INTRODUCTION
[0001] The present invention relates generally to hydraulic lash adjusters and, more particularly,
to lightweight adjusters applied within direct-acting valve gear.
BACKGROUND OF THE INVENTION
[0002] Valve gear of the direct-acting type employs tappets having one end thereof contacting
the engine camshaft and the other end contacting the end of the stem of the combustion
chamber valve. Direct-acting valve gear offers the advantage of low mass, fewer working
parts and higher stiffness due to the elimination of the rocker arm and/or push rods.
Low mass and high stiffness result in a high natural resonant frequency which allows
the valve gear to attain higher RPM's before valve mismotion occurs. Direct-acting
valve gear also permits the use of lighter valve spring loads for a given valve motion
and engine speed, as compared with those used in other valve gear arrangements. The
low mass and high stiffness of the system also permits valve lift velocities and accelerations
which increase the area under the valve lift curve and thus provide increased specific
engine output. Although other overhead cam configurations can be made to have comparable
lift velocities and accelerations, a direct-acting valve gear arrangement offers the
additional advantage of permitting rotation of the cam contacting surfaces as the
lifter rotates, which is not possible with rocker arm type valve gear arrangements.
Direct-acting valve gear arrangements, therefore, permit higher cam contact streses.
[0003] In addition, the cam profile for other overhead cam valve gear arrangements with
high lift accelerations and velocities is more complex than that required for direct-acting
valve gear. The simpler cam profile requirement of direct-acting valve gear results
in less manufacturing difficulties and less cost in the valve gear when high velocities
and accelerations are desired.
[0004] Tappets for direct-acting valve gear are received in a guide bore provided in the
engine above the combustion chamber and reciprocated therein in a film of engine lubricant
provided to the guide bore. Tappets for direct-acting valve gear must have a sufficient
diameter to shroud the valve spring and provide adequate lift. Accordingly, tappets
for direct-acting valve gear generally have a length-to- diameter ratio in the order
of magnitude of one. When the tappet bore is formed in cast iron, the body of the
tappet may be formed from a suitable iron-based material or alloy steel to match the
hardness and the thermal expansion properties of the guide bore.
[0005] It has long been desired to find a way to provide a tappet for direct-acting valve
gear of substantially lower weight than iron or steel and yet provide a tappet having
similar durability and wear properties. Lower weight tappets permit greater valve
acceleration for a given valve spring load.
[0006] Moreover, where the engine combustion chamber head is formed of aluminum, it is desirable
that the tappet for such a direct-acting valve gear application match the surface
wear and thermal expansion properties of the aluminum engine head in order to prevent
excessive oil flow at engine operating temperatures. Tappets of iron or steel possess
the requisite durability and surface wear resistance but exhibit a substantially lesser
coefficient of thermal expansion. Thus, if the iron or steel tappets are optimally
sized to the tappet guide bore when the engine is cold, upon the engine reaching normal
operating temperatures, the tappet will fit loosely in the guide bore. Conversely,
if an iron or steel tappet is optimally sized to fit the tappet guide bore in the
aluminum engine head at normal engine operating temperatures, assembly at room temperature
will be impossible because of an interference fit. Furthermore, if the assembly is
performed with the engine head at normal engine operating temperatures and optimum
clearances, the tappet will be seized in the guide bore upon the engine cooling after
such assembly.
[0007] It has, therefore, been desirable to find a way to provide hydraulic lash adjusting
tappets for direct-acting valve gear in engines having combustion chamber heads of
aluminum or similar lightweight high-thermal expansion type materials. It has further
been desirable to provide a hydraulic lash adjusting tappet for direct-acting valve
gear with engines having aluminum heads in which the tappet will be capable of operating
against a camshaft formed of hardened iron-based material. This generally requires
that the cam face of the lightweight tappet be compatible in hardness and wear properties
with the hardened face of the cam lobe. Furthermore, it has been desirable to find
a way to economically and conveniently provide in such a hydraulic lash adjusting
tappet a controlled leakdown clearance, yet provide a lightweight tappet body.
BRIEF DESCRIPTION OF THE INVENTION
[0008] The present invention overcomes many of the above-described shortcomings of the prior
art by providing a hydraulic lash adjusting tappet for use in the valve gear of an
internal combustion engine including body means molded of a material having a coefficient
of thermal expansion not less than 22 x 10 /unit length/°C as measured in the range
of 20-100°C, such as plastic or aluminum. A face member is entrained within the body
means by the molding thereof and defines a reaction surface which, in application,
contacts a cam lobe. Finally, hydraulic lash adjusting means are provided which operatively
associate with the body means and define a second reaction surface which, in application,
will contact an associated engine valve gear component. In operation, the second reaction
surface is movable with respect to the face member reaction surface for lash adjustment
of the valve gear. This arrangement provides the advantage of an extremely lightweight,
inexpensive hydraulic lash adjuster which will perform satisfactorily in the environment
of a typical internal combustion engine.
[0009] In its preferred embodiment, the present invention provides a hydraulic lash adjusting
tappet of the type used in direct-acting valve gear for internal combustion engines
operating at high RPM. The hydraulic tappet of the present invention is of the type
having a general configuration known as a "bucket" tappet where the body of the tappet
has a diameter substantially larger than that of the hydraulic plunger contained therein.
The tappet of the present invention has a greater mass, or body, portion thereof having
the outer periphery thereof compatible for being slidably received in direct contact
with a guide bore formed in an aluminum engine head. The tappet of the present invention
contains a hydraulic lash adjusting unit in the form of a plunger-piston assembly
formed of steel and employs a one-way valve means and a high-pressure oil chamber
therein for providing lash adjustment.
[0010] A reservoir is formed in the plastic body in the region surrounding one end of the
plunger assembly. The tappet of the present invention has a steel alloy member provided
on the cam face of the tappet for wear resistance and compatibility with the driving
surface of a hardened iron-based engine cam. The face member is generally cup-shaped
and embedded within the body during its molding process. This construction enables
the tappet to be slidably compatible with the guide bore and further to match the
thermal expansion characteristics of the aluminum engine head to maintain the proper
running clearance between the tappet and the guide bore for necessary directional
control and lubrication between the sliding surfaces without excessive oil flow at
high temperatures.
[0011] The body of the present tappet has a generally tubular outer wall construction and
an annular hub disposed within the outer wall and spaced therefrom with an end wall
extending transversely therebetween. A web structure extends radially inwardly from
the outer wall to support the hub. The hydraulic plunger and piston assembly are received
in the inner hub, and a portion of the hydraulic reservoir is formed between the inside
face of the web, the end of the piston and inner periphery of the hub. This unique
construction provides for a relatively larger diameter of the outer periphery of the
tappet body, yet provides for ease of manufacturing in that the outer wall, hub and
web may be formed integrally. The hydraulic lash adjusting assembly is preassembled
and inserted into the hub and retained therein.
[0012] The unique construction of the present tappet further provides an arrangement wherein
the tightly controlled leakdown surfaces between the piston and plunger of the lash
adjusting unit are formed in the iron-based or steel parts. The use of the intermediate
plunger therefore makes the use of a lightweight body practical over the range of
normal engine operating temperatures. The present invention thus provides a solution
to the problem of providing a lightweight tappet for use in direct-acting valve gear
and one that is compatible with material of an aluminum engine head and functionally
compatible with the hardened iron-based engine camshaft, all providing adequate wear
resistance leakdown surfaces.
[0013] In several alternative embodiments of the invention, various face member configurations
are disclosed in which the skirt portion of the face member can be circumferentially
continuous or segmented to profide retention surfaces operative to react against the
material of the body to prevent relative movement therebetween. The skirt circumscribes
a generally disc-shaped face portion of the face member and can be embedded within
the outer wall or the annular hub of the body. Finally, the face portion of the face
member is substantially co-extensive with the nominal cross-sectional area of the
outer annular wall to maximize potential contact area with the cam.
[0014] These and other aspects and advantages of the invention will become apparent upon
reading the following Specification which, along with the patent drawings, describes
and discloses a preferred and several alternative embodiments of the invention in
detail.
[0015] A detailed description of the embodiments of the invention makes reference to the
accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0016]
FIGURE 1 is a cross-sectional portion of the direct-acting valve gear of an internal
combustion engine illustrating the tappet as installed in the engine;
FIGURE 2 is a cross-sectional view of a typical prior art steel-bodied bucket tappet;
FIGURE 3 is an end view of the plunger end of the preferred embodiment of the hydraulic
tappet of the present invention;
FIGURE 4 is a cross section taken along section indicating lines 4-4 of FIGURE 3 and
shows the tappet with the hydraulic lash adjusting means assembled therein;
FIGURE 5 is a cross-sectional view of the face member shown in assembly in FIGURE
4;
FIGURE 6 is an alternative embodiment of the face member of FIGURE 5;
FIGURE 7 is a second alternative embodiment of the face member of FIGURE 5;
FIGURE 8 is a cross-sectional view taken along section indicating lines 8-8 of FIGURE
7 and shows the interfitting relationship between the material forming the lash adjuster
body and the retention surfaces defined by the skirt portion of the face member;
FIGURE 9 is a view similar to FIGURE 3 and shows an alternative embodiment of the
tappet;
FIGURE 10 is a section view taken along section indicating lines 10-10 of FIGURE 9;
FIGURE 11 is a view similar to FIGURE 3 and shows another alternative embodiment of
the invention; and
FIGURE 12 is a section view take along section indicating lines 12-12 of FIGURE 11.
DETAILED DESCRIPTION OF THE
PREFERRED AND ALTERNATIVE EMBODIMENTS OF THE INVENTION
[0017] Referring to FIGURE 1, a hydraulic lash adjusting tappet 10 is slidably received
in a guide bore 12 provided in a cylinder head 14 of an internal combustion engine
16. A camshaft 18 having a cam lobe 20 contacts the upper end or cam face 22 of the
tappet. A typical combustion chamber valve 24 is shown seated on a valve seating surface
formed in the cylinder head, with a stem portion 26 of the valve extending substantially
vertically upwardly through a valve guide 28 formed in the cylinder head, with the
upper end 30 of the valve stem contacting the lower end of the tappet. The valve is
biased to the closed position by valve springs 32 having their lower ends registered
against the exterior of the upper portion of valve guide 28 and their upper ends in
contact with a retainer 34 secured to the valve stem adjacent its upper end and retained
thereon in a suitable manner as, for example, by the use of a split keeper 36, which
is well-known in the art. A supply of lubricant is provided to tappet 20 from a pressurized
source (not illustrated) through a gallery 38 and a passage 40 interconnecting gallery
38 and guide bore 12.
[0018] Referring to FIGURE 2, a typical all-steel prior art bucket tappet is illustrated
in which a hardened steel or iron cap 42 is affixed to a mild steel body 44 by welding
the circumferential joint 43 therebetween. This type of assembly is thoroughly treated
in prior art Patent 4,270,496.
[0019] Referring to FIGURES 3, 4, and 5, the presently Preferred Embodiment of the tappet
10 is shown wherein the body, indicated generally at 46, is shown as formed preferably
integrally with an outer tubular wall portion 48 having a transverse end wall 50 extending
generally radially inwardly from the inner periphery of the outer tubular wall portion
at a location adjacent the upper end thereof (as viewed in FIGURE 4). The end wall
50 has formed preferably integrally therewith a tubular hub portion 52 extending axially
from the end wall in a downward direction. The end wall isolates hydraulic pressure
inside hub 52 from a face member 54 cam face 22. Cam face 22 defines a face member
reaction surface which, in application, contacts cam lobe 20. The hub 52 has the inner
periphery thereof extending in general parallel relationship to the outer periphery
of the tubular wall portion 48. The outer periphery of the tubular wall portion 48
is sized to be received in the tappet guide bore 12 (FIGURE 1) in a generally closely
fitting relationship. At least one web 56 is provided to support hub 52 which extends
radially outwardly therefrom to the inner surface of wall 48.
[0020] In the presently preferred practice of the invention, the outer wall portion 48,
end wall 50, hub portion 52, and web 56 are formed integrally from a suitable lightweight
material having a coefficient of thermal expansion of at least 22.0 x 10-
6/unit length/°c, as measured in the range 20 to 100°c. The outer surface of the tubular
wall portion has a wear-resistant surface formed thereon as, for example, by anodic
hard-coating electrolysis metal plating (in the case of an aluminum body), or, the
surface of a high silicon aluminum alloy in order to have the surface hardness value
of at least 8 (topaz) as measured on the Mohs' scale. In the presently preferred practice,
the integrally formed body, web, end wall, and hub are formed of a material having
a bulk density less than 2.85 g/cu c, such as graphite reinforced plastic. The material
may include wear additives such as graphite fibers/particulates, Teflon or fiberglass.
As is well-known to those dealing in the specification of plastic materials for high-temperature
applications, additives can be included to enable matching of thermal expansion coefficients
of the plastic and the metal face member 54.
[0021] Cam face member 54 is a relatively thin disk-shaped face portion 58 and a generally
annular skirt portion 60 depending from the radially outward- most portion thereof.
Skirt portion 60 has formed therein a number of circumferentially spaced, radially
directed passageways 62. Body 46 is injection-molded to entrain or capture face member
54 wherein material comprising body 46 flows through passageway 62 and to establish
intimate contact with the retention surfaces defined thereby. Thus, after the material,
molded into the form defined by body 46 takes a set, face member 54 is permanently
joined to body 46 and restained from relative displacement with respect thereto. Although
retention surfaces of the preferred embodiment are manifested by bores or passageways
62, as will be seen hereinbelow, retention surfaces can be defined any number of ways
within the spirit of the present invention. In the presently preferred practice of
the invention, the cam face member 54 is formed of material, having a bulk density
not less than 7.5 g/cu c and a surface hardness value on the face member reaction
surface or cam face 22 thereof of at least 89, as measured on the Rockwell 15 IN scale
for a minimum effective depth of at least 0.012 inches (0.3 millimeter). However,
it is to be understood that materials having a bulk density less than 7.5 g/cu c may
be employed for the cam face member provided the surface hardness thereof is maintained.
The cam face member is preferably formed of an iron-base material as, for example,
a steel alloy having a desired amount of chromium added thereto for providing a desired
corrosion resistance; however, a suitably hard ceramic or cermet material may alternatively
be employed for base member 54, if desired. In the presently preferred practice of
the invention, the body member 46 preferably has a bulk density less than 40% of the
bulk density of the cam face member 54, although the bulk density of the body member
46 to the bulk density of the cam face member 54 can be greater than 40% if a suitably
hard, lightweight material is employed for the cam face member.
[0022] The body 46 has a hydraulic lash adjusting unit indicated generally at 64 slidably
received in the inner periphery of the hub 52 in a generally closely fitting relationship.
The hydraulic lash adjusting unit 64 comprises a generally cup-shaped plunger member
66 having the open end thereof disposed adjacent the end wall 50 and the closed end
extending axially slightly downwardly from the lower end of hub 52 and transversely
thereacross to provide a second reaction surface 68 for contacting upper end 30 of
valve stem portion 26 (see FIGURE 1). The plunger 66 has a precision bore 70 provided
on the inner periphery thereof which bore is maintain in tight tolerances of diameter,
circularity, and surface finish. The plunger has received therein in precision sliding
contact therein a piston member 72 having the outer periphery thereof sized to interfit
the plunger bore 70 in closely controlled clearance to provide control of the passage
or leakdown of hydraulic fluid between the bore 70 and the piston 72. The piston 72
has a generally cup-shaped configuration with the open end thereof disposed upwardly
adjacent end wall 50 of body 46 and has an interior cavity 74 provided therein with
a vertically extending passage 76 extending downwardly through the closed end of piston
72. A one-way valve means, in the form of a check ball 78, is disposed to contact
the lower end periphery 80 of the passage 76 for which periphery 80 provides a valve
seat for the check valve 78. The check valve is retained by a cage 82 attached to
the lower end of piston 72. A spring 84 is provided between the cage 82 and the check
ball for biasing the check valve 78 to the closed position against valve seat 80.
[0023] An annular recess 86 is provided in the inner periphery of hub 52 of body 46 adjacent
the upper or end wall end thereof for providing a portion of a reservoir for hydraulic
fluid. At least one bypass passage 88 is provided preferably for communicating the
annular recess 86 with the cavity 74 provided in the piston 72 to provide a divided
chamber hydraulic fluid reservoir for supplying the check valve 78, the reservoir
communicating with the passage 76. Web 56 extends radially inwardly from wall portion
48 to the hub 52 and has formed therethrough a hydraulic fluid passage 90 which communicates
with annular recess 86 from a fluid collecting recess or groove 92 provided in the
outer periphery of tubular wall 48 of the body 46.
[0024] In operation, valve 20 is biased in a closed position by springs 32 and, upon rotation
of the camshaft 18 in timed relationship to the events of the combustion chamber to
the position shown in solid outline in FIGURE 1, the upper surface of the tappet 10
is registered against the base circle portion of the cam with lobe 20 wherein so not
to contact the upper or cam face 22 of the tappet. Upon rotation of the camshaft 18
to the position shown in dashed outline in FIGURE 1, the cam lobe 20 contacts upper
face 22 of the tappet, causing the tappet to move downwardly to the position indicated
in dashed outline thereby opening the combustion chamber valve 24. Upon subsequent
rotation of the camshaft to return to the solid line position of FIGURE 1, the valve
event is complete, and the valve is reseated on the valve seat.
[0025] Although the embodiment of FIGURE 3 illustrates the invention in its presently preferred
form, wherein the end wall 50 of body 46 has a plurality of weight-reducing holes
94 provided thereabout in circumferentially spaced arrangement, it will be understood
that other shapes and configurations may be employed for reducing the weight of end
wall 50 and web 56. The end wall 50 in the presently preferred practice is solid in
the region extending transversely across the upper end of the hub 52. However, it
will be understood that the solid portion of the end wall 50 across the end of hub
52 may be omitted if the cam face member 54 is fluidly sealed to the outer wall about
its periphery and mechanically restrained against the force of the high-pressure hydraulic
fluid.
[0026] In operation, with the engine cam lobe 20 in a position shown in FIGURE 1, the plunger
spring 96, aided by hydraulic pressure, urges the piston 72 in an upward direction
maintaining the upper end thereof in contact with the undersurface of the end wall
50 and urges the plunger 66 in the downward direction until the reaction surface 68
thereof contacts the upper end 30 of the valve stem 26, thereby eliminating lash in
the valve gear. This causes an expansion of a high-pressure chamber 98 formed between
the closed ends of plunger 66 and piston 72, which draws open the check ball 78 to
a position spaced from valve seat 80 thereby permitting flow into the chamber 98.
Upon cessation of the expansion of chamber 98, the check ball 78 closes under the
biasing of spring 84. Upon subsequent rotation of cam lobe 20, the ramp of the cam
lobe begins to exert a downward force on the upper face 22 of the tappet 10, tending
to compress the piston 72 into the bore 70 in the plunger 66, which compression is
resisted by fluid trapped in chamber 98. The fluid trapped in chamber 98 prevents
substantial movement of the piston 72 relative to the plunger 66 and transmits the
motion through the bottom face 68 of the plunger onto the top 30 of the valve stem
26. It will be understood by those having ordinary skill in the art that a minor movement
of the plunger 66, with respect to the piston 72, occurs, the magnitude of which is
controlled by the amount of fluid permitted to pass between precision bore 70 and
the outer surface of piston 72 (leakdown surfaces). The piston 72 and plunger 66 thus
act as a rigid member transmitting further lifts of the cam lobe 20 for opening the
valve 24.
[0027] Lash adjusting unit 64 can be held in assembly within hub 52 in a number of ways.
For example, a radially inwardly opening circumferential groove can be formed within
hub 52 and a snap ring fitted therein to limit the downward displacement of lash adjusting
unit 64. Alternatively, the lowermost portion of hub 52 can be deformed radially inwardly
to likewise define a downward limit of travel for lash adjusting unit 64. Still another
alternative means of retention is described in United States Patent 4,373,477. However,
a particularly advantageous approach to the retention of lash adjusting unit 64 is
in the application of a bottlecap-type retainer 100 which is characterized by a plurality
of radially inwardly directed tangs 102 lanced inwardly from a skirt portion 104 thereof.
In assembly, retainer 100 is aligned concentrically with hub 52 and inserted thereover
by displacing it upwardly until the uppermost surface of a body portion 102 abuts
the lowermost surface of hub 52. In so doing, tangs 102 penetrate the outer surface
of hub 52 and establish an extremely tenacious interfit therewith. Base portion 106
defines a passageway 108 therethrough in register with the bore defined by hub 52
but of slightly smaller diameter. The lowermost portion of plunger 66 has an area
of reduced diameter forming a shoulder 110 which, contacts base portion 106 of retainer
100 when lash adjusting unit 64 is in its lowermost limit of travel. Use of the bottlecap-design,
retainer 100 is considered particularly attractive in the practice of the preferred
embodiment of the invention inasmuch as the plastic body material is relatively soft.
The outer circumferential surface of hub 52 can be designed in a uniform, easily moldable
configuration inasmuch as the tangs 102 can easily penetrate the surface thereof.
This eliminates the needs for machined or molded contours molded in the hub 52 for
mating or receiving the retainer as is required in other design types. For clarity
of underlying detail, FIGURE 3 is illustrated with retainer 100 removed.
[0028] Referring to FIGURE 6, the alternative embodiment of the cam face member is illustrated
at 112, which is substantially identical to face member 54, with the exception that
the outer peripheral portion of skirt portion 60 is removed to establish a circumferential
step 14 between the skirt portion l16 and face portion 118. In the embodiment of the
cam face member illustrated in FIGURE 5, the outer diameter of skirt portion 60 is
slightly less than the outer diameter of outer tubular wall portion 48 to enable the
plastic material thereof to circumferentially embrace substantially the entire outer
surface of skirt portion 60. However, in so doing, a small amount of cam face 22 surface
area has been sacrificed. The cam face member l12 embodiment of FIGURE 6 overcomes
that shortcoming by providing step 114 which renders the cam face 120 of cam face
member 112 substantially co-extensive with the nominal cross-sectional area of wall
portion 48.
[0029] Referring to FIGURES 7 and 8, a second alternative embodiment of cam face member
is illustrated generally at 122 including a face portion 124 and a skirt portion 126.
Face portion 124 defines a cam face 128 which, in application, is substantially co-extensive
with the nominal cross-sectional area of outer tubular wall portion 48. Skirt portion
126 has a diameter less than that of face portion 124 and is joined thereto through
a downwardly inwardly converging transitional portion 130. The cam face member 122
of FIGURE 7, not only presents a maximized cam face 128 area to cam lobe 20, but also
tolerates a degree of thermal expansion coefficient mismatch between the body 46 and
cam face member 122. Skirt 126 has a number of circumferentially spaced generally
trapezoidally shaped reliefs 132 formed therein and defines complementary pairs of
retention surfaces 134 thereby. Retention surfaces 134 are substantially axially misaligned
whereby, once injection-molded with a body 46', intimately embrace the material thereof
which has flowed adjacent thereto. Although the skirts illustrated in FIGURES 5, 6,
and 7 extend substantially parallel to the axis of body 46, it is contemplated that
they could be angled inwardly or outwardly to effectively increase the retention surface
area of the cam face member.
[0030] Referring now to FIGURES 9 and 10, an alternative embodiment of the tappet 10 of
the present invention is illustrated as having a body indicated generally at 136 and
a cam face member illustrated generally at 138. No lash adjusting unit is illustrated
for the sake of simplicity. Body 136 comprises an outer tubular portion 140, a tubular
hub portion 142, and a plurality of circumferentially spaced webs 144 integrally interconnecting
outer and hub portions 140 and 142, respectively. Cam face member 138 includes a face
portion 146 and an annular skirt portion 148, depending downwardly therefrom at a
point radially intermediate the center and the outside circumference of face portion
146. Hub portion 142 is provided within area of increased diameter 150 within which
is moldingly entrained skirt portion 148. Skirt portion 148 has a number of circumferentially
spaced, radially directed passageways 152 formed therein which establish retention
surfaces in intimate contact with the material of hub 142 which has flowed therethrough
during the molding process. A fluid passage 90' extends through one of the webs 144
in a manner described hereinabove in relation to the embodiment illustrated in FIGURES
3 and 4. Skirt 148 includes a local discontinuation 154 aligned with passageway 90'
to prevent the obstruction thereof. When provided with lash adjusting unit 64, the
embodiment of the invention illustrated in FIGURE 10 operates substantially identically
as that described hereinabove.
[0031] Referring now to FIGURES 11 and 12, still another alternative embodiment of the tappet
10 of the present invention is illustrated as having a body indicated generally at
154 and a cam face member 156. The embodiment of FIGURE 12 has structure very similar
to that illustrated in FIGURE 4 including an outer tubular portion 158, a hub portion
160, and an integrally interconnecting plurality of circumferentially spaced webs
162. Body 154 has an area of increased diameter 164. Cam face member 156 comprises
a face portion 166 and a tubular skirt portion depending therefrom at a point nearly
radially co-extensive with the outer circumferential edge of face portion 166. A plurality
of radially directed passageways 170 are formed within skirt 168 and are entrained
within the area of increased diameter 164 during the molding process of body 154 when
the material therecomprising flows through passageways 170. As in the case of the
embodiment illustrated in FIGURES 9 and 10, when the tappet body illustrated in FIGURE
12 is provided with a lash adjuster unit 64, its operation is substantially as described
hereinabove.
[0032] The novel construction of the present tappet provides lash adjustment by precision
fit of a piston in a bore formed in the plunger slidably received in the hub and thus
eliminates the need for precision fitting leakdown control surfaces on the interior
of the tappet hub. The area, surrounding the plunger between the web and the tubular
wall of the body and the cam face member, provides a reservoir for fluid to supply
the one-way check valve for hydraulic lash adjustment. The tappet of the present invention
provides a unique, lightweight tappet adapted for direct contact with the surfaces
of a guide bore provided in an aluminum engine cylinder head. The body of the tappet
of the present invention has the outer periphery thereof provided with a hard surface
or hard coating to be slidingly compatible with the properties of the aluminum engine
head. The tappet is formed of a suitable lightweight material, having surface hardness
properties compatible with those of the surface of the aluminim engine head and the
tappet material matching the coefficient of thermal expansion of the aluminum engine
head, to maintain control of the clearances therebetween for providing proper guidance
during reciprocation of the tappet and maintenance of an adequate lubricant film therebetween.
The tappet of the present invention employes a hardened, iron-base, cam-face member
moldingly attached to the body for wear-resistant driving contact, compatible with
the surface of the engine cam formed of iron-based material having a hardened surface.
[0033] It is to be understood that the invention has been described with reference to specific
embodiments, which provide the features and advantages previously described, and that
such specific embodiments are susceptible of modification, as will be apparent to
those skilled in the art. Accordingly, the foregoing description is not to be construed
in a limiting sense.
1. A hydraulic lash adjusting tappet (10) for use in the valve gear (18, 24) of an
internal combustion engine (16), said tappet comprising:
body means (46),
a face member (54) defining a reaction surface (22) adapted for contacting a cam lobe
(20), and
hydraulic lash adjusting means (64) operatively associated with said body means and
including structure defining a reaction surface (68) adapted for contacting associated
components (24) of the engine valve gear, said reaction surface movable with respect
to said face member reaction surface for lash adjustment of said valve gear, characterized
in that
said body means is formed of moldable material having a relatively high coefficient
of thermal expansion such as aluminum or plastic; and
said face member is joined to said body means by molding of said body means about
a portion of said face member.
2. The tappet defined in Claim 1 wherein said face member comprises a generally disc-shaped
face portion (58) defining said reaction surface and a generally annular skirt portion
(60) axially depending from said face portion entrained within said body means.
3. The tappet defined in Claim 1, wherein said body means structure is formed of material
having a bulk density less than 2.85 grams per cm3.
4. The tappet defined in Claim 1, wherein said face member is formed of steel and
said body means is formed of material having coefficient of thermal expansion not
substantially less than 22 x 10-6 per unit length per °C as measured in the range 20-100°C.
5. The tappet defined in Claim 1, wherein said face member defines retention surfaces
(62) operative to react against the material of said body means thereadjacent for
preventing relative movement therebetween.
6. A hydraulic lash adjusting tappet for use in the valve gear of an internal combustion
engine, said tappet comprising:
body means formed of material having a coefficient of thermal expansion not substantially
less than 22 x 10-6 per unit length per °C as measured in the range 20-100°C including structure defining,
(i) an outer annular wall (48),
(ii) an annular hub disposed (52) within said annular wall and spaced therefrom, and
(iii) a portion (56) interconnecting said wall and hub;
a face member defining a reaction surface adapted for contacting a cam lobe and joined
to said body means by molding of said body means about a portion of said face member;
and
hydraulic lash adjusting means movably received within said hub and including structure
defining a reaction surface adapted for contacting associated components of the engine
valve gear, said reaction surface extending generally parallel to said face member
reaction surface and movable with respect thereto for lash adjustment of said valve
gear.
7. The tappet defined in Claim 6, wherein said face member is formed of steel and
said body means outer wall, hub and interconnecting portion are formed of substantially
plastic material.
8. The tappet defined in Claim 6, wherein said body means structure is formed of material
having a bulk density less than 2.85 grams per cm3.
9. The tappet defined in Claim 6 wherein said face member comprises a generally disc-shaped
face portion defining said reaction surface and a generally annular skirt portion
axially depending from said face portion entrained within said body means.
10. The tappet defined in Claim 9, wherein said skirt portion extends axially into
said outer annular wall.
11. The tappet defined in Claim 9, wherein said skirt portion extends axially into
said hub.
12. The tappet defined in Claim 9, wherein said skirt is substantially circumferentially
continuous.
13. The tappet defined in Claim 9, wherein said skirt has at least one circumferential
discontinuation (132).
14. The tappet defined in Claim 9, wherein said skirt defines retention surfaces operative
to react against the material of said body means thereadjacent for preventing relative
movement therebetween.
15. The tappet defined in Claim 14, wherein said retention surfaces comprise generally
radially extending throughpassages (62).
16. The teppet of Claim 9, wherein said face portion is substantially co-extensive
with the nominal cross-sectional area of the outer annular wall.
17. A hydraulic lash adjusting tappet for use in the valve gear of an internal combustion
engine, said tappet comprising:
(a) body means including structure defining,
(i) an outer annular wall having a wear-resistant surface on the outer periphery thereof,
(ii) an annular hub disposed within said outer wall and spaced therefrom, said hub
including an inner surface defining a bore, (iii) an end wall attached respectively
to and extending transversely across one axial end of said hub, and
(iv) web structure extending inwardly from said outer annular wall and supporting
said hub, wherein said body means is formed of material having a coefficient of thermal
expansion not substantially less than 22.0 x 10-6 per unit length per °C as measured in the range 10-100°C;
(b) a face member defining a reaction surface adapted to contact an engine cam, said
face member further defining generally axially extending flange means circumscribing
at least a portion of said surface and moldingly entrained within said body means
radially outwardly of and encompassing said bore, said face member formed of material
having a surface hardness value of at least 89 as measured on the Rockwell 15N scale
for the reaction surface;
(c) hydraulic lash adjusting means movably received in said bore, said lash adjusting
means including structure defining a reaction surface adapted for contacting associated
valve gear components, said reaction surface extending generally parallel to said
face member reaction surface and movable with respect thereto, said lash adjusting
means including means defining a fluid pressure chamber (98) and plunger means including
piston structure (72) cooperating with said end wall to form a first fluid portion
(74) of a fluid reservoir, and said plunger means including plunger structure (68)
cooperating with portions of said hub to form a second portion (86) of said fluid
reservoir, and one-way valve means (78, 80) operable to admit fluid to said chamber
for altering the position of said reaction surface with respect to said face member
reaction surface, said lash adjusting means further including means (96) biasing said
reaction surface away from said face member reaction surface, said body means including
structure defining at least one bypass channel (88) operable to communicate said first
reservoir portion with said second reservoir portion for all positions of said piston
structure and said plunger structure in said hub;
(d) said body means including structure defining a fluid passage (90) through said
annular wall from said wear resistant surface to said second reservoir portion for
communicating fluid to said one-way valve means upon installation of said tappet in
an engine and supplying pressurized fluid to said passage; and
(e) means (100) retaining said lash adjusting means in said hub.
18. The tappet defined in Claim 17, wherein said fluid passage defining structure
includes a radial web extending between said outer tubular wall and said hub.
19. The tappet defined in Claim 17, wherein said body means structure is formed of
material having a bulk density less than 2.85 grams per cm3.
20. The tappet defined in Claim 17, wherein said face member is formed of steel and
said body means, outer wall, hub and web are formed of substantially plastic or aluminum
material.
21. A hydraulic lash adjusting tappet for use in the valve gear of an internal combustion
engine, said tappet comprising:
body means formed of material having a coefficient of thermal expansion not substantially
less than 22 x 10 6 per unit length per °C as measured in the range 20-100°C;
a generally cup-shaped insert member defining a reaction surface adapted for contacting
a cam lobe, said insert member further defining at least one recess for receiving
body material therein to join said body means and said insert; and
hydraulic lash adjusting means operatively associated with said body means and including
structure defining a reaction surface adapted for contacting associated components
of the engine valve gear, said reaction surface movable with respect to said face
member reaction surface for lash adjustment of said valve gear.