EP0525284B1 - Hydraulische Ventilspielausgleichseinrichtung für eine Verbrennungskraftmaschine - Google Patents

Hydraulische Ventilspielausgleichseinrichtung für eine Verbrennungskraftmaschine Download PDF

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Publication number
EP0525284B1
EP0525284B1 EP92103236A EP92103236A EP0525284B1 EP 0525284 B1 EP0525284 B1 EP 0525284B1 EP 92103236 A EP92103236 A EP 92103236A EP 92103236 A EP92103236 A EP 92103236A EP 0525284 B1 EP0525284 B1 EP 0525284B1
Authority
EP
European Patent Office
Prior art keywords
housing
hollow cylinder
compensating device
clearance compensating
valve clearance
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
EP92103236A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0525284A1 (de
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 EP0525284A1 publication Critical patent/EP0525284A1/de
Application granted granted Critical
Publication of EP0525284B1 publication Critical patent/EP0525284B1/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
    • F01L1/25—Hydraulic tappets between cam and valve stem

Definitions

  • the invention relates to a hydraulic valve lash adjuster for an internal combustion engine, in which a lash adjuster in a cylindrical guide can be moved up and down in the axial direction, comprising a first and a second hollow cylinder, which are sealed against one another and axially elastically supported on one another by a compression spring and by one essentially cup-shaped housing with a flat bottom and with at least one circumferentially arranged lubricant passage opening are concentrically enclosed, the first hollow cylinder and the lubricant passage opening being connected in a liquid-conducting manner, and wherein the lubricant passage opening on the side facing the hollow cylinders is assigned a first check valve that the lubricant passage through the opening releases in the direction of the first hollow cylinder and blocks the backflow from the first hollow cylinder through the opening.
  • valve lash adjuster is known from DE-OS 31 50 083.
  • a flexible rubber seal then forms a first check valve for sealing the reservoir for a hydraulic pressure medium.
  • the valve tappet contains the amount of pressure medium required for correct operation because the return flow of the pressure medium from the tank is blocked by the flexible rubber check valve. It should be noted, however, that the valve tappet is supplied with a lubricant from the lubricant circuit through a feed hole Internal combustion engine is filled. Such a configuration requires a high production outlay due to the bores arranged in the cylinder head and is therefore unsatisfactory in economic terms.
  • the invention has for its object to further develop a device of the type mentioned in such a way that the first hollow cylinder is always filled with pressure medium, even if the valves are kept in the open position when the internal combustion engine is at a long standstill, and that no oil supply holes specially provided for this purpose are used to fill the play compensation element is provided in the cylinder head.
  • the housing has an outer diameter in at least one partial area, which is reduced in size from the opening area to the bottom, the partial area of the housing and the guide delimiting a wedge-shaped gap in the axial direction, which in the Level of the floor is open.
  • the oil used for filling is spray oil that is present in the cylinder head for the lubrication of the camshaft, cam and tappet anyway.
  • the valve When the upward stroke has ended, the valve is in the closed position and the two hollow cylinders have the greatest possible distance from one another in the axial direction, due to the compression spring.
  • the lash adjuster To open the valve, the lash adjuster is moved downwards by a cam. Both the second check valve, which separates the second hollow cylinder from the first hollow cylinder, and the first check valve, which blocks the backflow from the first hollow cylinder through the opening in the direction of the cylinder head, are closed.
  • an almost rigid connection between the camshaft and valve is established in the axial direction, and on the other hand, causes at least the first hollow cylinder to be completely filled with oil in every operating state of the engine, even after a long standstill.
  • the main advantage is the fact that the difficult to manufacture feed holes in the cylinder head, which were previously required to supply the lash adjuster with lubricant, are avoided.
  • the configuration according to the invention is particularly advantageous in economic terms.
  • the housing can have a uniformly reduced outer diameter along a circumferential line in all partial areas.
  • This form of housing can be produced in a particularly simple manner, which gives advantages in terms of economy.
  • the housing has at least one segment-like wedge-shaped section on the circumference, the boundaries of which have the same outer diameter as the housing in the region of the cylindrical guide.
  • the advantage here is that the guide surface of the housing can be supported on a cylinder head over its entire axial extent in a guide bush. The Wear of the guide surface of the housing, caused by the tilting moments when the housing is moved in the axial direction, is thereby reduced comparatively.
  • four segment-like wedge-shaped sections are arranged along the circumference at right angles to one another.
  • the outer diameter can be continuously merging or reduced in steps.
  • the shape of the housing in this area can be particularly well adapted to the particular circumstances of the application. Some of the relevant parameters, on which the gap size between the housing and the guide depends, are formed by the first check valve, the size of the lubricant passage opening and the geometric dimensions of the hollow cylinder.
  • a partition is defined on the inside in the housing, which delimits an annular channel with the bottom, and that the channel is connected to the first hollow cylinder in a liquid-conducting manner.
  • the partition wall which fixes the first check valve, which consists for example of an elastically resilient material, in the radial direction in the region of the lubricant passage opening of the housing, ensures good performance characteristics with compact dimensions of the play compensation element.
  • the partition wall is touched on the side facing away from the bottom in the axial direction by the end face of the first hollow cylinder facing the channel and only by the second hollow cylinder with the greatest possible deflection.
  • the end face of the first hollow cylinder and / or the counter surface of the partition can be a pressure limitation in the first hollow cylinder Have a roughness depth of at least 1 ⁇ m. If a certain pressure in the first hollow cylinder is exceeded, the amount of liquid contained therein can escape in the form of a leak between the first hollow cylinder and the partition. Another leak that occurs during the intended use of the valve lash adjuster arises between the outer peripheral surface of the first hollow cylinder and the inner surface of the second hollow cylinder.
  • the second hollow cylinder can be captively, but axially displaceably arranged in the housing during use as intended.
  • the fastening element ensures simple assembly of the play compensation element in the valve train of an internal combustion engine.
  • the fastening element can, for example, be arranged in a groove along the inner circumferential surface of the housing and, in addition to the second hollow cylinder, can also fix the partition wall with the first check valve arranged therein in its radial direction.
  • this can be provided with recesses in the direction of the combustion chamber.
  • the partition and the fastening element can be formed in one piece and consist of polymeric material. This is advantageous both in terms of a further simplified assembly and in terms of the smallest possible mass of the play compensation element to be accelerated.
  • the fastening element can consist of a material with a particularly low coefficient of friction or can be provided with a surface coating which ensures low friction between the parts moving relative to one another.
  • a valve lash adjuster of the type according to the invention can be used in cylinder heads of internal combustion engines which do not have separate lines for filling the lash adjuster.
  • Fig. 1 two load conditions of the hydraulic valve lash adjuster are shown.
  • the second hollow cylinder 4 delimits the smallest volume of the high-pressure space and, with its end face open in the axial direction, lies against the partition 8.
  • the high-pressure space which is essentially delimited by the second hollow cylinder 4
  • the second hollow cylinder 4 bears in the axial direction with a projection on a stop surface of the fastening element 10.
  • the load state shown in the left part occurs, for example, when the lash adjuster 1 is arranged for a long time with the internal combustion engine switched off under axial load between a cam (not shown here) and an open valve.
  • a load state of the lash adjuster 1 is shown as it results during the operation of the internal combustion engine. Without external loads, i.e. at the top dead center of the game compensation element 1, the compression spring 5 moves the first 3 and second hollow cylinders 4 away from one another until the second hollow cylinder 4, which is relatively movable, comes to bear against the fastening element 10.
  • lubricant which is in the first hollow cylinder and in the channel 9 connected to it in a liquid-conducting manner can flow into the high-pressure chamber via the second check valve 13 and thus fill up with liquid volume displaced by leakage.
  • the play compensation element 1 is filled via a gap 12 which is formed by the housing 6 and the cylindrical guide 2. It is provided that the housing 6 has an outer diameter which is reduced in the area of the opening 6.2 starting in the direction of the bottom 6.1.
  • the function is as follows:
  • the starting point of the functional sequence is the position in which the valve of the internal combustion engine is fully open, ie the cam has brought the entire play compensation element 1 to its bottom dead center.
  • this oil is pressed into the wedge-shaped gap 12 and moved over the lubricant passage openings 6.2 past the first check valve 7 into the channel 9 and the first hollow cylinder 3.
  • the upward movement of the play compensation element 1 comes to a standstill at the top dead center. In this case, the valve of the internal combustion engine is closed.
  • the cam then moves the entire play compensation element 1 downward again to open the valve.
  • the first check valve 7 prevents the oil from flowing back out of the first hollow cylinder 3 and the channel 9 back through the lubricant passage opening 6.2 into the wedge-shaped gap 12.
  • the losses due to leakage in the high-pressure chamber are caused by a subsequent flow of the lubricant the first hollow cylinder 3 and the channel 9 equalized, so that a largely rigid connection between the cam and valve is formed.
  • the first check valve 7 prevents the first hollow cylinder 3 and the channel 9 from running empty with increasing time. This ensures that there is always sufficient oil in the channel 9 and in the first hollow cylinder 3 to supply the high-pressure space within the second hollow cylinder 4.
  • a hydraulic valve lash adjuster is shown, which is very similar to that in Fig. 1. It differs primarily in that the partition 8 and the fastening element 10 are formed in one piece and consist of polymeric material. The mode of operation is similar to that described above.
  • a valve lash adjuster is shown in perspective, in which the reduction of the outer diameter in the direction of the bottom 6.1 of the housing 6 is carried out only in segments.
  • the segment-like sections 12.1 have such an outer diameter in the area of their boundaries that there is a continuously constant outer diameter in the axial direction of the housing between the wedge-shaped sections 12.1.
  • the risk of tilting in a cylinder head (not shown here) during axial movement is significantly reduced by the comparatively large expansion of the housing 6 in the axial direction.
  • the main advantage of the invention can be seen in the oil supply, which takes place automatically during the upward movement of the play compensation element 1 by the pressure arising in the gap 12. This results in a significant simplification in the design and manufacture of the cylinder heads and cylinder blocks of the internal combustion engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Check Valves (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Soil Working Implements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Catching Or Destruction (AREA)
  • Mechanically-Actuated Valves (AREA)
EP92103236A 1991-07-24 1992-02-26 Hydraulische Ventilspielausgleichseinrichtung für eine Verbrennungskraftmaschine Expired - Lifetime EP0525284B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4124484 1991-07-24
DE4124484A DE4124484C1 (es) 1991-07-24 1991-07-24

Publications (2)

Publication Number Publication Date
EP0525284A1 EP0525284A1 (de) 1993-02-03
EP0525284B1 true EP0525284B1 (de) 1994-08-24

Family

ID=6436881

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92103236A Expired - Lifetime EP0525284B1 (de) 1991-07-24 1992-02-26 Hydraulische Ventilspielausgleichseinrichtung für eine Verbrennungskraftmaschine

Country Status (9)

Country Link
US (1) US5183016A (es)
EP (1) EP0525284B1 (es)
JP (1) JP2584569B2 (es)
AT (1) ATE110440T1 (es)
BR (1) BR9202047A (es)
CA (1) CA2074414C (es)
DE (2) DE4124484C1 (es)
ES (1) ES2059169T3 (es)
MX (1) MX9204313A (es)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19503699A1 (de) * 1995-02-04 1996-08-08 Schaeffler Waelzlager Kg Hydraulischer Ventiltriebsstößel
DE19617669A1 (de) * 1996-05-03 1997-11-06 Schaeffler Waelzlager Kg Hydraulisches Spielausgleichselement für einen Ventiltrieb einer Brennkraftmaschine
GB9707387D0 (en) * 1997-04-11 1997-05-28 Clancy Limited G Hydraulic tappet assembly
KR100486846B1 (ko) * 1997-11-29 2005-08-24 국방과학연구소 선배열음탐기의오일충전용체크밸브구조
DE102006037816A1 (de) * 2006-08-12 2008-02-14 Schaeffler Kg Hubübertragungsvorrichtung mit hydraulischem Ventilspielausgleichselement
DE102019105607A1 (de) * 2019-03-06 2020-01-09 Schaeffler Technologies AG & Co. KG Hydraulisches Abstützelement für einen Ventiltrieb einer Brennkraftmaschine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8902780U1 (de) * 1989-03-08 1989-04-20 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Sich selbsttätig hydraulisch einstellender Ventilstößel

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2595583A (en) * 1949-09-26 1952-05-06 Johnson Products Inc Oil supply for hydraulic tappets
IT7853889V0 (it) * 1978-11-15 1978-11-15 Fiat Spa Punteria idraulica a ripresa automatica del gioco per motori a combustione interna con alberi a camme in testa
US4392462A (en) * 1980-12-22 1983-07-12 Stanadyne, Inc. Inverted bucket tappet with seal
US4463713A (en) * 1981-09-02 1984-08-07 Riv-Skf Officine Di Villar Perosa S.P.A. Hydraulic tappet with automatic taking up of the clearance for endothermic engines
IT8453964V0 (it) * 1984-10-25 1984-10-25 Fiat Auto Spa Valvola oleodinamica in particolare per una punteria idraulica

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8902780U1 (de) * 1989-03-08 1989-04-20 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Sich selbsttätig hydraulisch einstellender Ventilstößel

Also Published As

Publication number Publication date
US5183016A (en) 1993-02-02
ATE110440T1 (de) 1994-09-15
JP2584569B2 (ja) 1997-02-26
EP0525284A1 (de) 1993-02-03
DE59200407D1 (de) 1994-09-29
CA2074414A1 (en) 1993-01-25
ES2059169T3 (es) 1994-11-01
DE4124484C1 (es) 1993-01-14
MX9204313A (es) 1992-11-01
JPH05195724A (ja) 1993-08-03
CA2074414C (en) 1994-10-25
BR9202047A (pt) 1993-10-05

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