U.S. patent number 3,888,216 [Application Number 05/402,917] was granted by the patent office on 1975-06-10 for system for the control of the intake and exhaust valves of internal combustion engines.
This patent grant is currently assigned to Regie Nationale des Usines Renault, Societe dite: Automobiles Peugot. Invention is credited to Stevan Miokovic.
United States Patent |
3,888,216 |
Miokovic |
June 10, 1975 |
System for the control of the intake and exhaust valves of internal
combustion engines
Abstract
A system for the control of the intake and exhaust valves of
internal combustion engines which permits the automatic variation
in the valve overlap and the respective open angles during engine
operation, is characterized by having two camshafts, one of which
serves to open a valve while the other of which serves to close the
valve, each shaft having mutually adjustable timing angles, and the
rocker arms each have two cam followers one of which contacts a
first cam upon one shaft and the other of which similarly contacts
a cam upon the other shaft.
Inventors: |
Miokovic; Stevan (Paris,
FR) |
Assignee: |
Regie Nationale des Usines
Renault (FR)
Societe dite: Automobiles Peugot (FR)
|
Family
ID: |
9108083 |
Appl.
No.: |
05/402,917 |
Filed: |
October 2, 1973 |
Foreign Application Priority Data
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Dec 1, 1972 [FR] |
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72.42860 |
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Current U.S.
Class: |
123/90.15;
123/90.17; 123/90.27; 123/90.25 |
Current CPC
Class: |
F01L
1/30 (20130101); F01L 1/08 (20130101) |
Current International
Class: |
F01L
1/30 (20060101); F01L 1/00 (20060101); F01l
001/34 () |
Field of
Search: |
;123/90.15,90.17,90.16,90.22,90.24,90.25,90.26,90.27,90.44 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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818,531 |
|
Aug 1959 |
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GB |
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343,688 |
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Feb 1931 |
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GB |
|
Primary Examiner: Antonakas; Manuel A.
Assistant Examiner: O'Connor; Daniel J.
Attorney, Agent or Firm: Oblon, Fisher, Spivak, McClelland
& Maier
Claims
What is claimed as new and desired to be secured by Letters Patent
of the United States is:
1. A system for the control of the intake and exhaust valves of
internal combustion engines which permits the automatic variation,
during engine operation, of valve overlap and the respective open
angles thereof comprising, in conjunction with engine intake and
exhaust valves:
two camshaft means for respectively lifting and closing said engine
intake and exhaust vauves;
said camshafts having mutually adjustable timing means for
adjusting the timing angles of said valves; and
a pair of rocker arms operated by said camshafts, and each of said
rocker arms having two cam follower means thereon for respectively
contacting cam means upon each of said camshafts.
2. A system as set forth in claim 1, wherein said means for
adjusting the timing of said valves during engine operation
comprises:
two bushings intermeshed with one another and within which said
camshafts respectively rotate;
the end portions of said bushings defining diametrically opposed
tongue members;
gear means disposed upon said tongue members for longitudinal
movement thereto;
sprial fin means disposed upon said camshafts for interengaging
recess means within said gear means; and
hydraulic actuator means for moving said gear means relative to
said tongue members.
3. A system as set forth in claim 1, wherein:
said cam means have arcuate crest portions, the center of which
lies upon the axes of said cam means,
whereby shocks are prevented from occurring during passage of said
rocker arms from said lifiting cam to said closing cam.
4. A system as set forth in claim 1, wherein:
said lifting cam has prolonged descending slope configuration which
is compatible with the slope of said closing cam,
whereby at the points of intersection of said two cams no abrupt
changes in movement occur so as to thereby maintain accelerations
within acceptable limits and to prevent the occurrence of any
shocks during passage of said rocker arms from said lifting cam to
said closing cam.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to the intake and exhaust
systems of internal combustion engines and more particularly to an
arrangement for the control of the intake and exhaust valves so as
to permit the automatic variation, during engine operation, of the
valve overlap, the angles at which the valves open, and the cyclic
periods throughout which the valves remain open.
2. Description of the Prior Art
As is well-known, in internal combustion engines the durations of
the intake and exhaust periods, which normally should be limited to
the time necessary for the piston to traverse the corresponding
strokes, are regularly prolonged so that each valve opens before
the piston reaches dead-center and closes after the piston reaches
the next dead-center. This prolongation of the intake and exhaust
phases is required for several reasons, such as for example,
compensation for the losses and recharging of the cylinders due to
the passage of the gases around the valves, or the reduction in
atmospheric pollution by decreasing the proportion of unburned
gas.
Thus, in order to maximize motor efficiency at all speeds and loads
it is necessary to vary the intake and exhaust periods which are of
course longer, with large advance periods and delay times in valve
opening and closing, respectively, for higher engine speeds.
Arrangements have in fact already been proposed for varying the
advance periods and delay times in the intake and exhaust phases in
internal combustion engines as a function of motor speed and
load.
One known mechanism provides for the control of the intake and
exhaust valves of the internal combustion engine through means of a
rotating control shaft which includes means for converting the
rotary motion of the control shaft into an oscillatory motion of a
cam whose profile includes a lobe disposed upon a circular base, as
well as means for varying the width of the cam lobe so as to
control the valves as a function of motor speed and load.
Another known timing mechanism for an automobile internal
combustion engine, each cylinder of which has intake and exhaust
valves actuated by means of a cam shaft which is driven by means of
the motor crankshaft, includes a system wherein the camshaft is
able to slide within its bearings, integral with the block
whereupon the camshaft includes a pair of axially separated cam
lobes for actuation of the respective rocker arms of each of the
exhaust valves, one lobe being wider than the other, and also
includes a piston disposed at one end thereof which tends to be
reciprocated within a cylinder integral with the block in one
direction by means of a return spring compressed against the
camshaft bearing, the piston being actuated in the other direction
through means of the admission of fluid, at variable pressure, into
the cylinders so as to bring one or the other cam lobe into contact
with the respective rocker arm according to engine speed.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to provide a
mechanism for the control of the intake and exhaust valves of an
internal combustion engine which permits the continuous and
automatic variation during engine operation, of the overlap and
cyclic periods of the valves as a function of engine speed and
load.
The foregoing and other objects are achieved accoording to the
present invention through the provision of two camshafts, one of
which is utilized to raise the valve while the other is utilized to
close the valve and which have mutually adjustable timing cycles, a
pair of rocker arms, each of which have two cam followers for
respectively contacting a cam upon one of the camshafts and a cam
upon the other of the camshafts, and means to vary the mutal timing
cycle of the camshafts.
BRIEF DESCRIPTION OF THE DRAWINGS
Various other objects, features, and attendant advantages of the
present invention will be more fully appreciated as the same
becomes better understood from the following detailed description
when considered in connection with the accompanying drawings, in
which like reference characters designate like or corresponding
parts throughout the several views, and wherein:
FIG. 1 is an end view, partly in section, of a valve assembly
constructed according to the present invention and its cooperative
parts, including the two camshafts, the rocker arms having two cam
followers and the drive shaft, the control mechanism having been
removed;
FIG. 2 is a partial plan view of the assembly shown in FIG. 1;
FIG. 3 is an end view of the control mechanism of the present
invention;
FIG. 4 is a plan view of the control mechanism shown in FIG. 3;
FIG. 5 is a longitudinal cross-section view taken along a central
vertical plane through the control assembly shown in FIG. 4;
FIG. 6 is a cross-section view of the control mechanism taken along
line A-A of FIG. 5;
FIG. 7 is a view of the drive mechanism taken along the line F of
FIG. 5;
FIG. 8 and 9 are schematic views showing the profiles of the cams
for opening and closing the valves and showing the minimum and
maximum angular configurations utilized for which the valves can
open;
FIG. 10 is a graph showing the angles at which the valves can open
as a function of the relative positions of the two cams; and
FIG. 11 is a view similar to that of FIG. 1, showing however
another embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, and more particularly to FIG. 1
thereof, there is shown a rocker arm casing 18 within which are
disposed two sets of rocker arms 19 and 20 which are engaged with
the intake and exhaust valves 21 and 22. The rocker arms 19 and 20
may oscillate about the respective shafts 23 and 24, and also
include a pair of cam followers 19' and 19", and 20' and 20",
respectively, cam follower 19' of rocker arm 19 being in contact
with an upper cam shaft 4, while the other follower 19" is in
contact with a lower camshaft 5. Similarly, the cam follower 20' of
rocker arm 20 is also in contact with camshaft 4 while follower 20"
is in contact with camshaft 5. Camshafts 4 and 5 rotate in opposite
directions and are driven by means of engine drive shaft 1, through
appropriate gearing, which is of course driven by means of the
automobile internal combustion engine, although it should be noted
that shaft 1 is not indispensable since the camshafts can be driven
directly by means of the engine. However,, as depicted, the use of
shaft 1 permits minimum modification of existing engines.
Referring now to FIGS. 5, 6 and 7, the drive shaft 1 which is
driven by means of the engine, transmits the rotary motion to
gear-type bushings 2 and 3 which are intermeshed with one another.
Bushings 2 and 3 rotate within bearings 6' and 7' and serve to
support the end bearings 6 and 7 of camshafts 4 and 5 which of
course permit rotation of the shafts within the bushings. The right
end portions of the bushings 2 and 3, as seen in FIG. 5, include
partially cut portions which define diametrically opposed tongues 8
and 9. Upon these tongues are mounted annular gears 10 and 11
which, by means of keyways, are permitted to slide therealong and
relative thereto but will be caused to rotate therewith, the
sliding gears also engaging the camshafts 4 and 5 which are
furnished with spiral fins 12. When the sliding gears 10 and 11,
which are driven by means of the vehicle engine, are shifted along
the tongues 8 and 9 of bushings 2 and 3 so as to mesh with the
camshafts, the latter are rotated in opposite directions, and
consequently, the timing of the valves with respect to the
particular times at which the valves open as well as the duration
of the valve overlap may be varied.
The control mechanism will now be described with particular
reference being made to FIGS. 3, 4 and 5. Drive shaft 1 has
associated therewith a centrifugal regulator, now shown, and as the
engine speed changes, the regulator by means of rod 13, moves spool
valve 14 so as to direct oil into a piston-type actuator 15 in
accordance with the engine oil pressure. The actuator 15 is
provided with a fork 16 which serves to move the sliding gears 10
and 11 by means of an actuating plate 17 which is secured between
flanged members, not numbered, of gears 10 and 11.
As noted heretofore, rocker arms 19 and 20 each have two cam
followers for respectively contacting the lifting or opening
camshaft and the lowering or closing camshaft. The camshafts rotate
in opposite directions, the lower shaft 5 rotating in a clockwise
direction, while the upper camshaft rotates in a counterclockwise
direction. As seen in FIG. 1, before rocker arm 19 loses contact
with the lifting cam upon lower shaft 5, it is affected by means of
the closing cam upon shaft 4, which will then be at a position
noted by the phantom lines.
According to one feature of the present invention, in order to
prevent the occurrence of any shocks when the rocker arm cam
followers shift contact from the lifting cam to the closing cam,
the crests of the cams may have the form of a circular arc the
center of which lies upon the cam axis. FIGS. 8 and 9 show the cams
having profiles exhibiting the minimum and maximum angular
configurations for opening the valves, it being noted that for ease
of comprehension the two cams are shown as being superimposed.
It should be noted further in conjunction with the desire to
prevent the occurrence of shocks when the cam followers are
transferred from one cam to another, that the configurations of the
lifting and closing cams may be such that the descending slope of
the lifting cam is prolonged so as to intersect that of the closing
cam. The intersection is such that passage from one slope to that
of the other does not produce abrupt changes in motion, whereby the
attendant accelerations remain within acceptable limits. The
lifting function of the valves, that is, the angles at which the
valve can open, which is dependent upon the relative positions of
the cams as well as the profile configurations thereof, is shown in
FIG. 10, curve 40 illustrating the descending curve for the lifting
cam while curves 41, 42 and 43 illustrate the descending curves for
the closing cam when disposed at three different angular positions.
Curve 41 gives the maximum open angle which is derived from the
descending curves of the two cams which intersect at point 44,
while point 45 illustrates the maximum open angle which is derived
from the descending curves of the two cams which intersect when the
closing cam is disposed at a position representative of curve 42.
When the closing cam is disposed at a position represented by curve
43, valve closure is accomplished entirely upon the descending
slope of the closing cam.
Referring now to FIG. 11, another embodiment of the present
invention may be used in which only the overlap of the intake and
exhaust valves, and not their open angles, is made to vary
automatically. Two camshafts 25 and 26, which are respectively
provided for initiating intake and exhaust, are driven by means of
the engine drive shaft 27. The rocker arms 28 and 29 for intake and
exhaust, respectively, each have a single cam follower in contact
with their respective cams, and the angular displacement of one
camshaft with respect to the other shaft, which thereby varies the
valve overlap, is done automatically by means of a mechanism
similar to that discussed heretofore in connection with the
embodiment of FIG. 1.
Obviously, many variations and modifications of the present
invention are possible in light of the above teachings. It is to be
understood therefore that within the scope of the appended claims,
the invention may be practiced otherwise than as specifically
described herein.
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