US3322104A - Tappet - Google Patents

Tappet Download PDF

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Publication number
US3322104A
US3322104A US553548A US55354866A US3322104A US 3322104 A US3322104 A US 3322104A US 553548 A US553548 A US 553548A US 55354866 A US55354866 A US 55354866A US 3322104 A US3322104 A US 3322104A
Authority
US
United States
Prior art keywords
tappet
groove
oil
cylindrical
push rod
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
US553548A
Other languages
English (en)
Inventor
Jr Roy F Abell
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.)
Eaton Corp
Original Assignee
Eaton Yale and Towne Inc
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 Eaton Yale and Towne Inc filed Critical Eaton Yale and Towne Inc
Priority to US553548A priority Critical patent/US3322104A/en
Priority to SE4317/67A priority patent/SE323243B/xx
Priority to CH462567A priority patent/CH454532A/de
Priority to GB14923/67A priority patent/GB1148331A/en
Application granted granted Critical
Publication of US3322104A publication Critical patent/US3322104A/en
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
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/107—Lubrication of valve gear or auxiliaries of rocker shaft bearings
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/34—Lateral camshaft position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement

Definitions

  • Papenguth teaches a hollow push rod and a floating plate-like valve adapted to restrict oil flow into the push rod for delivery to the rocker arm during operation of the valve train.
  • Papenguth structure is disclosed in conjunction with a hydraulic valve lifter, the principles of metering lubricant through a hollow push rod is equally applicable to both mechanical valve lifters and tappets.
  • FIGURE 1 is an elevational view, partly in section, of a pair of tappets constructed according to this invention in a V-8 internal combustion engine block.
  • FIGURE 2 is a sectional view of a tappet constructed according to one embodiment of this invention.
  • FIGURE 3 is a sectional view of a tappet constructed according to a second embodiment of this invention.
  • FIGURE 1 there is shown an engine block having a pair of tappets 12 and 14, constructed according to this invention, received in cylindrical bores 16.
  • One end of each of said tappets 12 and 14 includes a cam engaging face 18 adapted to abut cam shaft 20.
  • Cam shaft 20 includes a base circle portion 22 and a lift portion 24.
  • tappet 12 is engaging the base circle portion 22 of cam shaft 20 and tappet 14 is engaging the lift portion 24 of cam shaft 20.
  • Abutting portions of the tappets near the other ends thereof are push rods 26 and 28.
  • Push rods 26 and 28 are adapted to engage suitable rocker arms to complete the valve train linkage from the cam shaft to the valve.
  • each of the push rods 26 and 28 Defined in each of the push rods 26 and 28 is a passageway 30 for the purpose of conducting oil from the tappet to the rocker arm to thereby lubricate the points of contact of the push rod and the rocker arm as well as the valve and the rocker arm.
  • this invention is concerned primarily with the means by which oil flow from the engine to the push rod is metered or controlled, only that portion of the valve train linkage will be described.
  • tappets 12 and 14 are identical and include a first external annular groove 32 and a second external annular groove 34. Separating grooves 32 and 34 is a cylindrical metering land 36.
  • the engine oil gallery passageway 38 Intersecting the cylindrical bores 16 so as to overlie the first groove 32 of each tappet is the engine oil gallery passageway 38. As shown in FIGURE 1, the oil gallery 38 intersects the center line of each of the cylindrical tappet receiving bores 16 of the engine block 10. Gallery 38 is thus parallel to the axis of cam shaft 20.
  • the tappet structure of FIGURE 2 includes a tappet body 38 having a cam engaging surface 40 at one end thereof.
  • the valve actuating push rod is adapted to be received in a socket element 42 generally defined as a T-shaped element.
  • Socket element 42 is suitably seated on shoulders 44 defined on the interior surface of the tappet body 38. Retaining the socket element 42 in place is a snap ring 46 suitably received in a recess 48 of the tappet body 38.
  • a generally spherical bearing surface 50 adapted to receive one end of a hollow push rod.
  • a passageway 54 designed to provide communication between the interior 52 of the tappet body 38 and the passageway of the hollow push rod.
  • the exterior of tappet body 38 of FIGURE 2 is generally cylindrical and includes a first annular groove 32 and a second annular groove 34. Separating grooves 32 and 34 is a cylindrical land 36. Provided in the tappet body 38 so as to provide communication between the interior 52 of the tappet and the second groove 34 is a radial passageway 56.
  • FIGURE 1 wherein the operation of the embodiment of the tappet shown in FIG- URE 2 will be described.
  • the exterior configuration of the tappets 12 and 14 as shown in FIG- URE 1 is identical to the exterior configuration of the tappet as shown in FIGURE 2.
  • oil is caused to flow in the oil gallery 38 at a pressure of approximately 45 to 50 psi.
  • groove 32 is in communication with the gallery 38, an oil ring or reservoir is caused to be collected in the groove 32.
  • the groove 32 provides two functions in the operation of the tappet of this invention. Because the gallery 38 intersects the center line of the tappet receiving bores 16, the first function of the groove 32 is to provide a communication means from one cylindrical bore 16 to an adjacent cylindrical bore 16.
  • oil entering one portion of cylindrical bore 16 may be conducted halfway around the exterior of the tappet in groove 32 and continue in Patented May 30, 1967 the gallery 38 to an adjacent cylindrical bore 16.
  • a second function of the groove 32 is to provide a ring of oil at uniform pressure so that a controlled flow of oil may be established to the rocker arm.
  • the control means of this invention is the cylindrical metering land 36.
  • a controlled flow of oil may thereby be established to the rocker arm. Oil is thus caused to flow from the first groove 32 across the metering land 36 into the second groove 34.
  • Groove 34 might appropriately be called a collecting groove as a ring of oil is thereby established in the groove 34.
  • the oil in groove 34 may thereafter be conducted through the radial passageway 56 into the interior of the tappet.
  • a flow of pressurized oil into the passageway 56 will eventually fill the interior 52 of the tappet body 38. After filling of the interior of the tappet a continued input of oil into the tappet will result in a flow through the passageway 54 of the socket element 42 and thereafter into the hollow push rod to the rocker arm.
  • FIGURE 3 there is shown a second embodiment of this invention. Wherein it is possible, like reference characters will be used in FIGURE 3 as were used in FIGURES 2 and 1.
  • the embodiment of FIGURE 3 includes a tappet body 58 having a generally external cylindrical surface provided with a first annular groove 32 and a second annular groove 34. Separating annular grooves 32, 34 is a cylindrical land 36.
  • the external configuration of the tappet embodiment of FIGURE 3 is therefore identical to the external configuration of the tappet embodiment of FIGURE 2.
  • Tappet body 58 of FIGURE 3 includes a cam engaging face 40 at one end thereof and a recessed portion 60 at the other end thereof. Recess 60 extends approximately midway into the tappet body 58 and is terminated by a generally spherical bearing surface 62.
  • Bearing surface 62 is adapted to receive one end of a hollow push rod in a manner similar to the bearing surface 50 of FIGURE 2.
  • an axial passageway 64 which intersects a radial passageway 56.
  • the operation of the tappet embodiment of FIGURE 3 is similar to that described with reference to the embodiment of FIG- URE 2.
  • the oil gallery 38 deposits a ring of oil in the first annular groove 32. Due to the slight clearance between the cylindrical land 36 and the Walls of the cylindrical bore 16, oil is caused to flow from the first annular groove 32 to the second annular groove 34 wherein it is conducted by means of passageway 56 and passageway 64 to the bearing surface 62. Because the oil is pressurized it will thereafter be conducted through the hollow push rod to the rocker arm to lubricate the points of contact of the hollow push rod and the rocker arm as well as the valve and the rocker arm.
  • the oil gallery Since the function of the cylindrical land surface 36 is to meter or control the flow of oil from the annular groove 32 to the annular groove 34, the oil gallery must be positioned with respect to the tappet such that at no time during the operation of the valve actuating mechanism the oil gallery is in direct communication with the second annular groove 34. Obviously, if the oil gallery directly communicates with the second annular groove 34, the means to control or meter the flow of oil will have been by-passed and, thus, an uncontrolled flow will be established between the oil gallery and the hollow push rod. Such uncontrolled flow is undesirable in that excessive oil is thereby conducted to the rocker arm.
  • the oil gallery 38 is positioned such that at all times during reciprocating movement of the tappet the gallery will partly overlie the first annular groove 32 without overlying the second annular groove 34.
  • tappet 12 of FIGURE 1 it will be seen that as tappet 12 is at rest on the base circle 22 of the cam shaft 20, the oil gallery 38 almost completely overlies the first annular groove 32.
  • tappet 14 of FIG- URE 1 it may be seen that as said tappet is at rest on the lift portion 24 of the cam shaft 20, oil gallery 38 at least partially overlies the annular groove 32 while at the same time overlying a portion of the cylindrical land 36. A portion of the cylindrical land 36 is therefore still available for purposes of metering flow of oil from groove 32 to groove 34.
  • the amount of oil that will flow past the metering land 36 during operation of the internal combustion engine is a function of (a) the engine oil pressure, (b) the clearance between the metering land and the walls defining the cylindrical bore 16, (c) the width of the meter land 36, (d) the viscostiy and cleanliness of the oil and (e) the external diameter of the tappet.
  • Operating oil pressure in an internal combustion engine is approximately 45-50 p.s.i. With a tappet diameter of 0.75-1.00 inch, it has been found that a suitable flow of oil may be established to the rocker arm with a metering land band width of inch, and a clearance of .0015 inch between the metering land and the walls of the tappet receiving bore.
  • the heart of the oil metering structure of this invention is therefore the metering land 36 of FIGURES 2 and 3.
  • a carefully controlled clearance must therefore exist between the metering land 36 and the cylindrical tappet receiving bore of the engine block.
  • Cylindrical lands 66 and 68 of FIGURES 2 and 3 serve to align the tappet in the tappet receiving bore as well as provide guide means for reciprocation of the tappet in the tappet receiving bore during operation of the valve train.
  • the external diameter of the metering land 36 may be equal to or less than the external diameter of cylindrical lands 66 and 68. Production of the tappet of this invention may be greatly simplified, of course, if the external diameter of land 36, 66 and 68 are equal.
  • the critical clearance for purposes of metering oil to the rocker am is the clearance between the metering land and the walls of the tappet receiving bore. Should leakage of oil past the upper and lower cylindrical lands of the tappet become excessive then these clearances may be reduced without affecting the clearance between the metering land and the tappet receiving bore.
  • this invention be considered limited to the environment in which a tappet is received in a cylindrical bore in an engine block. Where, for instance, tolerances in the manufacturing of the engine block are excessive, it may prove impractical to achieve a regulated clearance at the oil metering land of the tappet due to the wide fluctuations in the internal diameter of the tappet receiving bore. In such an instance it is conceivable that a cylindrical bore liner may be utilized between the cylindrical bore of the engine block and the tappet to thus achieve a controlled oil metering clearance between the liner and the tappet. Communication between the oil gallery and the tappet groove may be established by means of a passageway in the liner.
  • a lubricating system for an engine or the like including a reciprocatedly actuated tappet, a rocker, and a hollow push rod drivingly connecting said rocker to the tappet and constituting an oil conductor between said rocker and said tappet, the combination of:
  • said tappet including,
  • second communication means between said fluid passageway and said first groove for providing direct communication only between said fluid passageway and said first groove, while providing indirect communication to said second groove only via said flow metering means.
  • said tappet guide means is defined by a cylindrical bore in said engine block and said second communication means is defined by an opening in the wall defining said cylindrical bore, at least a portion of said opening overlying said first groove of said tappet at all times during reciprocation of the tappet.
  • said bearing surface of said tappet is further defined by a T-shaped socket element seated on shoulders of an internal wall of said tappet, said socket element defining a bearing surface to receive one end of a hollow push rod, and said first communication means is further defined by a passageway in said socket opening into the interior of said tappet and a passageway in said tappet extending from said second groove to said interior.
  • said tappet including,
  • a cylindrical tappet body with a cam engaging face on one end thereof and a recessed portion at the other end thereof,
  • the clearance between said cylindrical land surface and said cylindrical bore being in the range 0.0005 to 0.0025 inch to permit a controlled flow of oil from said oil gallery passageway to said hollow push rod.

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)
US553548A 1966-05-27 1966-05-27 Tappet Expired - Lifetime US3322104A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US553548A US3322104A (en) 1966-05-27 1966-05-27 Tappet
SE4317/67A SE323243B (de) 1966-05-27 1967-03-29
CH462567A CH454532A (de) 1966-05-27 1967-03-31 Einrichtung zur Regelung der Schmierölzufuhr zum Schwinghebel der Ventilsteuerung in Brennkraftmaschinen
GB14923/67A GB1148331A (en) 1966-05-27 1967-03-31 Lubrication device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US553548A US3322104A (en) 1966-05-27 1966-05-27 Tappet

Publications (1)

Publication Number Publication Date
US3322104A true US3322104A (en) 1967-05-30

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Application Number Title Priority Date Filing Date
US553548A Expired - Lifetime US3322104A (en) 1966-05-27 1966-05-27 Tappet

Country Status (4)

Country Link
US (1) US3322104A (de)
CH (1) CH454532A (de)
GB (1) GB1148331A (de)
SE (1) SE323243B (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3437080A (en) * 1967-11-13 1969-04-08 Eaton Yale & Towne Valve tappet
US3448730A (en) * 1967-06-07 1969-06-10 Eaton Yale & Towne Hydraulic valve lifter
US3450228A (en) * 1967-07-19 1969-06-17 Gen Motors Corp Hydraulic valve lifter
US4009696A (en) * 1975-11-20 1977-03-01 Sealed Power Corporation Hydraulic lash adjuster with internal oil pressure control
USD387066S (en) * 1996-06-10 1997-12-02 Cheek Sr John B Internal combustion engine roller tappet
US6871622B2 (en) 2002-10-18 2005-03-29 Maclean-Fogg Company Leakdown plunger
US7028654B2 (en) 2002-10-18 2006-04-18 The Maclean-Fogg Company Metering socket
US7128034B2 (en) 2002-10-18 2006-10-31 Maclean-Fogg Company Valve lifter body
US7191745B2 (en) 2002-10-18 2007-03-20 Maclean-Fogg Company Valve operating assembly
US7273026B2 (en) 2002-10-18 2007-09-25 Maclean-Fogg Company Roller follower body
WO2020167290A1 (en) * 2019-02-12 2020-08-20 Cummins Inc. Integrated tappet assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3333844A1 (de) * 1983-09-20 1985-03-28 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Zylinderkopf fuer eine vorzugsweise mehrzylindrige brennkraftmaschine
JPS61167109A (ja) * 1985-01-18 1986-07-28 Toyota Motor Corp 内燃機関のメカニカルバルブリフタ装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2145484A (en) * 1937-01-25 1939-01-31 Charles E Johnson Hydraulic tappet
US2682865A (en) * 1952-05-08 1954-07-06 Voorhies Carl Valve lifter
DE925866C (de) * 1951-02-17 1955-03-31 Kloeckner Humboldt Deutz Ag Hydraulischer Stoessel
US3089473A (en) * 1962-02-01 1963-05-14 Johnson Products Inc Mechanical tappet
US3262434A (en) * 1963-03-02 1966-07-26 Motomak Motorenbau Maschinenun Self-adjusting hydraulic valve lifter for piston engines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2145484A (en) * 1937-01-25 1939-01-31 Charles E Johnson Hydraulic tappet
DE925866C (de) * 1951-02-17 1955-03-31 Kloeckner Humboldt Deutz Ag Hydraulischer Stoessel
US2682865A (en) * 1952-05-08 1954-07-06 Voorhies Carl Valve lifter
US3089473A (en) * 1962-02-01 1963-05-14 Johnson Products Inc Mechanical tappet
US3262434A (en) * 1963-03-02 1966-07-26 Motomak Motorenbau Maschinenun Self-adjusting hydraulic valve lifter for piston engines

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3448730A (en) * 1967-06-07 1969-06-10 Eaton Yale & Towne Hydraulic valve lifter
US3450228A (en) * 1967-07-19 1969-06-17 Gen Motors Corp Hydraulic valve lifter
US3437080A (en) * 1967-11-13 1969-04-08 Eaton Yale & Towne Valve tappet
US4009696A (en) * 1975-11-20 1977-03-01 Sealed Power Corporation Hydraulic lash adjuster with internal oil pressure control
USD387066S (en) * 1996-06-10 1997-12-02 Cheek Sr John B Internal combustion engine roller tappet
US7028654B2 (en) 2002-10-18 2006-04-18 The Maclean-Fogg Company Metering socket
US6871622B2 (en) 2002-10-18 2005-03-29 Maclean-Fogg Company Leakdown plunger
US7128034B2 (en) 2002-10-18 2006-10-31 Maclean-Fogg Company Valve lifter body
US7191745B2 (en) 2002-10-18 2007-03-20 Maclean-Fogg Company Valve operating assembly
US7273026B2 (en) 2002-10-18 2007-09-25 Maclean-Fogg Company Roller follower body
US7281329B2 (en) 2002-10-18 2007-10-16 Maclean-Fogg Company Method for fabricating a roller follower assembly
US7284520B2 (en) 2002-10-18 2007-10-23 Maclean-Fogg Company Valve lifter body and method of manufacture
WO2020167290A1 (en) * 2019-02-12 2020-08-20 Cummins Inc. Integrated tappet assembly

Also Published As

Publication number Publication date
GB1148331A (en) 1969-04-10
SE323243B (de) 1970-04-27
CH454532A (de) 1968-04-15

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