EP0324085B1 - Hydraulisches Spielausgleichselement - Google Patents

Hydraulisches Spielausgleichselement Download PDF

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Publication number
EP0324085B1
EP0324085B1 EP88119539A EP88119539A EP0324085B1 EP 0324085 B1 EP0324085 B1 EP 0324085B1 EP 88119539 A EP88119539 A EP 88119539A EP 88119539 A EP88119539 A EP 88119539A EP 0324085 B1 EP0324085 B1 EP 0324085B1
Authority
EP
European Patent Office
Prior art keywords
piston
supply chamber
lubricating oil
valve
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.)
Expired - Lifetime
Application number
EP88119539A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0324085A1 (de
Inventor
Markus Dietrich
Frank Berger
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.)
Daimler Benz AG
Original Assignee
Daimler Benz AG
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 Daimler Benz AG filed Critical Daimler Benz AG
Priority to AT88119539T priority Critical patent/ATE72879T1/de
Publication of EP0324085A1 publication Critical patent/EP0324085A1/de
Application granted granted Critical
Publication of EP0324085B1 publication Critical patent/EP0324085B1/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
    • 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
    • F01L1/245—Hydraulic tappets

Definitions

  • the invention relates to a hydraulic lash adjuster for a valve train of an internal combustion engine according to the preamble of claim 1.
  • a hydraulic lash adjuster of the generic type is known from US-A-3 406 668.
  • the shut-off valve arranged in the storage space of the displaceable piston part consists of a ball which is held by a return spring in an open position with respect to the connecting bore between the pressure and storage space.
  • the ball has a predetermined mass, by means of which the connecting bore is closed only after a certain high speed of the internal combustion engine due to its inertia. This is to prevent undesired inflation of the play compensation element at extremely high speeds. Due to the design of the shut-off valve as a ball, it is not possible to control the valve depending on the pressure of the lubricating oil in the reservoir.
  • a valve lifter in the valve train of an internal combustion engine which comprises a cylinder part actuated by the camshaft and a piston part displaceably arranged therein.
  • the piston part can be operated from a special pressure pump with a pressurized one Lubricating oil.
  • the stroke curve of the exhaust valves for engine brake operation can be changed.
  • the connection between the piston part and the pressure pump is blocked, so that a play compensation by means of the piston part is not possible.
  • the invention has for its object to develop a hydraulic lash adjuster of the generic type so that the adjustment function can be interrupted under certain engine operating conditions.
  • the invention makes it possible to control the shut-off valve as a function of the lubricating oil pressure in the reservoir.
  • the adjustment function of the play compensation element can advantageously be deactivated, controlled only by the lubricating oil pressure. This makes it possible to use backlash compensation elements in the valve train even in internal combustion engines with an engine brake controlled via the gas exchange valves, since the previously undesired adjustment of the compensation elements has been eliminated by the measures according to the invention.
  • the safe interruption of the readjusting function can be impaired, for example, by overflow of leakage oil from the pressure chamber into the reservoir or vice versa via the annular gap between the piston part and cylinder part.
  • the annular gap is therefore kept particularly small, or it is bridged by a sealing ring according to the features of claim 2.
  • a capillary overflow bore is provided between the pressure chamber and the reservoir.
  • the overflow bore allows oil to flow out of the storage space into the pressure space when the adjustment function is switched off and the minimal adjustment movement generated thereby is undesirable.
  • the overflow bore opens out in the region of the valve seat surface.
  • a play compensation element 3 is inserted in a housing bore 2 and can be displaced in the longitudinal direction of the bore.
  • the clearance compensation element 3 comprises a cylinder part 4, in the between a valve tappet, not shown or shaft and a compression spring 5 a piston part 6 is slidably held.
  • the compression spring 5 is supported on the bottom part 7 of the cylinder part 4 and on an end wall 8 of the piston part 6, whereby the cylinder and piston part are biased in opposite directions of movement so that on the one hand the cylinder part 4 with its bottom part 7 on a control cam (not shown) and on the other hand the Piston part rests on the tappet or stem of the gas exchange valve without play.
  • the piston part 6 encloses with the cylinder part 4 a pressure chamber 9 which is filled with lubricating oil from a reservoir 10 formed in the piston part 6 and which is supplied through a connecting channel 11.
  • the storage space 10 is constantly supplied with lubricating oil from the lubricating oil circuit of the internal combustion engine, which reaches the storage space 10 through an inlet channel 12 branched off from the lubricating oil circuit and corresponding inlet bores 13 and 14 in the cylinder 4 and piston part 6.
  • the connecting channel 11 is closed by a spring-loaded closure element 15 arranged on the pressure chamber side. If there is play in the valve train, the piston part 6 is displaced in the direction of the tappet linkage by the compression spring 5 located in the pressure chamber 9. Due to the pressure drop occurring in the pressure chamber 9, the closure element 15 is controlled by the pressure of the lubricating oil in the reservoir 10 and lubricating oil is pushed into the pressure chamber.
  • This inflating of the play compensation element 3, which serves to compensate for play, is e.g. undesirable during engine braking operation of the internal combustion engine.
  • a shut-off valve 16 is provided in the storage space, from which the readjustment function of the play compensation element 3 can be switched off.
  • the shut-off valve 16 consists of a stepped piston 17, the extended piston section of which is guided in a longitudinally displaceable manner in a guide sleeve 18.
  • the guide sleeve 18 is attached to a piston wall 19 opposite the connecting channel 11 and projects into the storage space 10.
  • a closing member 20 is provided, which cooperates with a valve seat 21 formed in the region of the mouth of the connecting channel 11 into the storage space.
  • the shut-off valve 16 is controlled as a function of the lubricating oil pressure in the supply room 10.
  • the shut-off valve 16 In normal operation of the internal combustion engine, the shut-off valve 16 is in the open position, that is to say the stepped piston 17 is controlled by the lubricating oil pressure against the action of a return spring 22 supported on the piston 17 and the piston wall 18 in an upper end position, in which the closing member 20 moves from the seat surface 21 is lifted off so that a game compensation can take place.
  • the readjustment or backlash compensation function is switched off by lowering the lubricating oil pressure in the reservoir 10.
  • the stepped piston 17 is displaced by the return spring 22 in the direction of the connecting channel 11 until the closing member 20 rests on the seat surface 21.
  • the lubricating oil pressure can be controlled, for example, via an electromagnetically switched shut-off valve arranged in the inlet channel 12.
  • the valve In normal operation of the internal combustion engine, the valve is open, so that the lubricating oil pressure is present in the reservoir 10.
  • a corresponding voltage signal is applied to the shut-off valve, as a result of which the inlet channel 12 is separated from the lubricating oil circuit and the reservoir 10 is therefore depressurized.
  • This voltage signal can be derived, for example, from a position sensor located on the exhaust gas flap in the exhaust pipe of the internal combustion engine. It is possible to control the shut-off valve via other operating parameter signals of the internal combustion engine.
  • the piston part 6 is guided in the cylinder part 4 with a close fit.
  • the piston part 6 can also be sealingly guided in the cylinder part 4 by a sealing ring 24 inserted in an annular groove 23 on the circumference of the piston between the inlet bore 14 and the piston wall 8.
  • the pressure chamber 9 is connected to the storage chamber 10 by a capillary overflow bore 25, the mouth of which lies within the seat surface 21.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Damping Devices (AREA)
EP88119539A 1988-01-15 1988-11-24 Hydraulisches Spielausgleichselement Expired - Lifetime EP0324085B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88119539T ATE72879T1 (de) 1988-01-15 1988-11-24 Hydraulisches spielausgleichselement.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3800945A DE3800945C1 (enrdf_load_stackoverflow) 1988-01-15 1988-01-15
DE3800945 1988-01-15

Publications (2)

Publication Number Publication Date
EP0324085A1 EP0324085A1 (de) 1989-07-19
EP0324085B1 true EP0324085B1 (de) 1992-02-26

Family

ID=6345299

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88119539A Expired - Lifetime EP0324085B1 (de) 1988-01-15 1988-11-24 Hydraulisches Spielausgleichselement

Country Status (6)

Country Link
US (1) US4881499A (enrdf_load_stackoverflow)
EP (1) EP0324085B1 (enrdf_load_stackoverflow)
JP (1) JPH01216008A (enrdf_load_stackoverflow)
AT (1) ATE72879T1 (enrdf_load_stackoverflow)
DE (2) DE3800945C1 (enrdf_load_stackoverflow)
ES (1) ES2030827T3 (enrdf_load_stackoverflow)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1230011B (it) * 1989-04-20 1991-09-20 Eaton Automotive Spa Punteria idraulica a compensazione migliorata del gioco dopo un periodo di inattivita' del motore.
US4977867A (en) * 1989-08-28 1990-12-18 Rhoads Jack L Self-adjusting variable duration hydraulic lifter
DE4039075C2 (de) * 1990-10-01 2001-11-29 Volkswagen Ag Ventiltrieb für zumindest zwei gleichzeitig betätigbare Hubventile
US5088458A (en) * 1991-02-01 1992-02-18 Siemens Automotive L.P. Lash adjusted for engine valve actuator assembly
US5168840A (en) * 1992-03-26 1992-12-08 Siemens Automotive L.P. Temperature compensated damping mechanism for hydraulic engine valve actuator
DE19517401C1 (de) * 1995-05-15 1996-09-26 Hydac Technology Gmbh Ausgleichsvorrichtung
DE19818893A1 (de) 1998-04-28 1999-11-04 Mwp Mahle J Wizemann Pleuco Gm Hydraulisches Ventilspielausgleichselement
US5931132A (en) * 1998-08-24 1999-08-03 Freeland; Mark Hydraulic lash adjuster with pressure relief check valve
US6318324B1 (en) * 1998-12-07 2001-11-20 Daimlerchrysler Corporation Sealed hydraulic lifter for extreme angle operation
DE10129729A1 (de) * 2001-06-20 2003-01-23 Mahle Ventiltrieb Gmbh Hydraulisches Spielausgleichselement für einen Ventiltrieb eines Verbrennungsmotors
DE10143012A1 (de) * 2001-09-03 2003-03-20 Daimler Chrysler Ag Hydraulisches Spielausgleichselement, insbesondere für einen Ventiltrieb eines Verbrennungsmotors
US20070215080A1 (en) * 2006-02-14 2007-09-20 Thomas Engine Company, Llc Variable valve actuation
DE102007014248A1 (de) * 2007-03-24 2008-09-25 Schaeffler Kg Hubkolbenbrennkraftmaschine mit Motorbremseinrichtung
DE102007014250A1 (de) * 2007-03-24 2008-09-25 Schaeffler Kg Brennkraftmaschine mit Motorbremse
DE102007022652A1 (de) * 2007-05-15 2008-11-20 Daimler Ag Gaswechselventilbetätigungsvorrichtung
JP4865740B2 (ja) 2008-01-30 2012-02-01 株式会社オティックス ラッシュアジャスタ
DE102011005575A1 (de) * 2011-03-15 2012-09-20 Schaeffler Technologies Gmbh & Co. Kg Ventiltrieb mit Zusatzhub im Nockengrundkreis
EP2653674A1 (en) * 2012-04-19 2013-10-23 Eaton S.r.l. Hydraulic lash adjuster
GB2503705A (en) * 2012-07-05 2014-01-08 Eaton Srl Hydraulic Lash Adjuster and Lost Motion System
US11060427B2 (en) 2019-06-24 2021-07-13 Schaeffler Technologies AG & Co. KG Valve train including engine braking system
US10823018B1 (en) 2019-06-25 2020-11-03 Schaeffler Technologies AG & Co. KG Valve train arrangement including engine brake system and lost-motion hydraulic lash adjuster

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2442575A (en) * 1945-05-03 1948-06-01 Weatherhead Co Self-adjusting tappet
US2694388A (en) * 1950-12-30 1954-11-16 Thompson Prod Inc Self-contained hydraulic valve train length adjusting mechanism
US3406668A (en) * 1968-01-19 1968-10-22 Ford Motor Co Hydraulic tappet assembly
DE2606464C2 (de) * 1975-02-18 1986-12-04 Eaton Corp., Cleveland, Ohio Hydraulisches Spielausgleichselement
US4164917A (en) * 1977-08-16 1979-08-21 Cummins Engine Company, Inc. Controllable valve tappet for use with dual ramp cam
GB2006373A (en) * 1977-10-10 1979-05-02 Ricardo & Co Eng 1927 Ltd I. C. Engine Valve Clearance Regulating Means
US4254749A (en) * 1979-03-23 1981-03-10 Eaton Corporation Fuel injection system and timing advance device therefor
JPS56124615A (en) * 1980-03-06 1981-09-30 Aisin Seiki Co Ltd Rush adjuster device
US4462364A (en) * 1981-09-17 1984-07-31 Aisin Seiki Kabushiki Kaisha Hydraulic lash adjuster
JPS58124011A (ja) * 1982-01-19 1983-07-23 Toyota Motor Corp 油圧調整式バルブリフタ−
JPS58136605U (ja) * 1982-03-09 1983-09-14 トヨタ自動車株式会社 密封型油圧リフタ
JPS5976302A (ja) * 1982-10-22 1984-05-01 株式会社渡辺組 温水式アスフアルト再生装置
DE3712020A1 (de) * 1987-04-09 1988-10-27 Schaeffler Waelzlager Kg Ventilsteuereinrichtung

Also Published As

Publication number Publication date
EP0324085A1 (de) 1989-07-19
US4881499A (en) 1989-11-21
ATE72879T1 (de) 1992-03-15
ES2030827T3 (es) 1992-11-16
DE3868615D1 (de) 1992-04-02
JPH01216008A (ja) 1989-08-30
DE3800945C1 (enrdf_load_stackoverflow) 1989-02-16

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