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Publication numberUS3304925 A
Publication typeGrant
Publication dateFeb 21, 1967
Filing dateJun 20, 1966
Priority dateJun 20, 1966
Publication numberUS 3304925 A, US 3304925A, US-A-3304925, US3304925 A, US3304925A
InventorsRhoads James E
Original AssigneeRhoads James E
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydraulic valve lifter
US 3304925 A
Images(2)
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Description  (OCR text may contain errors)

Feb. 21, 1967 J. E. RHOADS 3,304,925

HYDRAULIC VALVE LIFTER Filed June 20, 1966 2 Sheets-Sheet l I N VEN TOR. JAME S Ev RHOADS 1967 J. E. RHOADS HYDRAULIC VALVE LIFTER 2 Sheets-Sheet 2 Filed June 20, 1966 INVENTOR.

JAMES E RHOADS 143m & 141- 36 Fig.7

United States Patent Qfifice 3,304,925 HYDRAULIC VALVE LIFTER James E. Rhoads, 8888 Lemon Ave., La Mesa, Calif. 92041 Filed June 20, 1966, Ser. No. 558,907 7 Claims. (Cl. 123-90) With conventional types of hydraulic valve lifters, each valve actuating push rod seats in a plunger axially slidable in a lifter body, and the lifter body rides on one lobe of the cam. Oil from the engine lubrication system is .introduced under pressure between the body and plunger to.

expand the valve lifter assembly axially and tighten the linkage in the valve actuating train. The oil pressure,

governed by the engine driven oil pump, increases with engine speed, so that at high speed the valve lifters are pumped up and become effectively solid. At low speed the pressure is not so high, so the plunger rides lower in the valve lifter body and the valves are not opened as far or as soon. Many .lifters are designed to trap oil in the body chamber and pump up to an effectively solid condition at relatively low speed. Some typesof hydraulic lifters have been designed with .intentional leakage to avoid premature pumping up. However, with high performance cams the valves are timed to have considerable overlap in order to provide for a large flow through the engine. At low speeds this large overlap is not necessary and the engine runs inefiiciently, resulting in a loss in low speed horsepower. Basically, increasing the valve lash will shorten valve open duration and reduce overlap, since more crankshaft rotation is necessary to overcome the lash in the valve train. This will result in an improvement in low speed performance. However, excessive lash causes considerable noise and wear at idling and low speeds. Decreasing lash, as by tightening or pumping up the lifters, will lengthen valve duration and improve high speed performance.

The valve lifter described herein is designed to provide favorable characteristics over the entire speed range. At low speed the lifter pumps up rapidly to a predetermined position, set to suit the specific engine and cam, after which a closely controlled oil leak is permitted to prevent pumping up to a fully solid condition at intermediate speeds. In the intermediate speed range the degree of pumping in the lifter is dependent on oil system pressure governed by the oil pump, which is related to, engine speed, so the lifter operates generally in proportion to engine speed. At high speeds the motion is so rapid that the oil can no longer escape to any degree through the restricted leak path and the lifter becomes effectively solid.

The valve lifter and its action are illustrated in the drawings, in which:

FIGURE 1 is a sectional view, taken axially along a valve lifter, showing the mechanism in the valve closed position;

FIGURE 2 is a similar sectional view with the mechanism in the valve open position;

FIGURE 3 is a sectional view taken on line 33 of FIGURE 2;

Patented Feb. 21 1967 FIGURE 4 is a perspective view of the plunger;

FIGURE 5 is a sectional view similar to FIGURE 1, but with a modified form of lifter;

FIGURE 6 is a sectional view similar to FIGURE 2, with the modified lifter;

FIGURE 7 is a sectional view taken on FIGURE 6; and

FIGURE 8 is a perspective view of the modified plunger.

Similar characters of reference indicate similar or identical elements and portions throughout the specification and throughout the views of the drawing.

The preferred form of the valve lifter, illustrated in FIGURES 1-4, shows the valve lifter 10 axially slidably mounted in a bore 12 in a portion of the engine head casting 16. A single valve lifter is shown, there being one lifter for each valve in the engine, with each lifter operated by a lobe 18 on a camshaft 20. In the head 16 is an oil gallery 22 with a supply duct 24 leading to bore 12 to supply oil to the lifter from the pressure side of the engine oil system.

Valve lifter 10 comprises a cylindrical body 26 having a closed lower end 28, and axially slidable within the body is a hollow cylindrical plunger 30. In the upper end of plunger 30 is a cup 32 in which is seated the end of a push rod 34, the push rod being coupled to a conventional rocker arm and valve, not shown. Plunger 30 is retained by a snap ring 36 in a groove38 within the upper end of body 26. Body 26 has an external peripheral collecting channel 40 which registers with the supply duct 24 when the lifter is moved to the raised position by cam lobe 18, as in FIGURE 2. A port 42 communicates from channel 40 to the interior of body 26 and plunger 30 has a peripheral channel 44 which registers with port 42 at all times. terior of plunger 30, so that oil is admitted into the inner chamber 48 of the plunger.

At the lower end of plunger 30 is a small outlet 50, the lower end of which is closed by a ball check valve 52 held in place by a seating spring 54, the spring and valve being held in place by a perforated retaining cage 56. The space between plunger 30'and the lower end of body 26 comprises a pressure chamber 58 and in this chamber is a return spring 60 which biases the plunger upwardly out of the body, until stopped by the snap ring 36. In normal assembly the plunger 30 is pressed down against return spring 60 by the push rod 34, which is loaded by the much stronger valve spring, not shown.

The structure thus far described is conventional and representative of hydraulic valve lifters, which may vary somewhat in porting and check valve arrangements. In operation the plunger chamber 48 receives oil under pressure at each upward stroke of the lifter, the oil being forced down through check valve 52 into pressure chamber 58. At low pressure the plunger rides low in the body and is raised by increasing pressure to tighten the valve train. With no return leakage, or only that which may occur through the normal sliding clearance of plunger 30 in the body 26, the oil in chamber 58 is pumped up rapidly and the lifter becomes effectively solid.

The novel action is provided by a bleed duct 62 formed by a flat portion 64 ground along the outer surface of plunger 30 from the lower end upwardly. In FIGURE 3 the flattening is exaggerated to simplify illustration, the

line 7-7 of From channel 44 a port 46 leads to the in-' 3 actual proportions being closer to that shown in FIG- URE 4. Body 26 has an internal return channel 66 extending axially to port 42 and flat portion 64 extends along the plunger to a point just short of said return channel when the oil pressure in chamber 58 is at minimum, as in FIGURE 1.

As the pressure in chamber 58 increases, with the engine running, the lifter will pump up and plunger 30 will rise until bleed duct 62 communicates from chamber 58 to the return channel 66. Oil can now leak from the pressure chamber back to the source and delay further pumping action. The depth and length of the bleed duct 62 are critical to proper engine operation. If the bleed duct is too large oil will leak too fast and the lifterwill not pump up in accordance with engine speed. If the bleed duct is too small the oil will not be able to escape sufficiently and excessive pumping up will occur. The size of the bleed duct 62 must be such that oil will leak sufficiently to prevent rapid pumping up but not so much that the plunger will not rise beyond a certain point. At high speeds it is necessary that the bleed duct is not large enough to pass oil at a flow rate sufiicient to relieve pressure in chamber 58. In other words, at high speeds the motion is so rapid in the lifter action that oil does not have time to escape through the bleed duct and the lifter becomes effectively solid.

It has been found in tests that a flat portion 64 ground off to provide a bleed duct having a depth on the order of from two to five thousandths of an inch will provide the required characteristics in the engine of a passenger automobile. The exact amount will depend on the normal oil pressure in the engine, the cam design with regard to valve timing and duration and to the overall performance range of the engine. In racing engines it would be possible to enlarge the bleed duct to as much as ten or fifteen thousandths of an inch. An oil bleed of this magnitude would result in considerable valve lash and noise at idle speeds, but this can be tolerated in a racing engine.

The length of the fiat portion 64 governs low speed lash and determines the point at which the rapid initial pumping up becomes more proportional to engine speed. If the fiat portion is short the plunger must be pumped higher in the lifter body before leakage can occur and low speed performance will not be improved over that available with a non-leaking lifter. But if the fiat portion 64 is too long only a slight pumping up will take place before leakage begins and undue valve lash may occur in the low to medium speed range. Again, the precise length depends on the cam, the engine performance and the speed at which it is determined to begin pressure bleed to obtain the most desirable overall characteristics. Actual dimensions cannot be given since the position of the return channel 66 must also be take into account.

A modified form of valve lifter is illustrated in FIGURES 5-8, in which all the conventional structure is identical to that described above and is correspondingly numbered. The only differences are in the bleed duct and oil return arrangement.

In the plunger instead of a fiat portion, oil bleed is provided by circumferentially spaced, axially extending bleed grooves 68, three being shown as an example. The bleed grooves 68 extend from the lower edge of plunger 30 to a circumferential ring groove 70, the axial position of which determines the upper end limit of the bleed grooves. Body 26, instead of an inner channel, has a single return port 72 from the interior thereof to the collecting channel to return bleed oil to the source.

Before pump up the ring groove 70 is below return port 72 and no leakage occurs. When the plunger is pumped up to a predetermined position the ring groove 70 registers with return port 72 and leakage occurs. Beyond a certain speed the oil can no longer escape at a sufficient rate and the lifter becomes effectively solid, the overall action being as described above. The total cross sectional area of the bleed grooves 68 will, of

course, be in the same proportion as that provided by the fiat portion 64 and ring groove 70 will be of appropriate size to carry the combined flow from the bleed grooves, but the size is not especially critical since flow is governed by the size of the return port 72. To facilitate precise control of the flow the return port 72 is contained in a screw-in plug 74 which seats firmly in the wall of body 26', the element being similar to a replaceable jet as used in a carburetor. By using plugs with return ports of different sizes the lifters can be set up for specific engines and performance ranges.

In each form of the lifter, oil from the pressure chamber 58 escapes or bleeds through a restricted channel, formed in one instance by a flat portion on the plunger and in the other instance by grooves. At a particular position of the plunger in the lifter body the oil can escape to the source through a return opening, which in one instance is a combination of channel 66 and port 42 and in the other instance a port 72. In each form the return opening leads to the conventional collecting channel 40.

The arrangement is adaptable to a variety of engines and can be incorporated into many existing types of valve lifters, without requiring any changes in the engines. In fact existing lifters already in use can be modified in accordance with this disclosure.

It is understood that minor variation from the form of the invention disclosed herein may be made without departure from'the spirit and scope of the invention, and that the specification and drawings are to be considered as merely illustrative rather than limiting.

I claim:

1. In a hydraulic valve lifter having a hollow cylindrical body with a closed lower end for engagement with a cam; a hollow cylindrical plunger axially slidable in said body and enclosing a pressure chamber in the lower end of the body; an external collecting channel on said body to receive oil from a pressurized source; a port opening into said body from said channel; a port in said plunger communicating with said first mentioned port to admit oil into the plunger; and a one-way valve in said plunger opening into said pressure chamber;

the improvement comprising:

at least one restricted oil bleed channel extending from said pressure chamber along the outside of said plunger;

an oil return opening from the interior of said body to said collecting channel;

said bleed channel terminating short of said return opening when pressure in said pressure chamber is low and moving into registration therewith when said plunger is raised to a predetermined level by pressure in the pressure chamber;

the cross sectional area of said bleed channel being insufiicient to sustain oil bleed beyond a predetermined flow rate at high engine speed.

2. The structure according to claim 1, wherein said bleed channel comprises a flat portion on the outer surface of said plunger.

3. The structure according to claim 1, wherein said return opening includes an internal channel in said body communicating with said first mentioned port.

4. The structure according to claim 1, wherein said bleed channel comprises a flat portion on the outer surface of said plunger, and said return opening includes an internal channel in said body communicating with said first mentioned port.

5. The structure according to claim 1, wherein said bleed channel comprises a plurality of grooves extending from said pressure chamber along the outer surface of said plunger.

6. The structure according to claim 1, wherein said bleed channel comprises a plurality of grooves extending from said pressure chamber along the outer surface of 5 said plunger, and a circumferential ring groove interconnecting said grooves;

and said return channel comprises a restricted port opening from the interior of said body to said collecting channel. 7. The structure according to claim 6, wherein said restricted port is contained in a replaceable plug element removably inserted in said body.

References Cited by the Examiner UNITED STATES PATENTS 1,965,517 7/1934 Vitalini 123-90 6 2,484,109 10/1949 Meinecke "123-90 2,614,547 10/1952 Meinecke 123 90 2,931,347 4/1960 Williams 123 90 3,142,290 7/1964 Lesher 123 90 5 FOREIGN PATENTS 768,336 I 2/1957 Great Britain.

MARK NEWMAN, Primary Examiner.

' 10 A. L. SMITH, Assistant Examiner.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US1965517 *Jul 30, 1932Jul 3, 1934Vitalinl Walter RHydraulic valve tappet
US2484109 *Mar 2, 1945Oct 11, 1949Meinecke Helmuth AValve mechanism
US2614547 *Jul 22, 1946Oct 21, 1952Meinecke Helmuth AHydraulic valve tappet operable to vary valve-lift and valve-timing
US2931347 *Apr 10, 1958Apr 5, 1960Williams Ned LVariable valve lifter for internal combustion engines
US3142290 *Jul 13, 1962Jul 28, 1964 Hydraulic lash adjuster
GB768336A * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3650251 *May 11, 1970Mar 21, 1972Mack TrucksHydraulic valve lifter
US3786792 *May 28, 1971Jan 22, 1974Mack TrucksVariable valve timing system
US3859973 *Sep 13, 1973Jan 14, 1975Allis ChalmersTiming device for fuel injector
US3875911 *Aug 6, 1973Apr 8, 1975Joseph CharlesHydraulic tappet
US3921609 *Aug 16, 1974Nov 25, 1975Rhoads Jack LVariable duration hydraulic valve tappet
US3967602 *Sep 23, 1974Jul 6, 1976Brown William GHydraulic valve lifter for reciprocating internal combustion engines
US4020806 *Dec 29, 1975May 3, 1977Nissan Motor Co., Ltd.Hydraulic valve lifter for internal combustion engine
US4248104 *Aug 1, 1977Feb 3, 1981Xomox CorporationMethod of and means for providing a cam-actuated, spring-return mechanism wherein the torque output is a function of the cam profile
US4398510 *Mar 27, 1981Aug 16, 1983The Jacobs Manufacturing CompanyTiming mechanism for engine brake
US4524731 *Aug 15, 1983Jun 25, 1985Rhoads Jack LHydraulic valve lifter with continuous void
US4930463 *Aug 28, 1989Jun 5, 1990Hare Sr Nicholas SElectro-rheological valve control mechanism
US5014829 *Aug 31, 1990May 14, 1991Hare Sr Nicholas SElectro-rheological shock absorber
US5103779 *Dec 10, 1990Apr 14, 1992Hare Sr Nicholas SElectro-rheological valve control mechanism
US5119774 *Nov 8, 1990Jun 9, 1992General Motors CorporationDirect acting hydraulic valve lifter
US5158109 *Mar 11, 1991Oct 27, 1992Hare Sr Nicholas SElectro-rheological valve
US5245958 *Jun 8, 1992Sep 21, 1993General Motors CorporationDirect acting hydraulic valve lifter
US5623898 *Jan 16, 1996Apr 29, 1997Bruton; Murl L.Variable duration hydraulic valve lifters
US6318324Dec 7, 1998Nov 20, 2001Daimlerchrysler CorporationSealed hydraulic lifter for extreme angle operation
US7921823Oct 23, 2006Apr 12, 2011Schaeffler KgHydraulic play compensation device
EP0017413A1 *Mar 24, 1980Oct 15, 1980Eaton CorporationFuel injection system and timing advance device therefor
EP0608925A1 *Jan 13, 1994Aug 3, 1994General Motors CorporationCompact valve-lifters
WO1992014039A1 *Jan 16, 1992Aug 20, 1992Schaeffler Waelzlager KgHydraulic clearance compensator for use in internal combustion engines
WO2005113942A1 *Apr 23, 2005Dec 1, 2005Ina Schaeffler KgHydraulic play compensation device
Classifications
U.S. Classification123/90.55, 74/569, 123/90.16
International ClassificationF01L1/20, F01L1/245
Cooperative ClassificationF01L1/245
European ClassificationF01L1/245