EP0473887A2 - Compensateur hydraulique du jeu de soupapes pour moteurs à combustion interne - Google Patents

Compensateur hydraulique du jeu de soupapes pour moteurs à combustion interne Download PDF

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Publication number
EP0473887A2
EP0473887A2 EP91109577A EP91109577A EP0473887A2 EP 0473887 A2 EP0473887 A2 EP 0473887A2 EP 91109577 A EP91109577 A EP 91109577A EP 91109577 A EP91109577 A EP 91109577A EP 0473887 A2 EP0473887 A2 EP 0473887A2
Authority
EP
European Patent Office
Prior art keywords
displacement body
storage space
compensation element
valve
clearance compensation
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
EP91109577A
Other languages
German (de)
English (en)
Other versions
EP0473887B1 (fr
EP0473887A3 (en
Inventor
Klaus Döhring
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 EP0473887A2 publication Critical patent/EP0473887A2/fr
Publication of EP0473887A3 publication Critical patent/EP0473887A3/de
Application granted granted Critical
Publication of EP0473887B1 publication Critical patent/EP0473887B1/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
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2107—Follower

Definitions

  • the invention relates to a hydraulic valve lash adjuster for internal combustion engines, in which an inner tappet is axially displaceable relative to an outer tappet and, together with the latter, limits a volume-variable, oil-filled storage space which is sealed off from the outside by a seal.
  • valve lash adjuster is known from DE-OS 35 06 730.
  • the storage space contained therein is closed off from the outside by a bellows-shaped seal and, moreover, is adamantly limited.
  • the durability is unsatisfactory and damage to the seal is particularly evident after a relatively short time.
  • valve clearance compensation element is known from DE-OS 28 47 699. Thereafter, it is provided that a plurality of erectile tissue are assigned adjacent to one another and receive an air cushion between them. However, it should be noted that there is both hydraulic fluid and a certain amount of air in the reservoir. The resulting performance characteristics are unsatisfactory. According to another embodiment, it is provided that the air in the storage space is to be retained by glass balls or plastic beads, or that the erectile tissue is made of a sponge-like material, which is partially soaked in liquid and forms the air cushion with its predetermined proportion of air. An effective keeping away of the air components from the high pressure space cannot be guaranteed with this configuration.
  • the invention has for its object to show a valve clearance compensation element with an externally closed storage space, which is inexpensive to manufacture and has a significantly improved service life and improved properties.
  • valve lash adjuster of the type mentioned in that at least one compressible displacement body for compensating for volume changes is included in the storage space, that the displacement body consists of a closed-cell soft foam and that the soft foam is provided with a non-porous surface layer.
  • the displacement body can consist of a soft foam sealed liquid-tight to the outside, for example a flexible polyurethane foam with a density of 30 to 700 kg / m3.
  • the production is expediently carried out in such a way that an essentially non-porous surface skin is obtained.
  • the diffusion of oil constituents into the pores of the soft foam body, which are closed off from the outside like a balloon, is thereby additionally hindered and the achievement of a particularly long service life is promoted.
  • the compressible displacement body enclosed in the storage space can contain at least one gas-filled cavity and can be formed, for example, by a flexible and / or elastically deformable gas bubble which is made of polymeric material.
  • the size depends on the particular circumstances of the application and in particular on the increase in volume experienced by the oil contained in the valve lash adjuster when the room temperature rises to operating temperature and / or changes in volume due to a change in the support length of the valve lash adjuster.
  • the support length can change, for example, if a valve is still in the open position when the internal combustion engine is shut down. In this case, the valve clearance compensation element is loaded by the return spring of the valve over a longer period of time, which requires a gradual reduction in the support length.
  • the mechanical load on the displacement body under normal operating conditions can be reduced if the displacement body is arranged in a recess in the wall of the storage space.
  • a mutual gluing is carried out with the wall of the storage space, there is the additional advantage that in the region of the gluing zone a direct wetting of the displacement body by the oil contained in the storage space is not possible.
  • the corresponding zone of the displacer is thereby protected in an excellent manner against physical and / or chemical effects from the oil contained in the storage space.
  • the bonding can be effected using a secondary adhesive, which is introduced in the liquid state in the intermediate zone between the displacement body and the wall and subsequently solidified.
  • the displacement body In the case of designs in which the displacement body is designed to be rotationally symmetrical, it is advisable for the displacement body to be concentric with the valve clearance compensation element assign. Damage and functional impairments resulting from undesired relative displacements can thereby be avoided.
  • Fig. 1 to 3 different versions of valve clearance compensation elements in a longitudinal section.
  • the valve clearance compensation element shown in FIG. 1 is intended for an internal combustion engine. It comprises an inner plunger 1 which is axially displaceably mounted in an outer plunger 2.
  • the inner tappet 1 is supported by means of a compression spring 8 on a piston 7 which bears against the bottom of the outer tappet 2.
  • the compression spring 8 has a softer spring identification than the return spring of the associated valve of the internal combustion engine (not shown). As a result, it is in no way able to hinder the closing movement of the valve. Rather, a secure installation of the valve plate on the valve seat is guaranteed at all times if the valve in question is not actuated.
  • the force of the compression spring 8 is sufficiently large to ensure that the valve lash adjuster element engages without play on the one hand on the valve stem and on the other hand on the camshaft of the internal combustion engine (not shown). If the cam located on it comes into engagement with the valve lash adjuster, this results in an axial displacement of the valve lash adjuster including the valve supported thereby. This takes place in such a short time that the valve clearance compensation element behaves almost rigidly. The valve is thereby moved into its open position to the extent necessary to enable the desired gas exchange of the associated cylinder of the internal combustion engine.
  • the cavities enclosed by the inner tappet 1, the outer tappet 2 and the piston 7 are filled with oil, it being additionally provided that a compressible displacement body 4 is arranged in the storage space 3.
  • This consists of a circular, gas-filled rubber bubble, which is concentrically assigned to the valve lash adjuster. It is dimensioned so large that the change in the oil volume contained in the valve clearance compensation element as a result of temperature changes and / or changes in the support length can be absorbed while avoiding a pressure increase which impairs the functionality.
  • the O-ring seal 6 is thus only used as a movement seal to the extent necessary for the gradual compensation of the valve wear.
  • the resulting relative displacements are of very small size. As a result, the O-ring seal can guarantee excellent sealing results over very long periods of use. From a functional point of view, the explanations described below correspond to the above. Their structure differs only slightly from the embodiment according to FIG. 1.
  • a guide ring made of a hard plastic is arranged between the inner plunger 1 and the outer plunger 2, which is opposite the outer plunger and is sealed from the inner tappet by an O-ring seal.
  • the immovable fixing of the guide ring 11 with respect to the outer plunger 2 is carried out by a circumferential retaining claw 10 which is snapped into a circumferential groove of the outer plunger 2 or by other fastening means, for example a snap ring.
  • the use of other fasteners is possible, for example snap rings.
  • the guide ring has a U-shaped profile in its entirety, which encloses a compressible displacement body 4 in its lower region.
  • the displacement body 4 consists of closed-cell foam made of polyurethane, silicone or another polymeric material, which is provided with a cast skin on the surface and has an average density of 35 kg / m3. It is also possible to use a silicone foam or other closed-cell soft foams made of polymer material. If necessary, the performance properties should be checked in a test.
  • the soft foams used should have a cast skin on the surface. This is characterized by a particularly good permeation security when the displacement body is manufactured using the free-foam process.
  • a cast skin produced using the free-foam process therefore has the function of an additional separating membrane.
  • Figure 3 shows an embodiment similar to Figure 2, in which the outer plunger 2 and a displacer 4 receiving ring 15 are made of plastic.
  • the ring 15 and the displacement body 4 on the one hand and the ring 15 and the outer plunger 2 on the other hand are captively connected to one another by welding or gluing.
  • the displacement body 4 consisting of closed-cell polyurethane foam in the event of a temperature-related pressure increase in the storage space 3, it can nevertheless easily absorb the resulting increase in volume.
  • An O-ring seal is again provided for the sealing against the inner tappet 1.
  • the end face of the outer plunger 2 is glued to an armor plate 16 made of metallic or ceramic material. With a relatively low weight, the embodiment shown in FIG. 5 is characterized by particularly good durability.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gasket Seals (AREA)
EP91109577A 1990-08-24 1991-06-11 Compensateur hydraulique du jeu de soupapes pour moteurs à combustion interne Expired - Lifetime EP0473887B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4026793A DE4026793A1 (de) 1990-08-24 1990-08-24 Hydraulisches ventilspielausgleichselement fuer brennkraftmaschinen
DE4026793 1990-08-24

Publications (3)

Publication Number Publication Date
EP0473887A2 true EP0473887A2 (fr) 1992-03-11
EP0473887A3 EP0473887A3 (en) 1992-07-01
EP0473887B1 EP0473887B1 (fr) 1994-03-02

Family

ID=6412838

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91109577A Expired - Lifetime EP0473887B1 (fr) 1990-08-24 1991-06-11 Compensateur hydraulique du jeu de soupapes pour moteurs à combustion interne

Country Status (5)

Country Link
US (1) US5107806A (fr)
EP (1) EP0473887B1 (fr)
JP (1) JPH04234509A (fr)
DE (2) DE4026793A1 (fr)
ES (1) ES2050014T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0555521A1 (fr) * 1992-02-11 1993-08-18 Firma Carl Freudenberg Poussoir de soupape hydraulique
EP0568157A1 (fr) * 1992-05-01 1993-11-03 General Motors Corporation Poussoir hydraulique de soupape à action directe et de faible masse
WO1994019597A1 (fr) * 1993-02-26 1994-09-01 Siemens Aktiengesellschaft Dispositif de dosage de fluides

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5245958A (en) * 1990-11-08 1993-09-21 General Motors Corporation Direct acting hydraulic valve lifter
US5168840A (en) * 1992-03-26 1992-12-08 Siemens Automotive L.P. Temperature compensated damping mechanism for hydraulic engine valve actuator
US5280771A (en) * 1992-09-23 1994-01-25 Eaton Corporation Direct acting hydraulic tappet
US5584268A (en) * 1994-12-27 1996-12-17 Ford Motor Company Low inertia rocker arm with lash adjuster and engine valve
DE19705726A1 (de) * 1997-02-14 1998-08-20 Schaeffler Waelzlager Ohg Ventiltrieb einer Brennkraftmaschine
US5964193A (en) * 1998-08-20 1999-10-12 Ford Global Technologies, Inc. Synchronous hydraulic lash adjuster
US20060196559A1 (en) * 2005-03-07 2006-09-07 Baker David L Valve pressure accumulator

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2109816A (en) * 1935-12-21 1938-03-01 Packard Motor Car Co Hydraulic valve tappet
DE2847699A1 (de) * 1978-11-03 1980-05-14 Kellermann Fa Rudolf Hydraulisches spielausgleichselement
EP0197246A2 (fr) * 1985-04-12 1986-10-15 Goetze Ag Dispositif de compensation du jeu dans la commande de soupapes
EP0225096A1 (fr) * 1985-11-14 1987-06-10 Eaton Corporation Poussoir hydraulique autonome
DE3910666A1 (de) * 1989-04-03 1990-10-04 Schaeffler Waelzlager Kg Hydraulischer tassenstoessel

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2517370A1 (de) * 1975-04-19 1976-10-28 Volkswagenwerk Ag Hydraulische spielausgleichsvorrichtung
JPS53107517A (en) * 1977-03-02 1978-09-19 Aisin Seiki Co Ltd Enclosed rush adjuster
JPS56124615A (en) * 1980-03-06 1981-09-30 Aisin Seiki Co Ltd Rush adjuster device
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
DE3311280A1 (de) * 1983-03-28 1984-10-11 FEV Forschungsgesellschaft für Energietechnik und Verbrennungsmotoren mbH, 5100 Aachen Hydraulisches ventilspielausgleichselement
JPS60192811A (ja) * 1984-03-13 1985-10-01 Aisin Seiki Co Ltd 密封式油圧リフタ
IT8467294A0 (it) * 1984-03-27 1984-03-27 Riv Officine Di Villar Perosa Punteria idraulica per il comando del moto di una valvola di un motore endotermico
IT8454108V0 (it) * 1984-12-04 1984-12-04 Riv Officine Di Villar Perosa Punteria idraulica a tenuta stagna per il comando del moto di una valvola di un motore endotermico
US4590899A (en) * 1985-05-17 1986-05-27 Stanadyne, Inc. Self-contained lash adjuster with shell mounted cartridge assembly
DE3615791A1 (de) * 1985-05-22 1986-11-27 Volkswagen AG, 3180 Wolfsburg Abgeschlossene hydraulische laengenausgleichsvorrichtung, insbesondere fuer ventile von brennkraftmaschinen
DE3528348A1 (de) * 1985-08-07 1987-02-19 Daimler Benz Ag Hydraulischer tassenstoessel fuer einen ventiltrieb von brennkraftmaschinen
DE3606824A1 (de) * 1986-02-13 1987-08-20 Goetze Ag Ventilspielausgleichseinrichtung
DE3713680A1 (de) * 1987-04-24 1988-11-03 Goetze Ag Geschlossener hydraulischer tassenstoessel

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2109816A (en) * 1935-12-21 1938-03-01 Packard Motor Car Co Hydraulic valve tappet
DE2847699A1 (de) * 1978-11-03 1980-05-14 Kellermann Fa Rudolf Hydraulisches spielausgleichselement
EP0197246A2 (fr) * 1985-04-12 1986-10-15 Goetze Ag Dispositif de compensation du jeu dans la commande de soupapes
EP0225096A1 (fr) * 1985-11-14 1987-06-10 Eaton Corporation Poussoir hydraulique autonome
DE3910666A1 (de) * 1989-04-03 1990-10-04 Schaeffler Waelzlager Kg Hydraulischer tassenstoessel

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0555521A1 (fr) * 1992-02-11 1993-08-18 Firma Carl Freudenberg Poussoir de soupape hydraulique
EP0568157A1 (fr) * 1992-05-01 1993-11-03 General Motors Corporation Poussoir hydraulique de soupape à action directe et de faible masse
WO1994019597A1 (fr) * 1993-02-26 1994-09-01 Siemens Aktiengesellschaft Dispositif de dosage de fluides

Also Published As

Publication number Publication date
DE59101085D1 (de) 1994-04-07
ES2050014T3 (es) 1994-05-01
DE4026793A1 (de) 1992-03-05
EP0473887B1 (fr) 1994-03-02
US5107806A (en) 1992-04-28
EP0473887A3 (en) 1992-07-01
JPH04234509A (ja) 1992-08-24

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