US2053743A - Valve operating mechanism - Google Patents

Valve operating mechanism Download PDF

Info

Publication number
US2053743A
US2053743A US679633A US67963333A US2053743A US 2053743 A US2053743 A US 2053743A US 679633 A US679633 A US 679633A US 67963333 A US67963333 A US 67963333A US 2053743 A US2053743 A US 2053743A
Authority
US
United States
Prior art keywords
oil
cylinder
chamber
plunger
piston
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
US679633A
Other languages
English (en)
Inventor
Robert C Russell
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.)
Individual
Original Assignee
Individual
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
Priority to BE398430D priority Critical patent/BE398430A/xx
Application filed by Individual filed Critical Individual
Priority to US679633A priority patent/US2053743A/en
Application granted granted Critical
Publication of US2053743A publication Critical patent/US2053743A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01L1/2416—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device attached to an articulated rocker
    • H—ELECTRICITY
    • H03—ELECTRONIC CIRCUITRY
    • H03J—TUNING RESONANT CIRCUITS; SELECTING RESONANT CIRCUITS
    • H03J1/00—Details of adjusting, driving, indicating, or mechanical control arrangements for resonant circuits in general
    • H03J1/02—Indicating arrangements
    • H03J1/04—Indicating arrangements with optical indicating means
    • H03J1/044—Illumination of the tuning dial; On and off switching of the illumination; Circuits related with illumination

Definitions

  • This invention relates to valve operating mechanism and more particularly to hydraulic self adjusting or compensating rocker arms used principally in connection with internal combustion motors to automatically maintain a noclearance operating engagement between all parts of said valve mechanism.
  • a main purpose of. the invention is to produce a new and useful hydraulic rocker arm which is adapted for use with conventional or standard cam operated valve means employed in internal combustion engines and to compensate for variation in length of the operating parts due to wear and temperature changes.
  • the invention provides a hydraulic rocker arm, rugged in construction, having few parts, economical to manufacture, which is positive in operation in carrying the load or pressure of the springloaded engine valve reacting against the enginedriven cam, which silences the valves and their operating mechanism, and increases engine efliciency.
  • a characteristic object of the invention is to produce a hydraulic rocker arm having its automatic self adjusting parts or compensating means carried within one of the lever arms of the rocker and receiving its working supply of oil from the rock shaft on which the arm oscillates under the action of the engine driven cam to open the spring closed engine valve and-carry its load and permit said valve tosoftly close on its seat thru an incompressible oil body confined in an automatic self adjusting hydraulic compression or pressure chamber, whereby all parts of the mechanism are held to zero-clearance or no-clearance engagement.
  • a further object is to produce an automatic self adjusting rockerarm carried on a fixed axis as distinguished from known types which oscillate on an eccentric bearing wherein said eccentric automatically moves the rocker arm up and down in relation to the valve stem and push rod to maintain zero-clearance between the operating parts.
  • One example of my invention as illustrated herein, carries out its automatic function without recourse to a self adjusting rocker arm bearing or eccentric, by providing a compensating unit in direct engagement with either the valve stem or push rod. Consequently, I make use of the conventional bearing now in general use to mount my automatic rocker in operating position and thus avoid undue changes from standard engine design when I install my rocker arms on internal combustion engines.
  • Another object is to produce ahydraulic rocker arm having compensating instrumentalities including means acting to positively expel the air, or the maximum thereof, from its hydraulic compression chamber, prior to the oil filling operation, to thus avoid entrapped or occluded gas and air bubbles, and by which is secured a positive and solid oil or liquid body thru which to transmit the force, or a part thereof, from the rotating cam to the reciprocating valve to open or actuate the latter against the compression of its closing spring.
  • a still further object is to produce a rocker arm having a combination of hydraulic and mechanical means to reduce the pressure on the oil,5 within the self adjusting hydraulic compression chamber, the result of which is to minimize the tendency of the oil to escape therefrom as well as lowering the tendency to aerate and emulsify the Oil.
  • the same feature also ciples thereof.
  • An additional object is to produce mechanical leverage means for relieving or minimizing the pressure on the oil in the hydraulic chamber, and said leverage means carries and transmits the major portion of the load of the spring-loaded valve, the operation of such leverage means generating a certain amount of friction; and thus the mechanical leverage and the friction serve to relieve the hydraulic compression chamber of the greater portion of the valve and cam load.
  • my compensating rocker arm gains all the advantages of a hydraulic self adjusting means but retains the positiveness of mechanical means for transmitting the major operating forces.
  • Another object is to produce a rocker arm the self adjusting means of which lends itself well to manufacturing conditions, whereby it may be conveniently produced with either a low or high compression hydraulic chamber, depending on which type or form appears most desirab e from the standpoint of performance for different uses and varying types of engines.
  • Fi ure 1 shows a side elevation diagram of a com lete valve operating mechanism including a hydraulic rocker arm in partial longitudinal section.
  • the hydraulic compensatng chamber is a low pressure form and shown full of oil with the self adjusting means in fully extended position, all parts in no-clearance engagement, and thus compensated for variation in length of all parts.
  • Figure 2 shows a rear view of the rocker arm, as seen from the left in Figure 1, and the upper end of a push rod in working engagement therewith.
  • Fi ure 3 shows a cross section on the line 3-3 of Fi ure 1, except there is shown how an oil feed groove may be formed in a rock shaft, instead of in the rocker arm hub in Figure 1.
  • Figure 4 is a plan view of the rocker arm mounted on a broken away rock shaft portion.
  • Figure 5 shows an exploded or disassembled view of the rocker arm with its self adjusting parts drawn outwardly from the rocker arm cylinder and hydraulic compression chamber and arranged in the order of which said parts are adapted to be assembled in the cylinder.
  • Figure 6 is a side longitudinal sectional view of the rocker arm self adjusting parts in fully closed or compressed position with its hydraulic compression or oil compensating chamber shown dry and without oil therein, the ball check valve being unseated preliminary to taking in a charge of oil.
  • This view shows the compression chamber collapsed to its limit thus expelling all air by leaving no void spaces or air pockets therein, a function of the maximum-displacement chamber means, just prior to sucking in a full charge of oil.
  • Figure 7 is a cluster view of a stationary washer or plug adapted to be disposed within the hydraulic compression chamber to act as a spring seat and to hold the spring away from the ball as well as retaining the latter within a somewhat limited space though free for movement, and having oil passages therethrough.
  • Figure 8 is a side view of a similar rocker arm, but showing a modification in the compensating parts by which all the load, other than that absorbed by friction of the leverage wedging means, is transmitted thru a high compression hydraulic chamber and then to the valve by 45- degree wedge angle means. Consequently this is a high compression form of the hydraulic rocker arm, while the other views show the low compression type.
  • Figure 9 illustrates another modification having features especially for retaining the compensating parts in place after assembly of the complete rocker arm but before it is installed on an engine or the push rod is set in place.
  • a conventional engine cylinder head 2 having an inlet or exhaust port seat 3, as the case may be.
  • a spring-loaded poppet valve 4 with its stem 5 is normally seated by the usual valve closing spring 6.
  • a rocker arm 1 has its hub 8 oscillating on a tubular rock shaft 9 supported above the engine cylinder 2 in any approved manner, as by a bracket l8.
  • the self adjusting means is compactly arranged within the rear end l2 of the rocker arm which is tubular or bored to form a cylinder I3.
  • the rocker includes a central bearing hub 8 carrying a solid arm 1 and a tubular arm l2.
  • a push rod I4 is interposed between the rocker arm and the engine cam l5 to actuate said rocker arm 1 which constantly engages the valve 5.
  • a valve tappet I6 reciprocates in a bearing guide I1 usually carried in the crank case of an internal combustion engine.
  • the tappet sleeve I 6 acts as a cam follower to transmit the cam action and load to the push rod I4 and thence to the rocker arm and the spring-loaded engine valve 4, 6.
  • a conventional rocker arm 1 and the like ordinarily has a clearance space between it and the valve 5 or between the push rod M and arm end l2 to insure the seating of the valve under all operating conditions and consequently an operating backlash occurs.
  • the hydro-mechanical self adjusting rocker arm comprising this invention automatically and continuously adjusts out the above mentioned conventional operating clearances and back lash, occupies very little space, silences the valve operation, and improves the performance of an engine.
  • My new compensating means is arranged within a cylinder l3 bored into one of the lever arms of the rocker, say the rear arm I 2, and positively maintains the front arm I in zero or no-clearance engagement with the valve stem 5 and also holds the push rod ends in close working no-clearance engagement with the rocker arm and cam means under any and all operating conditions, regardless of elongation or contraction of the push rod I 4, the valve stem 5 and other parts, or due to the wear' of the mechanism or the :bearings thereof.
  • the compensating rocker armi'bore or cylinder l3 opens at its innermost or bottom end thru an: oil inlet port or ball seat'20' into an oil channel2
  • the hub groove 22 connects with an oil hole 23 formed thru the wall of a hollow rock shaft 9 and thence leads into the central oil passage 24 of said shaft.
  • this modification shows a plain bear- .ing rocker arm hub 26 adapted to oscillate-upon a circumferentially grooved rock shaft 21..
  • this rock shaft 2! is. made with .an external oil feed groove 28 adapted tocommunicate with the same longitudinaloil passage 2
  • This form of construction is preferred in some instances so as to produce a plain bearing rocker arm'hub 26 'journalled to oscillate upon the grooved rock shaft 21 so that the two oil'feed'passages 2
  • a ball check valve 33 normally rests on its port seat 2
  • This ball retainer and spring seat is enlarged in Figure 7 and 'its'reference character 32 points to the flange thereof against which a spring rests, as later described.
  • the above named washer 32 may'begrooved at 33 on its flat face adjacent the ball check 30 to provide limited movement of said ball check in respect to its oil inlet port or seat 23 of the latter.
  • the grooves 33 form oil passages to afford a ready flow of oil thru the washer 32 since the latter is disposed within the hydraulic oil chamber 3
  • Free movement of the ball 39 is shown in Figures 6 and 9 where the unrestrained ball check 30 is unseated and has dropped to rest against its retainer washer 32 due to the fact that no oil is present in the compression chamber 3
  • the spring-seat. 32 may to advantage be :providedwith a central boss 34, see enlarged views in Figure'l, directed outwardly toward the 'open endof the cylinder "bore l3 in the rocker arm.
  • This piston 35, 31 is disposed against-the outer free end of 'the'spring 35 and is adapted. to move in'the cylinder
  • the piston 35als o sets off or defines the front end of the low compressiori hydraulic compensating chamber 3
  • the wedge plunger 38, 39 serves the useful purpose of reducing the operating load and thrust'on the entrapped-oil in the hydraulic chamber'3l, thereby prov'iding'a low compression chamber 3
  • the angle at 39 may range somewhere between 15 and 35 degrees,'the lower figure'approachi'ng the sticking'or nonsliding point, while the higher figure begins to transmit considerable pressure to'the oil in the hydraulic chamber; and a satisfactory 'com'pro mise angle is about 20 degrees.
  • the two spring bosses 34 and 31 come together, one abutting the other, and the surrounding spring 35 is so designed and constructed with the correct number of coils and proper diameter as to completely fill all space or close up said space within the oil compression chamber 3
  • the spring is nested solid and leaves no air space around the bosses when they come together, as in Figure 6.
  • the oil piston 36 is always placed in the cylinder with this air escapement 29 in uppermost position and it is found that it remains and operates in that position. Should any air remain in the compression chamber 3
  • a further characteristic built into my hydraulic rocker arm is its low or small capacity hydraulic or compression chamber formed by arranging the piston 36 to have a short stroke.
  • this plan of construction aids in overcoming the difliculties experienced with air entrapped inside the oil chamber so that should any air remain therein despite the provisions discovered and provided thereagainst in my invention, it is found to do little harm and not interfere with good performance.
  • the maximum displacement characteristics of my invention and the air bleed 29 fail to prevent a retention of a slight trace of occluded air or a gas bubble in the compression chamber 3
  • the compensating cylinder I3 is provided with a plunger opening 43 in its lower side and at the rear end thereof.
  • a self adjusting wedge plunger 44 is movably confined in the hole 43 and coacts with the first named compensating wedge 38.
  • the upper end of the wedge plunger 44 is made with a bevel or angular face 45 on the same angle, about 20 degrees, to ride against the face 39 of the wedge plunger 38.
  • the lower end of this wedge plunger 44 is made with a ball socket 46.
  • the wedge plunger 44 is positively retained in its operating position, coaxially with the push rod 4 and at right angles to the axis of the rocker arm, by reason of the guide hole 43 in the cylinder 3 and said plunger 44 is adapted to compensate or move in and out of said cylinder relatively to its companion wedge plunger 38.
  • the push rod I4 is ordinarily provided with a ball joint or head 41 which rests within the socket 46 of the wedge plunger 44.
  • oil grooves 40 may be made in the coacting' wedge faces-39 and 45 of the plungers and an oil hole 42 in the plunger 44 if desired. In this way, a film of oil works up the face 39 and down into theball and socket joint 46, 41 to lubricate these several parts. sufficient oil feeds or leaks past the piston 36 to lubricate the leverage wedge means 39, 45 and push rod joint 46, 41.
  • the reciprocating push rod [4 rapidly opens the engine valve 4 as the cam I4 rotates, as will be understood.
  • the major thrust of the push rod I4, required to compress the engine valve spring 6, is transmitted thru the co.- acting wedge means 44 and 38 and) directly thru the rear end I2 of the rocker arm to the valve stem 5, while the remainder and lesser portion of the cam valve spring load and thrust is transmitted directly thru the solid oil body entrapped within the low compression chamber 3
  • the comparatively flat self adjusting angle 39, 45 in relation to the axis of the cylinder I3, causes the thrust of the push rod I4 to be borne largely by the plunger 39 and transmitted directly to the rocker arm end I2, while the entrapped oil body in the low compression chamber 3
  • the pushrod l4, valve 5 and other parts may loe in contracted condition and hence are a few thousandths of an inch shorter than when they become hot.
  • the return Hence most of the load or force excompensating spring 355 had previously urged the compensating piston 36 outwardly with the result that the ball check 30 opened under suction to allow oil to flow from the passage 2
  • the push rod I4, valve 5, and other parts expand or elongate.
  • pensation of the rocker arm, for elongation of the valve mechanism follows b y reason of the fact that the load pressure exerted by the cam I5 and valvespring 6, assisted somewhat by the high speed'operation of the parts, causes the wedge 44 to creep upwardly on the wedge face 39 and thereby very gradually urging or moving the plunger 33 to the right, thus admitting the plunger 44 to retract inwardly of the rocker arm cylinder 13 in precisely the same degree or amount as elongation occurs in the push rod l4 and valve stem 5.
  • the plunger 44 moves inwardly a few thousandths of an inch, the oil in the hydraulic chamber 3
  • the wedge plunger 38 moves, for example, out several thousandths-of an inchmore and faster than the variation in length of the push rod M or valve stem 5, for example, contraction of the latter.
  • This operating ratio or relation transpires by reason of the low or flat angle 39, 45 between the'compensating' wedge plungers 38 and 44.
  • the plunger 38 moves out several thousandths of an inch and thus moves perceptibly .and sufficiently to quickly unseat the ball check 30 and draw a charge of oil into the low compression chamber 3
  • This oil is instantly trappedandbecomes a solid incompressible body whereupon the next turn of the cam lobe l5 upwardly serves to positively compress the engine valve spring 6 and open its valve because the oil body locked within the low compression chamber positively holds the wedge 38 against displacement.
  • This rocker arm has a satisfactorily long compensating range and there is no need for a manual adjustment screw in setting up and tuning the valve mechanism on an engine.
  • the self adjusting function is automatic and continuous and takes place in either direction under all working conditions. Should the push rod l4 and other parts grow in length, the wedging force of the plunger 44 against the plunger 38 urges the latter inwardly and enough oil will leak past the plunger means 36 and 38 to allow a contraction of the oil volume and body within the low compression chamber 31. Only slight oil leakage is necessary to accommodate the gradual elongation of the push rod l4 or valve stem 5. On the other hand, compensation in the other direction takes place by reason of the expansive force of the self adjusting spring 35 to keep the plunger 38 urged outwardly and maintain all parts in zero or noclearance operating engagement.
  • FIG 8 there is shown a rocker arm having a high compression hydraulic oil chamber, by reason of a change in the compensating angle on the self adjusting wedges, say about 45 degrees, instead of the low compression hydraulic chamber as first described in Figures 1 thru 6.
  • retains the compensating mechanism, comprising two wedges 52 and 53 which have their coacting wedge faces 54 formed on the 45-degree angle or more, which provides for a full load carrying capacity against and thru the oil in its high compression self adjusting hydraulic chamber 55.
  • this hydraulic rocker arm 50 and its chamber 55 is of high compression form.
  • the angle or inclined plane at 54 is about 45 degrees in relation to the axis of compensating cylinder 5
  • the leverage or pressure on the oil in this high compression chamber 55 is approximately equal to the load or pressure on the push rod 56 required to open the engine valve.
  • the pressure or operating load applied on the solid oil body in the chamber 55 is equal to the force exerted by the cam I5 to compress the engine-valve spring 6 and operate the train of mechanism, minus the operating friction present in the self adjusting unit including principally the sliding coacting wedges.
  • FIG. 9 Means to hold the parts in assembled relation
  • the same rocker arm construction having the same mode of operation, as heretofore described, comprising my compensating unit mechanism compactly arranged within a cylinder 58 of a lever arm 59, but with an added feature to hold all parts together against the expansive force of the compensating spring 63 in the hydraulic chamber.
  • a return compensating spring 63 is disposed in a low compression chamber formed at the inner end of the cylinder 58 and maintains the two wedges 60 and 6
  • This form of the invention is especially provided to retain the wedges 60 and 6
  • the expansive force of spring 63 in the arm displaces the parts and the assembly cannot be conveniently maintained until the arm is installed on the engine, and so I have provided the least expensive means in manufacture to accommodate this condition.
  • is carried in its guide 64, which is preferably extended below the lower end of said plunger 6
  • a stop 65 is burred or peened over with a suitable tool by forcing inwardly a slight portion of the lower edge of the guide sleeve 64, as shown. This plugged in stop means 65 afiords adequate clearance between it and the lower outer end of plunger 6! so that in operation there is suflicient room for relative compensating movement between the plunger and this shoulder stop 85 forming the assembly retaining means.
  • the return or compensating spring 63 thrusts the wedge plunger 60 outwardly andconsequently thejwedge plunger 6
  • this invention provides a valve operation mechanism in the form of arockerarm or lifter having positive oil-intake or priming means by which to prime or charge'its high or 1.
  • a rocker arm comprising a hub adapted to.
  • a valve. operating rocker comprising a central bearing hub, a solid arm projecting from the hub, a tubular arm projecting from the hub, an oil passage leading from the hub into one end of the tubular arm, a check valve preventing the flow of oil in the passage out of the tubular arm, a coil spring in the tubular arm having a diameter substantially equal to that of the interior of the latter, a stationary disc having an oil passage seated in the tubular arm over the check valve with limited space between the latter and said disc, a central boss formed on the disc around which the coils of the spring are disposed with one end of said spring bearing on said disc, an oil piston mounted within the tubular arm and urged outwardly by the other end of the spring yieldingly engaging said piston, and a central boss likewise formed on the oil piston and around which fits the last named end of the spring, said bosses and-spring substantially filling the fluid chamber in compressed fluid chamber position.
  • a valve operating rocker comprising a central bearing hub, a solid arm projecting from the hub, a tubular arm projecting fromthe hub, an oil passage leading from the hub into one end of the tubular. arm, a check valve seated over the passage where.
  • a coil spring in the .tubular arm have ing a diameter substantially equal to that-of the interior of the latter, astationary disc having an oil passage seated in the tubular arm over the check valve with limited space between the latter and said disc, a central boss formed on the disc around which the coils of the spring are disposed with one end of said spring bearing on said disc, an oilp-iston mounted within the tubulararm and urged outwardly by the other end of the spring yieldingly engaging said piston, and :a central has likewise formed on the oil piston. and around which fits the last named end of thespring, the spring and two central bosses being so prop'or. timed. and formed. that the coils of the spring collapse one upon the other.
  • a hydraulic rocker arm comprising 'a bear ing hub carrying a cylinder, a self adjusting pis-' ton mounted in the cylinder forming a hydraulic chamber therein, a valve controlled'oil passage leading to the hydraulic chamber, said piston adapted to reciprocate the full length of the hydraulic chamber to one end thereof upon the first operation of the rocker arm to fully close said chamber and effect complete air displacement therefrom, a boss within the cylinder, and a coil spring disposed inside the hydraulic chamber and around the boss and'reacting against the piston'to return the latter to its original position and suck a charge of oil past the valve into said chambenlthe. coils of said spring being rectangular incross section'and' substantially the size of the *cylinderso that when collapsed against each other the boss and spring substantially fill the oil chamber when the piston completes its airdi'splac'ement stroke aforesaid.
  • a hydraulic rocker arm comprising a heating hub carrying a cylinder, a self adjusting piston mounted in the cylinder forming a hydraulic chamber therein, a valve controlled oil passage leading to the hydraulic chamber, said piston adaptedto reciprocate the full length of the hy draulic chamber to one end thereof upon the first operation of the rocker arm to fully close "said chamber and effect complete air'displacement therefrom, a coil spring disposed inside the hydraulic chamber and reacting against the piston to return the latter to its original position and suck a charge of oil past the valve into said chamber,-the coils of said spring being rectangular in cross section and having a diameter substantially that of. the cylinder.
  • a stationary disc disposed over the valve and having a boss around which fits one end of the; rectangular cross section spring, and a boss formed on the piston and around which fits the otherendof the spring.
  • a hydraulic compensating rocker for actuating valves comprising a hub having arms ex tending therefrom, one of the arms being provided with a cylinder opening thru the outer end of the arm and extending toward the hub, an oil passage leading from the hub into the bottom of the cylinder, a check valve in the cylinder adapted to closethe passage, a disc disposed in the bottom of the cylinder over the checkvalve to retain the latter in place for sensitive restricted movement,
  • a piston inserted into the open end of the arm into the cylinderand normally spaced inclose compression chamber at the bottom of the cylinder, a cylindrical boss formed on the piston and on the disc in the compression chamber further reducing the volume of the latter, a coil spring in the compression chamber and substantially the diameter of the cylinder, said spring having its ends fitted over the bosses, said spring coils proportioned and arranged to collapse and engage each other when the spring compresses to its limit, and said bosses stopping one against the other to reduce the air space to a negligible amount when the spring coils are collapsed aforesaid.
  • a rocker arm for actuating valves comprising a hub, a cylinder extending from the hub and open at its outer end, a passage leading from the bottom ,end of the cylinder into the hub, a valve closing the passage, a piston inserted thru the open end of the arm into the cylinder and having its inner end spaced close to the bottom of the cylinder, a compensating spring made of rectangular-cross section coils inserted between the pistonand bottom end of cylinder, and a boss at each end of the spring around which seats the coils thereof, the bosses and the spring coils being proportioned and arranged to simultaneously close against each other at the end of the in-stroke of the piston.
  • a hydraulic self adjusting rocker for actuating valves comprising a hub with arms extending therefrom, one arm forming a cylinder, a piston in the cylinder forming a compression chamber, an oil supply leading to the compression chamber in the arm, and means including a plunger adjustably disposed in a guide transversely to the axis of the piston and engaging the piston to reduce the working load on the compression chamber by transmitting a major portion of the rocker arm operating force thru the walls of said cylinder to the other arm.
  • a hydraulic self adjusting rocker for actuating valves comprising a hub with arms extending therefrom, one arm forming a cylinder, a piston in the cylinder forming a compression chamber, an oil supply leading to the compres sion chamber in the arm, an opening formed thru the wall of the cylinder providing a bearing guide transverse to the axis of said cylinder, 'a plunger carried in said bearing guide and coacting with said piston, and means cooperating with the piston and plunger to amplify the movement of the piston and cause it to adjustably move thru a greater range of travel than takes place in the plunger.
  • a hub having operating arms extending radially therefrom, one arm provided with a cylinder formed therein and an oil passage leading thereto, a piston movably carried in the cylinder and setting off a hydraulic compensating chamber at one end of said cylinder, a spring urging the piston outwardly to draw oil into the chamber, and the outer end of said piston being provided with a surface inclined at an angle with respect to the axis of the piston and adapted to be engaged by a cam actuated member to oscillate the rocker arm.
  • a self adjusting rocker for actuating valves comprising a hub having operating arms extending radially therefrom, one arm provided with a cylinder formed therein and an oil passage leading thereto, a piston movably carried in the cylinder and'setting oif'a hydraulic compensating chamber at one end of said cylinder, a plunger engaging the piston at an angle to the latter, the
  • piston and plunger having sliding contacting surfaces formed at an angle to the axis of the cylinder, and a spring urging outwardly on the piston and plunger to draw oil into the compensating chamber.
  • a self adjusting rocker for actuating valves comprising a hub having operating arms extending radially therefrom, one arm provided with a cylinder formed therein and an oil passage leading thereto, an oil seal piston in the cylinder and forming a compensating chamber between it and the bottom of said cylinder, and a pair of plungers operatively engaging each other at an angle, one of said plungers engaging the oil seal piston, and a spring to urge outwardly on the piston to suck oil into the chamber.
  • a self adjusting rocker for actuating valves comprising a bearing hub and two oppositely projecting' arms, an oil feed passage leading from the hub along one of the arms, this latter arm bored from its outer end to form a cylinder the bottom end of which connects with the passage, a ball check valve in the bottom of the cylinder normally closing the passage against oil flow out of the cylinder, a stationary disc at the bottom of the cylinder holding the ball close to its seat passage, a coil spring in the cylinder having one end seated on the disc and its other end expansibly disposed in the cylinder, an oil seal piston in the cylinder and engaging the spring, an operating plunger in the cylinder and having its front end engaging the piston, a wedging inclined plane formed on the rear end of the plunger, an opening formed in the cylinder toward its outer end and under the wedging inclined plane, and a second plunger slidably confined in the opening and having a wedging surface which engages the first named plunger.
  • a self adjusting rocker for actuating valves comprising a bearing hub and two oppositely projecting arms, an oil feed passage leading from the hub down one of the arms, this latter arm bored from its outer end to form a cylinder the bottom end of which connects with the passage, a ball check valve in the bottom of the cylinder normally closing the passage against oil flow out of the cylinder, a piston disposed in the cylinder closely spaced from the inner end of said cylinder and having a short self adjusting stroke thereby forming a small volume compression chamber, said piston adapted to move to the end of the cylinder upon the first operation of the rocker arm and fully close said small volume compression chamber thereby displacing the air therefrom, a spring to return the piston to its outstroke position and suck in a charge of oil into the chamber, a wedging face formed on the outer end of the piston, and an operating plunger carried by the rocker and also having a wedging face which engages the similar face on the piston.
  • a hydraulic rocker arm for actuating valves comprising a hub having arms extending therefrom, a small volume compensating oil chamber formed in one arm of the rocker and an oil supply line leading to said chamber, a piston plunger working against the small volume body of oil in the chamber, said plunger arranged to undergo a full in-stroke and attain maximum displacement to close the small volume chamber upon the first operation of the rocker arm, a spring to return the plunger to its out-stroke position thereby sucking a full charge of oil into said small volume chamber, and a plunger coacting with the piston plunger and engaging each other on an angle to the axis of each to reduce the" operating load on thesmall body of oili'n the chamber.
  • V I j p 1-7 A hydraulic rocker arm for actuating valves
  • a hydraulic selfadjusting'rocker' arm comprising a hub with arms, a cylinder formed in one arm and an oil 'passageleading thereto, a pistonin: the cylinder'which sets offacompression chamber therein, said piston having a wedge face'on: itsouter end, a plunger disposedl at right angles to. the;pistoni.and also: having a .wedge face engaging the wedge face of said piston, said wedgev faces being formed on a plane at substantiallyaforty-five degree angle in relation to the axis of the piston or plunger whereby the. adjust ingtravel is the same for both the piston and the'pl'uiiger thereby imposing high pressure on the compression chamber, and spring means to urge outwardly on the piston and plunger.
  • Valve operating mechanism comprising a hydraulic device employing mechanical means in aid of self adjusting action, comprising an operating member adapted to be interposed between a cam and an engine valve, a hydraulic oil chamber in the operating member, wedge-like plunger means cooperating with each other and working against the oil in the chamber; said wedge-like plunger means including coacting parts slidably thrusting against each other on substantially a forty-five degree angle in relation to the direction of the adjusting movement thereof, whereby substantially the full load of the cam and engine valve is carried on the oil in the chamber.
  • a hydraulic rocker arm comprising a central hub having arms extending therefrom, one arm being provided with a cylinder, a piston in the cylinder, an oil supply passage leading into the cylinder in front of the piston, a plunger engaging the piston with an inclined operating face made on an angle to the piston axis, the plunger having a push rod operating connection by which a cam and push rod are adapted to oscillate the rocker arm by a tilting force applied to said plunger, an oil groove made in the inclined operating face and adapted to receive oil which leaks by the piston, and an oil hole extending longitudinally thru the plunger and receiving oil from the groove and leading said oil to the push rod operating connection.
  • a hydraulic rocker arm comprising a central hub having arms extending therefrom, one arm being provided with a cylinder, a piston in the cylinder, an oil supply passage leading into the cylinder in front of the piston, a check valve permitting oil to enter the cylinder and preventing oil from passing out therefrom, a plunger engaging the piston with an inclined operating face made on an angle to the piston axis, a spring expanding against the piston to urge it and the plunger outwardly from the rocker arm, and means engaging the inclined operating face to retain the piston and plunger in the rocker arm against the force of the spring.
  • a hydraulic rocker arm comprising a central hub having arms extending therefrom, one arm being provied with a cylinder, a piston in the cylinder, an oil supply passage leading into the cylinder in front of the piston, a plunger engaging the piston with an inclined operating face made on an angle to the piston axis, a spring expanding against the piston to urge it and the plunger outwardly from the rocker arm, and stop means engaging the plunger to limit its outer stroke to retain it and the piston in the rocker arm.
  • a rocker arm including a cylinder formed in one of its arms, a hydraulic compensating unit carried:i'n the cylinder and having a compression spring to actuate the unit, an opening formed thru the [wall of the cylinder and forming a'"sleeve made onct'he rocker arm, a plunger mounted in the sleeve and extending thru the opening into the cylinder and engaging the compensating unit with the outer end of saidplunger disposed with-j insaid s'levegarid stop means on the outer end of the sleeve against whichthe plunger is held infposition and preventedifrom dropping' o'ut of therocker arm dueto'the'forc'e of the spring.
  • a fro'cker arm including a cylinder formed in one oflfit sarms, a hydraulic compensating unit carried the cylinder and having I a compression spring tda'otuate the'unit," an opening formed thru the wall of the cylinder and forming a sleeve made on the rocker arm, a plunger mounted in the sleeve and extending thru the opening into the cylinder and engaging the compensating un1t with the outer end of said plunger disposed within said sleeve, and a stop made on the sleeve by deforming its outer extremity inwardly in line with the plunger to keep it in position against the force of the spring.
  • a rocker adapted to be actuated by an engine driven cam to operate a valve comprising a member having an opening, a compression chamber in the opening of the rocker and an oil supply connected therewith, plunger-wedge means carried in the opening and operating against the oil body in the chamber, and a spring acting on the plunger-wedge means to adjust same in one direction, said plunger-wedge means being adapted for operating connection with the cam.
  • a rocker for operating valves comprising a central hub adapted to oscillate on a rock shaft under the force of a cam, a pair of arms extending therefrom, a hydraulic self adjusting unit carried within one of the arms and including a hydraulic compression chamber in said arm, an oil supply leading to the hydraulic compression chamber, and coacting straight smooth-faced wedges having relative sliding motion against each other included in the self adjusting unit and operatively mounted within said arm and cooperating with the hydraulic compression chamber to reduce the operating cam and Valve load and pressure on said chamber.
  • a hydraulic rocker arm adapted to be actuated by an engine driven cam to operate a valve, comprising a member having an opening, a hydraulic compression chamber in the opening of the rocker arm and an oil supply connected therewith, plunger-wedge means carried in the opening and operating against the oil body in the chamber, and a spring acting on the plunger- Wedge means to adjust same in one direction, said plunger-Wedge means including one wedge member which is slidably carried within and which projects through the rocker arm and is adapted to be directly engaged by a cam-actuated push rod.
  • a self-adjusting hydraulic rocker arm for actuating engine valves comprising, in combination, a hub adapted to rock upon a hollow shaft which transmits oil to said hub, actuating arms extending from the hub, a bore in one arm forming a cylinder therein, an oil passage formed through the hub leading to the cylinder, a free check ball valve in the passage to admit oil into the cylinder and seated by pressure of said oil, a retainer over the free check ball valve to hold it in place and limit its movement; plunger means in the cylinder serving, when in normal operative self-adjusting position, to occupy or fill the space in said cylinder excepting a substantially small cylindrical portion thereof, which small cylindrical portion forms a hydraulic-pressure chamber of minimum size having a restricted volume set ofl to hold a minimum amount of oil trapped between the check-valve retainer and the plunger means; the inward movement of said plunger means, toward the check-valve retainer, serving to completely close the minimum-size hydraulicpressure chamber by reason of the plunger means stopping against said check-valve

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US679633A 1933-07-10 1933-07-10 Valve operating mechanism Expired - Lifetime US2053743A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
BE398430D BE398430A (de) 1933-07-10
US679633A US2053743A (en) 1933-07-10 1933-07-10 Valve operating mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US679633A US2053743A (en) 1933-07-10 1933-07-10 Valve operating mechanism

Publications (1)

Publication Number Publication Date
US2053743A true US2053743A (en) 1936-09-08

Family

ID=24727699

Family Applications (1)

Application Number Title Priority Date Filing Date
US679633A Expired - Lifetime US2053743A (en) 1933-07-10 1933-07-10 Valve operating mechanism

Country Status (2)

Country Link
US (1) US2053743A (de)
BE (1) BE398430A (de)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2818845A (en) * 1955-10-17 1958-01-07 Carl F Yandt Hydraulic self-adjusting rocker arm
US2818843A (en) * 1955-09-15 1958-01-07 Gen Motors Corp Push rod
US2970583A (en) * 1959-07-27 1961-02-07 Ford Motor Co Valve gear
US3189011A (en) * 1964-04-30 1965-06-15 Stephen F Briggs Valve actuating mechanism with mechanical means for self-adjustment
US3401677A (en) * 1967-08-29 1968-09-17 Ford Motor Co Integral lash adjuster
US4187810A (en) * 1978-02-17 1980-02-12 Buehner Joseph F Poppet valve stroke adjusting device for, and combination with, an internal combustion valve in head engine
US4392461A (en) * 1980-11-10 1983-07-12 Richard Rotondo Rocker arm adapter for altering cam profile of exhaust valve
US4491098A (en) * 1980-11-10 1985-01-01 Rotondo Richard D Device for altering cam profile
US4497307A (en) * 1984-02-03 1985-02-05 General Motors Corporation Integral rocker arm hydraulic lifter and bearing assembly
US5095862A (en) * 1991-04-22 1992-03-17 Ram Pushrods, Inc. Removable adjustable pushrod
DE4339433A1 (de) * 1993-11-18 1995-05-24 Bayerische Motoren Werke Ag Ventilhebel zur Steuerung eines Gaswechselventils einer Brennkraftmaschine, insbesondere Schlepphebel
US5584268A (en) * 1994-12-27 1996-12-17 Ford Motor Company Low inertia rocker arm with lash adjuster and engine valve
US6230676B1 (en) * 1999-04-23 2001-05-15 Toledo Technologies Inc. Interchangeable rocker arm assembly
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
US20080110424A1 (en) * 2006-09-11 2008-05-15 Hyundai Motor Company Variable valve lift apparatus
US20150240670A1 (en) * 2014-02-27 2015-08-27 Schaeffler Technologies AG & Co. KG Switching roller finger follower with rapid transition from locked to unlocked mode and method thereof

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2818843A (en) * 1955-09-15 1958-01-07 Gen Motors Corp Push rod
US2818845A (en) * 1955-10-17 1958-01-07 Carl F Yandt Hydraulic self-adjusting rocker arm
US2970583A (en) * 1959-07-27 1961-02-07 Ford Motor Co Valve gear
US3189011A (en) * 1964-04-30 1965-06-15 Stephen F Briggs Valve actuating mechanism with mechanical means for self-adjustment
US3401677A (en) * 1967-08-29 1968-09-17 Ford Motor Co Integral lash adjuster
US4187810A (en) * 1978-02-17 1980-02-12 Buehner Joseph F Poppet valve stroke adjusting device for, and combination with, an internal combustion valve in head engine
US4392461A (en) * 1980-11-10 1983-07-12 Richard Rotondo Rocker arm adapter for altering cam profile of exhaust valve
US4491098A (en) * 1980-11-10 1985-01-01 Rotondo Richard D Device for altering cam profile
US4497307A (en) * 1984-02-03 1985-02-05 General Motors Corporation Integral rocker arm hydraulic lifter and bearing assembly
US5095862A (en) * 1991-04-22 1992-03-17 Ram Pushrods, Inc. Removable adjustable pushrod
WO1992019845A1 (en) * 1991-04-22 1992-11-12 Ram Pushrods, Inc. Removable adjustable pushrod
DE4339433A1 (de) * 1993-11-18 1995-05-24 Bayerische Motoren Werke Ag Ventilhebel zur Steuerung eines Gaswechselventils einer Brennkraftmaschine, insbesondere Schlepphebel
US5584268A (en) * 1994-12-27 1996-12-17 Ford Motor Company Low inertia rocker arm with lash adjuster and engine valve
US6230676B1 (en) * 1999-04-23 2001-05-15 Toledo Technologies Inc. Interchangeable rocker arm assembly
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
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
US20080110424A1 (en) * 2006-09-11 2008-05-15 Hyundai Motor Company Variable valve lift apparatus
US7421993B2 (en) * 2006-09-11 2008-09-09 Hyundai Motor Company Variable valve lift apparatus
CN101144400B (zh) * 2006-09-11 2012-08-08 现代自动车株式会社 可变的阀升程装置
US20150240670A1 (en) * 2014-02-27 2015-08-27 Schaeffler Technologies AG & Co. KG Switching roller finger follower with rapid transition from locked to unlocked mode and method thereof
US9708938B2 (en) * 2014-02-27 2017-07-18 Schaeffler Technologies AG & Co. KG Switching roller finger follower with rapid transition from locked to unlocked mode and method thereof

Also Published As

Publication number Publication date
BE398430A (de)

Similar Documents

Publication Publication Date Title
US2053743A (en) Valve operating mechanism
US5460131A (en) Compact combined lash adjuster and reset mechanism for compression release engine brakes
US2098115A (en) Hydraulic valve lifter
US2109809A (en) Internal combustion engine
US4191142A (en) Self-contained hydraulic lash adjuster
US3405697A (en) Hollow valve construction for variable compression ratio piston
JPH06207539A (ja) 圧縮解放形エンジンリターダにおけるクリップ弁
US2938508A (en) Horizontally operable hydraulic valve lifter
US5186141A (en) Engine brake timing control mechanism
US4079707A (en) Variable compression ratio piston
US2956557A (en) Hydraulic tappets
US3161112A (en) Speed compensated variable compression ratio piston and valve
US4840160A (en) Valve control device
US2542036A (en) Self-adjusting tappet
US4399793A (en) Fuel injector
US3716036A (en) Valve actuating assembly
US3418983A (en) Automatically hydraulically adjusting play-equalization element for the valve control in piston engines
US2158730A (en) Valve operating mechanism
US4457270A (en) Hydraulic lifter
GB2251456A (en) I.c. engine with variable compression ratio
US2019444A (en) Valve compensator
US2255359A (en) Compressor
US1931833A (en) Compressor
USRE21802E (en) Valve operating mechanism
US3144010A (en) Push rod with ball check valve