EP0502241B1 - Poussoir à rattrapage de jeu hydraulique pour commande de soupape - Google Patents

Poussoir à rattrapage de jeu hydraulique pour commande de soupape Download PDF

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Publication number
EP0502241B1
EP0502241B1 EP91116179A EP91116179A EP0502241B1 EP 0502241 B1 EP0502241 B1 EP 0502241B1 EP 91116179 A EP91116179 A EP 91116179A EP 91116179 A EP91116179 A EP 91116179A EP 0502241 B1 EP0502241 B1 EP 0502241B1
Authority
EP
European Patent Office
Prior art keywords
compression spring
spring
temperature
support spring
bucket tappet
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
EP91116179A
Other languages
German (de)
English (en)
Other versions
EP0502241A1 (fr
Inventor
Volker Budde
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.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
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 Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of EP0502241A1 publication Critical patent/EP0502241A1/fr
Application granted granted Critical
Publication of EP0502241B1 publication Critical patent/EP0502241B1/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
    • 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
    • F01L1/25—Hydraulic tappets between cam and valve stem
    • 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 tappet with a hydraulic lash adjuster for a valve train of an internal combustion engine, comprising two movably sealed hollow cylinders, which are closed in the region of their ends facing away from each other by covers and axially elastically supported on one another by a compression spring.
  • Such a tappet is known for example from DE-PS 36 17 858. It is used between the camshaft and the valves of an internal combustion engine and effects an automatic compensation of the valve clearance. This eliminates the need to adjust the valve clearance in connection with maintenance work.
  • the known bucket tappet has a piston which can be displaced in a cylinder parallel to the direction of actuation of the valve and which is supported by a compression spring on the bottom of the cylinder. In the unloaded state of the cup tappet, this results in an axially directed movement apart of the piston in the cylinder, oil being drawn in from a storage space via a throttle opening and being stored in the interior of a pressure chamber of the piston / cylinder unit.
  • the cross-section of the throttle opening is very narrow.
  • the oil volume stored in the piston / cylinder unit is not noticeably reduced in the short time that is available during the normal actuation of the valves by the cams of the camshaft. The forces required to actuate the valves can rather be transferred without any problems.
  • the compression spring reliably presses the piston / cylinder unit apart even at low temperatures and brings about an equalization of the valve clearance.
  • the lubricating oil contained in the reserve space must be returned to the piston / cylinder unit by the compression spring at a sufficiently high speed. Because of the large viscosity of lubricating oil that occurs at low temperatures, great forces are required.
  • the compression springs used according to the state of the art are dimensioned accordingly. An undesirable strong movement apart of the piston / cylinder unit at normal temperature and in particular at high temperatures is the inevitable consequence of this and can cause undesirable wear on the tappet.
  • the invention has for its object to further develop a tappet of the type mentioned in such a way that an immediate filling of the piston / cylinder unit from the reserve space is ensured even at low temperatures and a soft elastic support of the two hollow cylinders on each other when the normal operating temperature is reached.
  • the hollow cylinders are supported in addition to the compression spring by a support spring with the compression spring in the opposite direction of action and that the support spring consists of a metallic shape memory alloy and has a load capacity that is lower when the As temperature is reached than the load capacity of the compression spring.
  • the support spring loses its spring force when it reaches low temperatures.
  • only the force of the compression spring acts in this temperature range, which is dimensioned such that despite the large viscosity of the lubricating oil contained in the tappet, parallel to the relative rotation of the cam of the camshaft, the piston / cylinder unit is immediately filled with lubricating oil. This ensures proper actuation of the associated valve of the internal combustion engine from the first moment.
  • valve train including the bucket tappet and the lubricating oil contained therein reach a sufficiently high operating temperature after the cold start, the support spring regains its spring force. It has an opposite direction of action to the compression springs. The total spring force available is thereby reduced to a value which, on the one hand, ensures a high level of operational safety and, on the other hand, achieves minimal wear.
  • the compression springs of the support spring are expediently designed as coil springs. As a result, they can be produced and assembled particularly cost-effectively.
  • the support spring consists of an alloy with an As temperature that is between ⁇ 15 and + 5 ° C. and expediently in the region of the freezing point of water. Especially within the specified range, the viscosity of common lubricating oils changes relatively strongly. However, it goes without saying that, depending on the type of lubricating oil used in the individual case, the use of support springs can be expedient, which are made of alloys with a possibly different As temperature.
  • the load capacity of the support spring should be 30 to 70% of that of the compression spring when the As temperature is reached. Such a design particularly meets the requirement of modern engine construction to prevent malfunctions during the entire service life.
  • the bucket tappet according to the invention always ensures that the piston / cylinder unit contained is so quickly filled with oil, regardless of the individual temperatures, that proper operation of the internal combustion engine is always guaranteed. It is of decisive advantage here that the external shape and the essential functional elements can be adopted from known designs. Both the manufacture of the bucket tappet according to the invention and its use in an ongoing production of internal combustion engines are thereby possible without any problems. Furthermore, the present invention can be used for tappets that are hermetically sealed to the outside and have a permanent oil filling, as well as for such tappets in which the enclosed cavity is connected to the oil circuit of the associated internal combustion engine.
  • the bucket tappet shown in the longitudinal section in the left part of the illustration is designed as a closed system which is provided with a permanent oil filling.
  • the bucket tappet shown in the right-hand part of the illustration in longitudinal section is designed as an open system which is connected to an oil circuit of the pressure circulation lubrication of an internal combustion engine.
  • the cup tappet shown comprises two hollow cylinders 1, 2 which are movably sealed against one another and which are closed in the region of their ends facing away from one another by covers 3, 4 and are axially elastically supported on one another by a compression spring 5.
  • the hollow cylinder 2 is guided on a piston 11 which extends coaxially to the hollow cylinder 1 and is supported on the cover 3 thereof.
  • a compression spring 5 is arranged between the piston 11 and the bottom 4 of the wooden cylinder 2, which causes the piston 11 to move axially apart with respect to the hollow cylinder 2.
  • the cavity enclosed by both is completely filled with oil. It is then only connected to the cavity 7 through a throttle gap in which the reserve oil is stored.
  • the cavity 7 can be connected to the oil circuit of the pressure lubrication system of the internal combustion engine through a connection opening (right part of the illustration), it can also be hermetically sealed to the outside by a bellows 12 (left part of the illustration), which means that the valve clearance compensation element is independent of the respective pressure of the Oil circuit gives the internal combustion engine good functional reliability.
  • the hollow cylinder 2 is axially displaceably mounted in a guide piece 14. Between the guide piece 14 and a collar 15 fixedly connected to the piston 11, a support spring 8 is arranged, which is made of memory metal.
  • the support spring 8 has the property of losing its spring force when falling below a certain temperature range and the original spring force with a subsequent warming up to their As temperature.
  • the support spring is also designed as a compression spring. It has an opposite direction of action to the compression spring 5, so that the total available spring force at low temperatures at which the support spring 8 is ineffective is determined only by that of the compression spring 5. At high temperatures, on the other hand, the spring force of the compression spring 5 is reduced by the spring force of the activated support spring 8. Overall, only the difference between the load capacities of the two springs is available.
  • the force of the closing spring (not shown) of the associated valve causes a gradual upward movement of the hollow cylinder 2 in with respect to the hollow cylinder 1 with a corresponding relative displacement of oil components originally contained in the high-pressure chamber 13 into the cavity 7.
  • the support spring 8 counteracts the compression spring 5 and thus reduces the total force that presses the hollow cylinder 2 and the piston 11 apart and thus also reduces the friction between the rotating cam 10 and the cover 3 of the cylinder 1 In the temperature ranges mentioned, only a small spring force is necessary because the oil is very thin.
  • the lubricating oil is viscous at low temperatures and especially when the internal combustion engine is cold started.
  • a large spring force is required in order to press the hollow cylinder 2 and the piston 11 apart in the axial direction and to draw in the lubricating oil via the ball check valve into the cavity enclosed by both.
  • the support spring 8 has no spring force. As a result, it no longer acts as a relief for the compression spring 5.
  • the entire load-bearing capacity of the compression spring 5 is thus available for the axial movement apart of the hollow cylinder 2 with respect to the piston 11. Even under correspondingly unfavorable conditions, this ensures that the piston / cylinder unit moves apart sufficiently quickly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (5)

  1. Poussoir avec élément hydraulique de rattrapage de jeu pour une commande de soupapes d'un moteur à combustion interne, comportant deux cylindres creux, étanchés et mobiles l'un par rapport à l'autre, qui sont fermés par des couvercles dans la zone de leurs extrémités mutuellement opposées et qui sont appuyés axialement et élastiquement l'un sur l'autre par un ressort de pression, caractérisé en ce que les cylindres creux (1, 2) sont appuyés l'un sur l'autre, en complément du ressort de pression (5), par un ressort de soutien (8) ayant une direction d'action opposée à celle du ressort de pression (5) et en ce que le ressort de soutien (8) se compose d'un alliage métallique à mémoire de forme et, lors de l'atteinte de la température-As, il a une capacité de charge qui est plus petite que la capacité de charge du ressort de pression (5).
  2. Poussoir selon la revendication 1, caractérisé en ce que le ressort de pression (5) et le ressort de soutien (8) sont agencés comme des ressorts hélicoïdaux.
  3. Poussoir selon l'une des revendications 1 et 2, caractérisé en ce que le ressort de soutien (8) se compose d'un alliage ayant une température-As qui est comprise entre -15 et + 5°C.
  4. Poussoir selon l'une des revendications 1 et 2, caractérisé en ce que le ressort de soutien (8) se compose d'un alliage ayant une température-As, située à peu près dans la zone du point de congélation de l'eau.
  5. Poussoir selon l'un des revendications 1 à 4, caractérisé en ce que la capacité de charge du ressort de soutien (8) est comprise, lors de l'atteinte de la température-As, entre 30 et 70% de celle du ressort de pression (5).
EP91116179A 1991-03-06 1991-09-24 Poussoir à rattrapage de jeu hydraulique pour commande de soupape Expired - Lifetime EP0502241B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4107041A DE4107041A1 (de) 1991-03-06 1991-03-06 Hydraulisches spielausgleichselement fuer einen ventiltrieb
DE4107041 1991-03-06

Publications (2)

Publication Number Publication Date
EP0502241A1 EP0502241A1 (fr) 1992-09-09
EP0502241B1 true EP0502241B1 (fr) 1994-05-25

Family

ID=6426538

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91116179A Expired - Lifetime EP0502241B1 (fr) 1991-03-06 1991-09-24 Poussoir à rattrapage de jeu hydraulique pour commande de soupape

Country Status (4)

Country Link
US (1) US5159907A (fr)
EP (1) EP0502241B1 (fr)
JP (1) JP2584563B2 (fr)
DE (2) DE4107041A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4203897C2 (de) * 1992-02-11 1994-01-27 Freudenberg Carl Fa Hydraulisches Ventilspielausgleichselement
DE4340035B4 (de) * 1992-12-10 2006-02-23 Ina-Schaeffler Kg Mechanischer Tassenstößel
DE19705726A1 (de) * 1997-02-14 1998-08-20 Schaeffler Waelzlager Ohg Ventiltrieb einer Brennkraftmaschine
DE102004035588A1 (de) * 2004-07-22 2006-02-16 Ina-Schaeffler Kg Hydraulisches Ventilspielausgleichselement
DE102006037816A1 (de) * 2006-08-12 2008-02-14 Schaeffler Kg Hubübertragungsvorrichtung mit hydraulischem Ventilspielausgleichselement
RU2532460C1 (ru) * 2013-07-01 2014-11-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Брянский государственный технический университет" Толкатель клапана двигателя внутреннего сгорания

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54155309A (en) * 1978-05-27 1979-12-07 Nissan Motor Co Ltd Valve moving system for internal combustion engine
US4397271A (en) * 1981-03-02 1983-08-09 Stanadyne, Inc. Semi-self-contained hydraulic lash adjuster
JPS60170008U (ja) * 1984-04-20 1985-11-11 日産自動車株式会社 油圧式バルブリフタ
JPS6134305A (ja) * 1984-07-25 1986-02-18 Aisin Seiki Co Ltd 密封型油圧リフタ
JPH063124B2 (ja) * 1985-10-15 1994-01-12 本田技研工業株式会社 内燃機関用油圧タペツト
DE3617858A1 (de) * 1986-05-27 1987-12-03 Freudenberg Carl Fa Tassenstoessel
US4977867A (en) * 1989-08-28 1990-12-18 Rhoads Jack L Self-adjusting variable duration hydraulic lifter

Also Published As

Publication number Publication date
JP2584563B2 (ja) 1997-02-26
DE4107041C2 (fr) 1993-02-11
DE59101724D1 (de) 1994-06-30
JPH04334707A (ja) 1992-11-20
US5159907A (en) 1992-11-03
DE4107041A1 (de) 1992-09-10
EP0502241A1 (fr) 1992-09-09

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