035085A1 (en) * 2006-08-14 2008-02-14 Hendriksma Nick J Method and apparatus for controlling a switchable cam follower
US9157340B2 (en) * 2013-03-25 2015-10-13 GT Technologies Dual feed hydraulic lash adjuster for valve actuating mechanism
DE102014212272A1 (de) * 2014-06-26 2015-12-31 Schaeffler Technologies AG & Co. KG Abstützelement
US10544710B2 (en) 2015-03-23 2020-01-28 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
US9650922B2 (en) 2015-04-28 2017-05-16 Ford Global Technologies, Llc External oil groove on a hydraulic lash adjuster
US9765656B2 (en) 2015-06-15 2017-09-19 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
GB201522269D0 (en) * 2015-12-17 2016-02-03 Eaton Srl Hydraulic lash adjuster
JP7099260B2 (ja) * 2018-11-06 2022-07-12 トヨタ自動車株式会社 内燃機関の動弁システム

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0899429A1 (de) * 1997-08-28 1999-03-03 Eaton Corporation Hydraulisches Ventilspielausgleichselement

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4133332A (en) * 1977-10-13 1979-01-09 The Torrington Company Valve control mechanism
US5445116A (en) * 1992-12-22 1995-08-29 Unisia Jecs Corporation Hydraulic variable lift engine valve gear
US5509385A (en) 1995-06-15 1996-04-23 Precision Engine Products Corp. Hydraulic lash adjuster metering valve
DE19744600A1 (de) * 1997-10-09 1999-04-15 Volkswagen Ag Abschaltbarer Ventiltrieb für Brennkraftmaschinen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0899429A1 (de) * 1997-08-28 1999-03-03 Eaton Corporation Hydraulisches Ventilspielausgleichselement

Also Published As

Publication number Publication date
EP1568851A1 (de) 2005-08-31
DE602004021767D1 (de) 2009-08-13
ATE435359T1 (de) 2009-07-15

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