Compact valve lifters

Compact valve lifters are disclosed for overhead camshaft engines with direct acting valve gear and for engines with indirect acting valve actuation such as push rod actuated overhead valves. Two step variable lift and non-variable lift valve lifters are included as are roller and non-roller follower types with various features in common.

TECHNICAL FIELD 
This invention relates to valve lifters for internal combustion engines and 
the like. In particular, the invention relates to cam actuated variable 
and non-variable lift, roller and non-roller type compact lifters of both 
direct and non-direct acting types for overhead, in-head and in-block 
camshaft engines. 
BACKGROUND 
PCT international patent application publication WO91/12413 (Lotus) 
published 22 Aug. 1991 discloses valve lift control devices of various 
forms which provide variable valve lift. In one embodiment, a lifter has a 
cylindrical high lift outer cam follower that engages a pair of spaced 
cams for high lift valve actuation and a low lift inner cam follower that 
engages a central low lift cam directly or through an intermediate 
follower member for low lift valve actuation. 
The inner follower is reciprocable in a bore of the outer follower and 
directly actuates the valve through a hydraulic lash adjuster. The outer 
follower is reciprocable in a bore of an associated engine component and 
is selectively connectable to the inner follower by locking means. These, 
when engaged, cause the inner follower to move with the outer follower, 
thereby actuating the valve in a high lift motion determined by the 
profiles of the high lift cams. 
SUMMARY OF THE INVENTION 
The present invention involves novel combinations of elements based in part 
on the teachings of publication WO91/12413 but having various 
modifications and improvements which provide various additional features 
and advantages. 
In a first embodiment, the invention provides an indirect acting two step 
variable hydraulic valve lifter for push rod or rocker actuation. 
Additional features include conventional lash adjuster arrangement for cam 
in block valve mechanism, modified locking and rotational alignment of 
followers and rotation enhancing means. 
In a second embodiment, the invention also provides rollers for inner and 
outer cam followers similar to the first embodiment. 
In a third embodiment, the invention provides a direct acting two step 
variable hydraulic valve lifter having roller followers for the high lift 
cams while retaining a compact configuration for the valve lifter 
assembly. 
In a fourth embodiment, the invention provides a direct acting one step 
non-variable hydraulic valve lifter having roller followers integrated in 
a compact configuration based upon the third embodiment. 
These and other features and advantages of the invention will be more fully 
understood from the following description of certain specific embodiments 
of the invention taken together with the accompanying drawings.

DETAILED DESCRIPTION 
First Embodiment--VHVL 
Referring now to FIGS. 1-3 of the drawings in detail, numeral 10 generally 
indicates an overhead valve cam in block reciprocating piston engine 
having push rod/rocker arm type valve gear and showing one embodiment of 
the invention. The engine includes a cylinder block 11 having at least one 
cylinder 12 closed by a cylinder head 14. The cylinder head carries at 
least one inlet valve 15 and one exhaust valve, not shown, controlling 
ports connecting with the cylinder. Each valve is biased closed by a 
spring 16 and is opened by valve gear or mechanism such as a rocker arm 18 
actuated by a push rod 19, a valve lifter 20 and an associated camshaft 
22. 
The exhaust valves may be actuated by conventional devices or by lifters in 
accordance with the present invention, but in the illustrated example, the 
lifter for each inlet valve 15 is a two step variable hydraulic valve 
lifter (VHVL) 20 selectively actuated by a pair of spaced high lift cams 
23 and a central low lift cam 24 located on the camshaft 22 between the 
high lift cams 23. The lifter 20 includes a high lift outer cam follower 
26 actuated by the high lift cams 23 and a low lift inner cam follower 27 
actuated by the low lift cam 24. 
The outer follower 26 has a cylindrical annular body 28 that is 
reciprocable in a lifter bore 30 of the engine block. A first annular end 
31 of the body engages the high lift cams while an opposite second annular 
end 32 includes a recess 34 in which a return spring 35 is seated. The 
first end 31 is preferably made as a separate plug that closes the open 
end of an annular hollow portion 36 of the body 28. This minimizes the 
mass and allows the body to be made of a different hardness or material 
than the end plug 31 which engages the cams. The body 28 also has a 
cylindrical outer surface 38 received in the lifter bore 30 and a 
concentric cylindrical inner surface 39. The spring 35 preferably seats 
upwardly against a rotator bearing 40 which is mounted in the engine block 
11 and facilitates rotation of the lifter 20, which is desirable for low 
wear. 
The low lift inner follower 27 is formed much like a conventional valve 
lifter although of smaller diameter than those now in common use. It 
includes a hollow piston 42 with a closed end 43, an open end 44 and a 
cylindrical wall 46 reciprocably engaging the cylindrical inner surface 39 
of the body 28. The closed end 43 selectively engages the central low lift 
cam 24 of the camshaft. Follower 27 further includes hydraulic lash 
adjusting elements including a plunger 47, check ball 48, ball cage 50, 
ball spring 51 and plunger spring 52. A push rod seat 54 mounts against 
the plunger 47 in a counterbore in the open end 44 of the piston 27. 
Lubricating oil flow to the push rod and rocker arm through an orifice 55 
in the seat 54 is controlled by a metering disk 56 retained by a retainer 
58 in known manner. These features are found in many production valve 
lifters. 
An annular oil groove 59 around the body 28 connects with a pressure oil 
gallery 60 in the engine block. Connecting oil passages 62, 63 in the body 
28 and piston wall 46, respectively, feed oil from the groove 59 through 
slots in the plunger 47 to the lash adjuster and to the hollow push rod 19 
for lubricating the rocker arm 18. Radial openings 64 in the body receive 
headed lock pins 66 biased outward by springs 67. Retaining pins 68 hold 
the lock pins in the body. Flats 70 or other suitable recesses are 
provided on the piston for engagement by the lock pins when forced inward. 
To prevent relative rotation of the body 28 and piston 42 and maintain the 
lock pins 66 and flats 70 in alignment, alignment means are provided such 
as a guide pin 71 fixed in the body 28 and engaging a guide groove 72 in 
the piston 42. 
In operation, pressure control means, not shown, are provided to 
selectively control the oil pressure in the oil gallery 60 to vary the 
valve lift between low and high lift functions and provide adequate oil 
pressure for hydraulic lash adjuster operation. With low pressure, the 
lock pins 66 are retracted and the inner and outer cam followers 27, 26 
are disengaged. Thus, the inner follower, 27 engages and is controlled by 
the central cam 24 to move the valve in a low lift motion and the outer 
follower 26 idles by moving with the high lift cams 23 but without any 
connection with or effect upon the valve motion. 
Increasing the oil pressure by the control means causes the lock pins to 
move inward and, when the cam followers are on the cam base circles, 
engage the flats 70 to lock the inner and outer followers together as 
shown in the drawings. The inner follower 27 thus moves with the outer 
follower 26 along the high lift curve established by the high lift cams 23 
and the valve 15 is moved in a corresponding high lift motion. 
Second Embodiment--RVHVL 
FIG. 4 illustrates another embodiment of engine with push rod type valve 
gear in which each intake valve is actuated by an indirect acting roller 
variable hydraulic valve lifter (RVHVL) 74 according to the invention. As 
shown, in the illustrated embodiment, the lubricating, lash adjusting, 
locking and alignment features of lifter 74 are the same as or similar to 
those of the first described valve lifter 20 so their description will not 
be repeated and, where needed, like numerals indicate like parts. 
The outer cam follower 75 and inner cam follower 76 differ from the first 
embodiment in the provision of cam engaging follower rollers. The annular 
body 78 of the outer cam follower 75 is extended to carry in slots or 
recesses 79 a pair of spaced rollers 80 engaging spaced high lift cams 82 
of the camshaft 83. The rollers 80 may ride on bearings, such as needles, 
not shown, which are carried on axle pins 84 received in transverse bores 
85 in the body 78. Similarly, the hollow piston 86 of the inner cam 
follower 76 is extended to carry in a recess 87 a single follower roller 
88 engageable with the central low lift cam 89 and rotatably carried on 
bearings, such as needles not shown, which ride on an axle pin 90. The pin 
90 is received in a transverse bore 91 in the piston extended portion. The 
pin 90 may be press fitted, staked or otherwise held fixed in the bore 91 
in spaced relation with the pins 84. If desired, the rollers could be 
journaled directly on bronze pins or have other suitable bearings instead 
of the needle bearings referred to. 
In operation, because of the use of roller followers 75, 76 suitable 
alignment means are needed to prevent rotation about their reciprocation 
axis 94. Obviously, the rotator bearing 40 of the first embodiment is no 
longer needed. For the outer follower 75, the outer ends 95 of the axle 
pins 84 may extend beyond the body 78 into mating grooves 96 provided in 
the associated bore 98 of the engine block 99. Then means, as shown, such 
as pin 71 and groove 72 similar to the first embodiment may be used to 
prevent relative rotation of the inner and outer cam followers 75, 76. 
Thus, the rollers 80, 88 are maintained square with the axis of the 
camshaft 83 and ride properly on their respective cams 82, 89. In other 
respects, the FIG. 4 embodiment operates in the same manner as that first 
described. However, instead of the extended axle pins 84, alternative 
alignment means, such as those of FIGS. 10 and 11 might equally well be 
used. 
FIGS. 4a and 4b illustrate some variations of the second embodiment in the 
manner of aligning the inner and outer cam followers. In FIG. 4a, the axle 
pins 84a have reduced diameter inner ends that extend beyond the inner 
surface 39 of the body 78 into grooves 72a formed in the modified piston 
86a to maintain alignment of the followers. The central roller axle pin 
90a is held in openings in the piston 86a. 
In the variation of FIG. 4b, flat inner ends of the axle pins 84b extend 
inward of the inner surface 39 and engage flats 72b on the modified piston 
86b to maintain follower alignment. The central roller axle pin 90b is 
again retained in openings in the piston 86b. 
Third Embodiment--RVDAH 
FIGS. 5-7 with added subletter views illustrate variations of still another 
embodiment of the invention wherein a two step variable lift valve 
mechanism is provided in an overhead cam engine having direct acting cam 
followers. As shown in FIG. 5, the engine 100 includes a block, head 
and/or carrier component 102 supporting a camshaft 103 and a plurality of 
roller variable direct acting hydraulic valve lifters (RVDAH) 104c, only 
one being shown. The camshaft 103 includes a pair of spaced high lift cams 
106 and a central low lift cam 107 for each of the inlet valves 108 and/or 
exhaust valves of the engine that are actuated by an RVDAH lifter. In the 
engine shown, each lifter 104c has a high lift outer cam follower 110 
associated with the high lift cams 106 and a low lift inner cam follower 
111 associated with the low lift cams. 
Detailed construction of the lifter is best shown in the variation of valve 
lifter 104 illustrated in FIGS. 5a, 5b, 6 and 7. The outer follower 110 
has an annular body 112 with a cylindrical outer surface 114 that is 
reciprocable in a sleeve or bore 115 in the engine cam carrier or other 
component 102. The outer surface 114 extends along an upper portion or 
head 116 of the body and an adjoining depending skirt 117 portion. The 
head 116 also has a cylindrical inner surface 118 spaced concentrically 
within the outer surface and terminates downward in a radial abutment or 
shoulder 119. 
Between the inner and outer surfaces 114, 118, are laterally spaced 
recesses or pockets 120 in which rollers 122 are located. The rollers 122 
engage the cams 106 and are rotatably carried by suitable bearing means 
supported on axle pins 124, 124' held by locator pins 125 in transverse 
openings of the follower head 116. Preferably, one of the pins 124' has an 
outer end 126 that extends outward of the outer surface 114 into a mating 
groove 127 of the associated bore 115. This prevents rotation of the 
follower and maintains the rollers in alignment with their respective cams 
106. 
The inner follower 111 comprises a hollow cylinder 130 having a closed end 
131 and a depending cylindrical outer wall 132 open at the other end. The 
closed end 131 is engageable with the central low lift cam 107 to follow 
its lift curve. The outer wall 132 is received in the cylindrical inner 
surface 118 of the outer follower 110 for reciprocation on a common axis 
134. Grooves or flats 135 are engaged by inner ends 136 of the pins 124, 
124' which extend inwardly beyond the inner surface 118 of the outer 
follower to prevent relative rotation of the followers. 
Within the follower cylinder 130, there is received a small hydraulic lash 
adjuster or hydraulic element assembly (HEA) 138. This HEA includes a 
hollow piston 139 internally carrying a plunger 140 with a check valve 141 
and other elements similar to conventional HEA's although of smaller size 
in preferred embodiments. Elements 50-52 of FIG. 3 are of generally 
similar character and function. A groove 142 may be provided on the 
plunger 140 to control oil leakage from the piston. The piston 139 
directly engages the stem of the valve 108 for actuating it in an opening 
direction. A valve spring 143 acting against the valve and a fixed seat, 
not shown, in the engine biases the valve 108 in a closing direction. A 
concentric outer spring 144, acting between the shoulder 119 and a fixed 
seat, not shown, similarly biases the rollers of the outer follower 110 
against the high lift cams 106. 
An annular or arcuate groove 145 around the outer surface 114 of the body 
112 receives oil from a gallery 146 in the component 102 and carries it 
through oil passages 147, 148 in the body 112 and cylinder 130 to deliver 
oil from the groove 145 to the interior of the cylinder for supplying oil 
to the lash adjuster (HEA). 
Lock pins 150 carried in the body 112 of the outer follower are open to the 
groove 145. They cooperate with elements similar to openings 64, springs 
67, retaining pins 68 and flats 70 of FIG. 3 to lock the inner and outer 
followers 110, 111 together or release them in the manner described with 
regard to the FIG. 3 embodiment. Oil pressure may be controlled in the 
manner described for that embodiment. 
FIGS. 6a and 7a show a variation of the third RVDAH embodiment wherein the 
inner ends 136a of the axle pins 124, 124' are of reduced diameter to 
extend into grooves 135a of relatively narrow width in the modified 
cylinder 130a. This provides an alternate manner of maintaining alignment 
of the inner and outer followers. A comparable variation is shown in the 
lifter 104c of FIG. 5 where the outer ends of the axle pins are of reduced 
diameter and engage narrower grooves in the sleeve 115 to prevent rotation 
of the lifter in its bore. Other arrangements, such as that of FIGS. 10 
and 11 can be used as alternatives. 
FIGS. 6b and 7b show another variation, similar to that of FIG. 2, wherein 
a guide pin 71b carried in the modified body 112b extends into a narrow 
groove 72b in the cylinder 130b to maintain alignment of the followers. 
In operation, camshaft rotation causes the high lift cams 106 to actuate 
the outer follower on a full or high lift curve while the low lift cam 107 
selectively actuates the inner follower 111 on a partial or low lift curve 
as determined by the cam profiles. When the oil pressure is controlled at 
a low level, the lock pins 150 are not engaged, as is shown in FIG. 7, and 
the valve is moved through the low lift curve by the low lift cam acting 
on the inner follower 111 while the outer cam follower 110 idles. When oil 
pressure is raised above a preset level, the lock pins 150 are actuated to 
lock the inner and outer followers together so that the high lift cams 106 
control valve motion to follow the high lift curve through the 
interconnected followers 110, 111. 
The rollers 122 on the outer follower 110 are effective to reduce the 
friction of the valve mechanism during operation on the high lift curve 
and also during low lift operation when the outer follower 110 is moved in 
a high lift idling motion against the bias of the outer return spring 144. 
While it would be possible to also provide a roller on the inner follower 
111 to further reduce friction loss, this would require an increase in the 
size and mass of the inner follower which may not be acceptable. Instead, 
the FIGS. 5-7 embodiment allows the HEA 138 lash adjuster to be located 
between the rollers to provide a compact and relatively low mass assembly. 
Since the friction created on the low lift valve curve by the cam 107 
moving the lighter low lift follower 111 only against the valve spring 143 
is relatively low, this provides a preferable compact and efficient design 
for use in many overhead cam direct acting valve gear applications. 
Fourth Embodiment--RDAH 
Turning now to FIGS. 8 and 9, another embodiment is illustrated which is 
based upon the RVDAH of FIGS. 5-7 but is simplified for operation as a 
single step non-variable lift valve mechanism. Like reference numerals are 
again used for like parts. The engine arrangement is similar to that of 
FIG. 5 wherein an engine component 102 supports a camshaft 103 and 
provides a sleeve or bore 115 having a guide groove 127 and communicating 
with an oil pressure gallery 146. At least one inlet valve 108 is provided 
for each cylinder of the engine as are exhaust valves, not shown. A spring 
143 biases the valve 108 toward closing. Central cam 107, cylinder 130 and 
return spring 144 are omitted. 
The camshaft carries only two spaced cams 106 which are configured to 
actuate the valve over the full non-variable lift curve. The cams engage 
spaced rollers 122 carried by suitable bearing means on axle pins 124, 
124' fixed by locator pins 125 in a cup-like body 152 of a cam follower 
154. The extended outer end 126 of pin 124 engages a groove 127 to prevent 
rotation of the follower 154. 
The follower body 152, includes a skirt 155 depending from a head 156 
carrying the rollers 122. Between the rollers, the head defines a cylinder 
158 closed at the top in which a lash adjusting HEA 138 is received. The 
HEA directly engages the stem of a valve 108 and receives oil through an 
oil passage 159 extending into the body to the cylinder 158 near the 
closed end. The HEA 138 together with the follower 154 including the body 
152 and rollers 122 form an assembly comprising a roller direct acting 
hydraulic valve lifter (RDAH) 160. 
In operation, the cams 106 actuate the rollers to move the valve lifter 160 
and the valve 108 in a preset lift curve. The arrangement provides a 
compact construction for a direct acting valve lifter having friction 
reducing rollers by reason of the split cams 106 actuating dual rollers 
122 with the HEA 138 located between the rollers. With this arrangement 
and proper sizing of the lifter 160 and its HEA 122, the distance between 
the camshaft and the end of the valve stem can be reduced to little or no 
more than is occupied by currently available non-roller direct acting 
hydraulic valve lifters. 
Anti-Rotation Variation 
FIGS. 10 and 11 show another variation of lifter anti-rotation device which 
is applicable to any of the embodiments previously shown where nonrotation 
is desired. In this case, it is shown as a variation 104' of the RVDAH 
lifter embodiment of FIGS. 5a, 5b, 6 and 7. 
This RVDAH lifter 104' deletes the long pin 124' and mating groove 127 of 
the RVDAH 104 and instead uses two identical axle pins 124 which do not 
extend beyond the body 112'. Rotation is prevented by a steel 
anti-rotation pin 162 which extends into two half round mating slots 163, 
164 in the body 112' and its supporting component 102' respectively. The 
pin 162 is preferably fixed to the component 102' such as through a tab 
166 which is secured to the outer end of the pin 162. This assembly is 
then attached to the component 102' such as by a screw 167 holding the tab 
in place. Any other suitable retention means might also be applied. 
This anti-rotation device has the advantage, when the support component 
102' is aluminum or the like, that the reciprocating friction and wear is 
between the harder steel elements of the body 112' and the pin 162. In 
this way, wear or abrasion of the aluminum material is avoided. Also, the 
slot 163 can be limited in length to the thick head portion of the body 
since the pin 162 is installed after the lifter 104' has been assembled 
into its associated bore. 
While the invention has been described by reference to certain preferred 
and alternative embodiments and variations, it should be understood that 
numerous additional changes could be made within the spirit and scope of 
the inventive concepts described. For example, solid tappets or other lash 
adjusters could replace the HEAs. Also, lifters according to the invention 
may be applied to all or less than all of the intake and/or exhaust valves 
of the engine. Accordingly it is intended that the invention not be 
limited to the disclosed embodiments, but that it have the full scope 
permitted by the language of the following claims.