EP0160287A2 - Poussoir hydraulique avec autorégulation pour moteurs à combustion interne - Google Patents

Poussoir hydraulique avec autorégulation pour moteurs à combustion interne Download PDF

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Publication number
EP0160287A2
EP0160287A2 EP85105161A EP85105161A EP0160287A2 EP 0160287 A2 EP0160287 A2 EP 0160287A2 EP 85105161 A EP85105161 A EP 85105161A EP 85105161 A EP85105161 A EP 85105161A EP 0160287 A2 EP0160287 A2 EP 0160287A2
Authority
EP
European Patent Office
Prior art keywords
chamber
piston
coupling
fact
hydraulic 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.)
Withdrawn
Application number
EP85105161A
Other languages
German (de)
English (en)
Other versions
EP0160287A3 (fr
Inventor
Franco Colanzi
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.)
SKF Industrie SpA
Original Assignee
RIV SKF Officine di Villar Perosa SpA
RIV Officine di Villar Perosa SpA
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 RIV SKF Officine di Villar Perosa SpA, RIV Officine di Villar Perosa SpA filed Critical RIV SKF Officine di Villar Perosa SpA
Publication of EP0160287A2 publication Critical patent/EP0160287A2/fr
Publication of EP0160287A3 publication Critical patent/EP0160287A3/fr
Withdrawn legal-status Critical Current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 present invention relates to a perfected hydraulic tappet with automatic slack take-up for internal combustion engines, in particular, one comprising a cup member, the latter housed in axially-sliding manner in a seat on the said engine and cooperating with a cam facing the said seat, and a piston housed in sliding manner inside the said cup member and defining with the latter a chamber filled with fluid under pressure, e.g. oil, supplied by a pipe fitted with a cut-off mem ber.
  • fluid under pressure e.g. oil
  • the aim of the present invention is to provide a hydrau lic tappet of the aforementioned type that is relatively straightforward and cheap to produce, of simple design and assembly, relatively unaffected by mechanical wear due to mutual sliding of the cam and cup member, and which provides for a high degree of efficiency and operating precision.
  • the present invention relates to a hydraulic tappet with automatic slack take-up for internal combustion engines, the said tappet comprising a cup member housed in axially-sliding manner in a seat on the said engine and cooperating with a cam facing the said seat; a piston housed in sliding manner inside the said cup member and cooperating at the bottom with a rod having one end sliding axially inside the said seat, the said piston defining, with and inside the said cup member, a chamber designed to be filled with fluid under pressure; a supply pipe for the said fluid formed at least partly through the said cup member; and a cut-off valve consisting of a ball housed in floating manner at least partly inside a truncated-cone seat which opens out at the top inside the said chamber and in which terminates the said pipe; characterised by the fact that the said cup member comprises : a first member, in turn, comprising an outer coupling and inner coupling, both cylindrical and formed coaxially in one piece, one inside the other, and an annular
  • Number 1 in Fig.1 indicates a hydraulic'tappet with auto matic slack take-up for any known type of internal combustion engine (not shown), the said tappet comprising a cup member 2 housed in axially-sliding manner inside an essentially-cylindrical seat 3 formed in the block 4 on the said known type of engine (not shown); a piston 5 housed in sliding manner inside a seat 6 in cup member 2 and cooperating at the bottom with a rod 7 having a top end sliding axially in seat 3 ; a pressure chamber 8 defined by piston 5 and member 2 , formed inside the latter and designed to be filled with pressure fluid, usually lubricating oil, for enabling mutual slid ing of member 2 and piston 5 for taking up any slack between rod 7 and cam 9 facing seat 3 and cooperating with member 2; a supply pipe 10 for the said pressure fluid; and a cut-off valve 11 on pipe 10 for enabling exclusive one-way supply of the said pressure fluid along pipe 10 into chamber 8.
  • valve 1 1 comprises a ball 1 2 of appropriate diameter and housed floating at least partly inside a truncated-cone seat 13 , the latter being arranged directly facing and communicating with chamber 8 into which it opens at the top, and being con nected at the bottom to pipe 10 terminating inside it.
  • cup member 2 comprises two separate members, 14 and 1 5 , secured integral with each other; the first defined by an essentially- flat, cylindrical plate of appropriate thickness and made from relatively hard material, e.g. by sintering hard metals; and the second defined by a load-bearing structure preferably made of steel or any other material of lower cost and hardness than the material of plate 14 .
  • member 15 comprises an essentially-cylindrical outer coupling 1 6 essentially equal in diameter to seat 3 inside which coupling 1 6 is designed to slide; an inner coupling 1 8, also essentially cylindrical, fitted coaxially and concentrically inside coupling 16 and being smaller in dia meter and length as compared with the same; and an annular wall 19 connecting couplings 1 6 and 1 8, formed integral with both and arranged essentially perpendicular to the axis of the same, in such a manner as to extend essentially radially and divide coupling 1 6 internally into two cavities, the upper cavity defining chamber 8 and the lower cavity open towards seat 3 for accommodating rod 7.
  • coupling 1 8 which is thus formed integral in one piece with wall 19 and outer coupling 1 6, is provided internally with seat 6 and presents essentially the same diameter and length as cylindrical piston 5 housed in sliding manner inside it.
  • wall 19 instead of being flat, is essentially slanted so as to define an essentially conical surface 2 0 defining, at the bottom, the bottom of chamber 8 and joining up with coupling 1 8 essentially on the centre line of the latter.
  • the opposite ends, 21 and 22 , of coupling 18 thus project from wall 1 9 respectively into chamber 8 and into the said lower cavity defined inside coupling 1 6 by wall 19 .
  • the latter also separates coupling 1 6 into two opposite, cylindrical, annular ends,respectively top end 23 and bottom end 24, the latter defining laterally chamber 8 and the said lower cavity in coupling 1 6 respectively.
  • the said wall 19 is also fitted internally with pipe 1 0, the latter comprising an annular groove 25, formed externally on coupling 1 6 for a length essentially equal to the distance travelled by cup member 2 inside respective seat 3 , and a slanting radial hole 2 6 formed through wall 19 and inner coupling 18 and coming out inside seat 6 defined by the said inner coupling 1 8. on end 23 at the top, coupling 1 6 is closed off by plate 1 4 arranged facing wall 19 and thus defining the top of chamber 8.
  • the diameter of plate 14 is larger than the inside diameter of coupling 1 6 and smaller than the outside diameter of the same, i.e. the diameter of seat 3.
  • the said plate 14 presents a bevel 27 facing a respective bevel 2 8 formed on end 23 itself.
  • plate 14 and end 23 on coupling 16 are laser-welded together so that, at bevels 27 and 28, plate 14 is secured to end 23 by weld bead 29.
  • the height of chamber 8 is such that the distance between truncated-cone seat 1 3 and plate 14 is less than the diameter of ball 12 , plate 14 thus acting as a retainer for the said ball 12 which, even if housed freely inside seat 13, is thus prevented from being withdrawn from the same.
  • valve 11 is fitted directly on to piston 5 , the latter consisting of a solid cylindrical body the bottom face 30 of which rests on rod 7 and the top face 31 of which is arranged facing chamber 8, in such a manner as to define the lat ter at coupling 1 8 by essentially defining a sliding wall by which the said chamber 8 is closed off.
  • Truncated-cone seat 13 is formed on face 3 1 , inside piston 5, and is connected to radial hole 2 6 by a further pair of holes, one radial 3 2 and one axial 33, formed through piston 5.
  • Coupling 18 is provided on bottom end 22 with a check ring 34 designed to act as a limit stop for piston 5.
  • Face 31 on piston 5 defines an active surface designed to detect the pressure inside chamber 8 and so cause piston 5 to slide inside seat 6 and consequent displace ment of member 2 and piston 5 , which are maintained con tacting cam 9 and rod 7 respectively by the pressure in side chamber 8, thus enabling recovery of any slack be- tveen cam 9 and rod 7 due to wear on tappet 1 and/or machining tolerances.
  • Tapper 1 operates in known manner and will be clear from the foregoing description, When the engine is started up, lubricating oil under pressure is fed along pipe 10 into seat 13 where it lifts ball 12 so as to flow into chamber 8 until the latter is full. As the said chamber 8 is being filled, the pressure exerted on the inner face of plate 1 4 and on the active face 3 1 of piston 5, as already described, causes member 2 and piston 5 to separate, thus enabling any slack to be taken up. During ope ration of tappet 1, chamber 8 remains full of oil, in that the latter is prevented from flowing out through seat 13 by ball 1 2 which is forced against seat 13 in fluidtight manner by the pressure in chamber 8, just like any other type of non-return valve.
  • chamber 8 clearly presents a considerable volume in relation to the size of piston 5.
  • ball 12 being provided with no mechanical retaining means mounted inside chamber 8, reacts readily to any change in oil pressure inside chamber 8 or pipe 1 0.
  • Tappet 1 according to the present invention thus clearly provides for a high degree of reliability, fast operation and far greater efficiency as compared with known tappets.
  • constructing cup member 2 in two separate parts having different mechanical characteristics and laser-welded together provides for simplifying manufacture of tappet 1 , reducing cost and increasing working life by reducing wear on member 2, the said reduction in wear being provided for by cam 9 cooperating directly with plate 14 having superior mechanical characteristics as compared with the rest of member 2 .
  • Fig. 2 shows a hydraulic tappet la consisting of a possible variation of tappet 1 as already described.
  • Tappet 1a differs from tappet 1 solely as to the shape of annular wall 19 defining chamber 8 at the bottom and to the position of valve 1 1 .
  • the latter in fact, is fitted on to cup member 2, in that seat 13 is formed on surface 20 of wall 19 , the said surface 2 0 being essentially flat instead of conical as on tappet 1 in Fig. l .
  • pipe 1 0 comprises only radial hole 26 and seat 13 is formed next to outer coupling 16.
  • End 23 on the latter is relatively short and essentially equal in length to the height of chamber 8, so that the distance between seat 13 and plate 14 is less than the diameter of ball 12, as in the case of tappet 1, thus resulting in plate 14 acting as a retaining member for the said ball 1 2.
  • piston 5 obviously having no holes 32 or 33 as on the similar piston on tappet 1 , is provided towards chamber 8 with a cavity 35 occupying most of the volume on piston 5 and defined by a surface 3 6, the latter being truncated-cone in shape in the non-limiting example shown and defining the active surface on piston 5 for detecting the pressure inside chamber 8.
  • All the remaining details on tappet l a, as well as its operation, are identical to those described in connection with tappet 1.
  • tappet 1 a is even more straightforward in design, owing to the relatively short length of pipe 1 0, thus resulting in even lower production cost.
  • Tappet 1 on the other hand, has the advantage of being provided with a sealing'seat on the piston, thus enabling lower production cost, should tappets for different engine types, i.e. having seats 3 of different sizes, need to be produced. If such is the case, the size of cup member 2 , which is relatively cheap, is simply adapted and the same size piston 5 used on all the tappets, thus enabling obvious scale economy.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP85105161A 1984-05-03 1985-04-26 Poussoir hydraulique avec autorégulation pour moteurs à combustion interne Withdrawn EP0160287A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT5333184U IT8453331V0 (it) 1984-05-03 1984-05-03 Punteria idraulica a ripresa automatica di gioco di tipo perfezionato per motori endotermici
IT5333184U 1984-05-03

Publications (2)

Publication Number Publication Date
EP0160287A2 true EP0160287A2 (fr) 1985-11-06
EP0160287A3 EP0160287A3 (fr) 1987-01-14

Family

ID=11281851

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85105161A Withdrawn EP0160287A3 (fr) 1984-05-03 1985-04-26 Poussoir hydraulique avec autorégulation pour moteurs à combustion interne

Country Status (2)

Country Link
EP (1) EP0160287A3 (fr)
IT (1) IT8453331V0 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5081976A (en) * 1989-06-16 1992-01-21 Mercedes-Benz Ag Bucket tappet for an internal combustion engine with overhead camshaft
GB2279719A (en) * 1993-07-09 1995-01-11 Clancey G Ltd An adjustable cam follower

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1241634A (en) * 1968-04-19 1971-08-04 Motomak Valve tappet for engines having an overhead camshaft
DE2952290A1 (de) * 1978-12-26 1980-07-17 Eaton Corp Nockenfolger
EP0052704A1 (fr) * 1980-11-21 1982-06-02 RIV-SKF OFFICINE DI VILLAR PEROSA S.p.A Poussoir à auto-régulation hydraulique pour moteurs thermiques
EP0055399A1 (fr) * 1980-12-29 1982-07-07 Eaton Corporation Dispositif hydraulique de rattrapage de jeu comprenant une butée de plongeur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1241634A (en) * 1968-04-19 1971-08-04 Motomak Valve tappet for engines having an overhead camshaft
DE2952290A1 (de) * 1978-12-26 1980-07-17 Eaton Corp Nockenfolger
EP0052704A1 (fr) * 1980-11-21 1982-06-02 RIV-SKF OFFICINE DI VILLAR PEROSA S.p.A Poussoir à auto-régulation hydraulique pour moteurs thermiques
EP0055399A1 (fr) * 1980-12-29 1982-07-07 Eaton Corporation Dispositif hydraulique de rattrapage de jeu comprenant une butée de plongeur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5081976A (en) * 1989-06-16 1992-01-21 Mercedes-Benz Ag Bucket tappet for an internal combustion engine with overhead camshaft
GB2279719A (en) * 1993-07-09 1995-01-11 Clancey G Ltd An adjustable cam follower

Also Published As

Publication number Publication date
IT8453331V0 (it) 1984-05-03
EP0160287A3 (fr) 1987-01-14

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Inventor name: COLANZI, FRANCO