U.S. patent number 3,895,614 [Application Number 05/421,334] was granted by the patent office on 1975-07-22 for split piston two-stroke four cycle internal combustion engine.
Invention is credited to Henry E. Bailey.
United States Patent |
3,895,614 |
Bailey |
July 22, 1975 |
Split piston two-stroke four cycle internal combustion engine
Abstract
A two-stroke, four-cycle internal combustion engine is provided
with a split piston which reciprocates within a cylinder having
primary and secondary pre-combustion chambers. The lower portion of
the piston is split by means of a partition which divides the
cylinder into opposed air and combustible charge pumping chambers.
One-way flow valves are provided to control the flow of air and a
combustible charge into respective pumping chambers as the piston
moves along its compression stroke. Movement of the piston along
its power stroke compresses volumes of air and the charge within
the pumping chambers, with these volumes then being directed
through ports formed in a piston skirt and the cylinder wall into
the pre-combustion chambers through one-way flow valves. Exhaust
gases are scavenged through exhaust ports in the cylinder wall
which are exposed as the piston completes its power stroke, with
scavenging being assisted by injection of air directed from the
pumping chamber through a one-way flow valve in a mid-portion of
the cylinder wall. Certain of the one-way flow valves are
threadably mounted for axial adjusting movement to vary valve lift
and to facilitate valve replacement. The partition is formed
integral with the piston and slidably projects through the end wall
of the cylinder which forms the pumping chambers. Reciprocating
movement of the piston and partition is converted into rotary
motion through a cam follower mounted on the plate and moving in
the cam track of a cylindrical cam.
Inventors: |
Bailey; Henry E. (Walnut Creek,
CA) |
Family
ID: |
23670083 |
Appl.
No.: |
05/421,334 |
Filed: |
December 3, 1973 |
Current U.S.
Class: |
123/67; 123/73CC;
123/74A; 123/74R; 123/56.7 |
Current CPC
Class: |
F02B
19/12 (20130101); F01B 3/04 (20130101); F02B
41/04 (20130101); F02B 33/12 (20130101); F02B
2075/025 (20130101); F02B 1/04 (20130101); F02B
2075/027 (20130101); Y02T 10/12 (20130101) |
Current International
Class: |
F01B
3/00 (20060101); F01B 3/04 (20060101); F02B
41/00 (20060101); F02B 33/12 (20060101); F02B
33/02 (20060101); F02B 41/04 (20060101); F02B
19/12 (20060101); F02B 19/00 (20060101); F02B
1/00 (20060101); F02B 75/02 (20060101); F02B
1/04 (20060101); F02b 033/44 (); F02b 033/12 () |
Field of
Search: |
;123/74AC,74B,74AP,67,69V,73CC,73EB,58A,58AA,197AB,74AA,74A,74R |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Rutledge, Jr.; W.
Attorney, Agent or Firm: Flehr, Hohbach, Test, Albritton
& Herbert
Claims
I claim:
1. In a two-stroke, four cycle internal combustion engine, the
combination of means forming at least one cylinder having opposed
first and second end walls, a piston mounted for reciprocating
movement through power and compression strokes within the cylinder,
one end of the piston separating the cylinder and cooperating with
said first end wall to define a combustion chamber, the other end
of the piston having a partition extending transversely across the
cylinder and cooperating with said second end wall to define an air
pumping chamber and an opposed combustible charge pumping chamber,
first means to direct volumes of air and a combustible charge into
respective air and charge pumping chambers during movement of the
piston along its intake compression stroke, said volumes being
compressed in respective chambers during movement of the piston
along its power stroke, second means to direct the volume of
compressed air from the air pumping chamber into the combustion
chamber, third means to direct the volume of compressed charge from
the charge pumping chamber into the combustion chamber, fourth
means to ignite the charge in the combustion chamber which is
compressed by movement of the piston along its compression stroke,
and exhaust means to exhaust the products of combustion from the
combustion chamber.
2. An engine as in claim 1 which includes means forming a primary
pre-combustion chamber communicating both with said third means and
said first mentioned combustion chamber, means forming a secondary
pre-combustion chamber communicated both with said second means,
with said first mentioned combustion chamber and with said primary
pre-combustion chamber.
3. An engine as in claim 1 in which said second means includes air
injection valve means for injecting air which is compressed in the
air pumping chamber into the combustion chamber for scavaging
products of combustion through the exhaust means.
4. An engine as in claim 1 in which the third and second means
include respective ports formed at a mid-portion of the cylinder,
the piston includes a cylindrical skirt adapted to occlude said
ports while the piston is moving through its compression stroke and
is compressing the air and combustible charge within respective
pumping chambers, and the skirt is formed with ports communicating
with respective pumping chambers and positioned to move into
register with said first mentioned ports when the piston
substantially reaches the end of its power stroke.
5. An engine as in claim 1 in which the partition comprises a flat
plate mounted for close-spaced sliding movement through the second
end wall of the cylinder, and means forming a seal between said
cylinder and the facing surfaces of the plate.
6. An engine as in claim 5 which includes means for converting
reciprocating movement of said piston and plate into rotary motion
comprising a cylindrical cam mounted for rotation about a
longitudinal axis parallel with the longitudinal axis of the
cylinder, means forming a curvilinear cam track about the periphery
of said cylindrical cam, and cam follower means carried by said
plate and mounted for movement in said cam track whereby
reciprocating movement of said plate causes the cam follower to
react against and rotate the cam about its longitudinal axis.
7. An engine as in claim 1 in which said first means includes valve
means for controlling one-way flow into respective air and
combustible charge pumping chambers comprising a valve body having
a valve seat, and a valve element having an integral plunger
slidably mounted in said body for moving the valve element to and
from the seat responsive to a pressure differential on opposite
sides of the valve element.
8. An engine as in claim 1 in which said second and third means
includes valve means for controlling one-way flow into the
combustion chamber comprising a fixed valve stop, a valve body
threadably mounted for axial adjustable positioning with respect to
the valve stop, the valve body including a valve seat, a valve
element including a plunger slidably mounted in the valve body for
guiding the valve element between the seat and valve stop
responsive to a pressure differential on opposite sides of the
valve element.
9. An engine as in claim 3 in which the air injection valve means
includes valve means for controlling one-way flow into the
combustion chamber comprising a fixed valve stop, a valve body
threadably mounted for axial adjustable positioning with respect to
the valve stop, the valve body including a valve seat, a valve
element including a plunger slidably mounted in the valve body for
guiding the valve element between the seat and valve stop
responsive to a pressure differential on opposite sides of the
valve element
10. An engine as in claim 1 which includes a drive member, formed
as an extension of said partition, mounted for reciprocating
movement with the piston and projecting in slidable sealing
relationship with the second end wall of the cylinder, a casing
mounted with said cylinder and enclosing the portion of the drive
member which projects from the second end wall, and means to direct
blow-by gases from within the casing to said first means for
injection into said air pumping chamber.
Description
BACKGROUND OF THE INVENTION
This invention relates to two-stroke, four-cycle internal
combustion engines.
Two-stroke, four-cycle internal combustion engines have heretofore
been utilized in applications requiring simplicity, low cost and a
relatively high horsepower-to-weight ratio, such as engines for
motorcycles, outboard motors, small utility motors and the like. It
is conventional in engines of this type to mix oil with the
gasoline fuel, and part of the oil is burned during the power
stroke to form harmful exhaust emissions. Moreover, such engines
function by directing the air-fuel mixture through an intake port
while spent gases exhaust through an opposite side of the cylinder,
with the result that some of the mixture is carried out with the
exhaust products. This loss, together with the relatively rich
mixtures required for smooth operation and good response in such
engines, results in a relatively high hydrocarbon and carbon
monoxide content in the exhaust gases, as well as a relatively high
fuel cost in relation to power output.
Conventional four-stroke, four-cycle combustion engines, on the
other hand, develope practically twice the power of a two-stroke
engine with equivalent bore and piston speeds, and also do not
require a separate crankcase for each cylinder. The four-stroke
engine is also more flexible, and is better adapted to the use of a
carburetted mixture. However, such an engine provides only one
power stroke for each cylinder in two revolutions of the crankshaft
and, as with the two-stroke engine, does not develope complete
expansion within the combustion chamber.
Recent Federal and State legislation has been enacted to require
manufacturers of mobile equipment powered by gasoline fuel internal
combustion engines to reduce harmful exhaust emissions by means of
external emissions control devices, engine modifications or other
methods. However, these objectives have heretofore not been fully
realized.
OBJECTS AND SUMMARY OF THE INVENTION
It is a general object of the invention to provide an improved
two-stroke internal combustion engine which will operate with
reduced amounts of harmful exhaust emissions.
Another object is to provide an engine of the type described which
will operate with more efficient fuel utilization.
Another object is to provide an engine of the type described which
will achieve a relatively higher horsepower-to-weight ratio.
Another object is to provide an engine of the type described which
can be employed in a wide range of power applications such as small
utility engines, motorcycles, automobiles and multi-cylinder
airplane engines.
The invention provides a two-stroke, four-cycle internal combustion
engine having a piston mounted for reciprocating movement through
power and compression strokes within a cylinder. One end of the
piston is formed with a transversely extending partition or plate
which separates an end of the cylinder into an air pumping chamber
and an opposed combustible charge pumping chamber. The other end of
the cylinder is formed with interconnected primary and secondary
pre-combustion chambers, both of which communicate with the main
combustion chamber in the cylinder. One-way flow control valves are
provided to direct air and a combustible charge into respective air
and charge pumping chambers as the piston moves through its
compression stroke. Return of the piston on its power stroke
compresses the volumes of air and combustible charge contained
within the pumping chambers and these volumes are then directed to
the pre-combustion chambers as ports in the piston skirt register
with ports formed in the cylinder wall. An air injection valve is
formed in the cylinder wall to direct air into the cylinder for
scavenging products of combustion through exhaust ports, and to
form a stratified charge in the combustion chamber, as the piston
moves toward the end of its power stroke. One-way flow valves are
provided to control flow into the pre-combustion chambers. The
one-way flow valves include a valve element and plunger slidable
within a valve body for movement to and from a valve seat.
Reciprocating motion of the piston and its partition is converted
to rotary motion by means of a cam follower mounted at the end of
the partition in rolling contact with a cam track formed about the
periphery of a cylindrical cam.
The foregoing and additional objects and features of the invention
will appear from the following description in which the preferred
embodiment has been set forth in detail in conjunction with the
accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is an axial sectional view of an internal combustion engine
embodying the invention;
FIG. 2 is a cross-sectional view taken along the line 2--2 of FIG.
1;
FIG. 3 is a cross-sectional view taken along the line 3--3 of FIG.
1;
FIG. 4 is a side elevational view of a flow control valve utilized
in the engine of FIG. 1; and
FIG. 5 is an axial sectional view taken along the line 5--5 of FIG.
4.
DESCRIPTION OF THE PREFERRED EMBODIMENT
In the drawings FIG. 1 illustrates generally at 10 a two-stroke,
four-cycle internal combustion engine constructed in accordance
with the invention. Engine 10 includes a pair of cylinders 11, 12
mounted together above a common casing 13. While a two-cylinder
engine is shown, it is understood that the invention is adaptable
for use as a single-cylinder engine, or as an engine utilizing more
than two cylinders.
The construction and operation of the two cylinders is
substantially identical and thus it will suffice to describe in
detail that for cylinder 11. A cylinder block 14 is mounted above
casing 13 and defines a circular cylinder wall 16. The cylinder
wall may be cooled by suitable means such as by circulation of a
liquid coolant in jacket 15, FIG. 3, which encloses the cylinder.
The cylinder head is formed with a primary precombustion chamber 17
and a secondary pre-combustion chamber 18. The two pre-combustion
chambers are in fluid communication by means of a by-pass port 19.
The two chambers are also in communication with the main combustion
chamber 21 of cylinder 11 by means of ports 22, 23. Suitable
combustible charge ignition means such as the illustrated spark
plug 24 is provided in pre-combustion chamber 17, and the spark
plug is energized through a suitable electrical ignition system,
not shown.
A piston 26 is mounted for reciprocating movement through power and
compression strokes within cylinder wall 16. A flat piston plate or
partition 27 is integrally formed below piston 26 and extends
transversely across the cylinder to separate the lower portion of
the cylinder into air pumping chamber 28 and an opposed combustible
charge pumping chamber 29. The piston plate slidably projects
through an opening 31 formed in cylinder end wall 32. Suitable
sealing elements 33 are mounted on opposite sides of opening 31 to
provide a fluid-tight seal between the piston plate and cylinder
end wall.
Reciprocating motion of the piston is converted into rotary motion
by means of a cam follower 34 rotatably carried at the lower end of
the piston plate and mounted for rolling contact within a cam track
36 formed about the outer periphery of a cylindrical cam 37. The
cylindrical cam is mounted on bearings 38, 39 within casing 13 for
rotation about an axis extending parallel with and between the
longitudinal axes of the cylinders 11, 12. A power shaft 41 is
connected with the cam and extends upwardly between the two
cylinders where it is supported on a bearing 42. The power shaft in
turn is connected with a suitable drive train such as a clutch,
transmission and road wheels or gear train, not shown. The
cylindrical cam itself acts as a flywheel so that a separate
flywheel is not required on the power shaft.
Cam track 36 is formed about the surface of the cam in a curve
which has an amplitude equal to the stroke of the two pistons. Each
of the cam followers for the two pistons are mounted in the same
cam track. The cam followers comprise truncated cones, and the side
walls of the cam track conform with the inclination of the cam
followers. Adequate clearance is provided between the side walls of
the track and the cam followers to permit rolling contact along the
track.
Where three or more cylinders are provided in an engine of the type
described, the diameter of the cam is enlarged with the cylinders
equally spaced about the axis of the cam and with all of the cam
followers engaging in the same cam track. In such a case the cam
track can be configured to provide one or more power strokes of
each cylinder per revolution of the cam. This permits a relatively
larger horsepower-to-weight ratio for the engine. In addition, the
curvature of the cam track can be designed to provide a variation
in piston speed for different sectors of cam rotation. Thus, the
cam track curve could provide for faster piston speed during the
power stroke as compared to the piston speed during the induction
stroke. Also, the cam track curve could provide for relatively
faster piston speed during the first portion of the power stroke
and slower speed through the end of that stroke to afford
additional time for exhaust scavenging.
A combustible charge such as an air-fuel carburetted charge is
induced into the cylinders from an intake manifold 45, FIG. 2,
through inlet passages 43, 44. A one-way flow valve 46 directs flow
from passage 43 into the lower portion of charge pumping chamber
29. A port 47 is formed in the mid-portion of cylinder wall 16 to
direct a compressed volume of the charge from the pumping chamber
through a passage 48 to a one-way flow valve 49 which in turn
directs the charge into pre-combustion chamber 17. Piston 26 is
formed with an integral downwardly extending annular piston skirt
51 fitted for sliding movement within the inner surface of the
cylinder wall. A piston port 52 is formed in the upper portion of
the piston skirt at a position such that the piston port moves into
register with outlet port 47 as the piston approaches the end of
its power stroke so that the compressed charge can be released into
passage 48.
Atmospheric air is inducted into the cylinders of the engine
through a one-way flow valve 53 which directs the air into charge
pumping chamber 28. An outlet port 54 is formed at a midportion of
cylinder wall 16 to direct the compressed volume of air from the
pumping chamber into a passage 56 leading upwardly to a one-way
flow valve 57 which directs the air into secondary precombustion
chamber 18. A piston port 58 is formed in the upper portion of
piston skirt 51 at a position such that it moves into register with
outlet port 54 as the piston reaches the end of its power stroke to
release the compressed air from the pumping chamber into passage
56.
A plurality of exhaust ports 59, 60 are formed through cylinder
wall 16 at a position such that the exhaust ports are uncovered by
the piston as it reaches the end of its power stroke. The exhaust
ports are connected to a suitable exhaust manifold 61, as shown in
FIG. 3. Exhaust scavenging is greatly enhanced in the invention by
the injection of air through a one-way flow valve 62 at the
completion of the power stroke. Valve 62 is mounted in the cylinder
wall at a position above the piston head when the latter is at the
end of its power stroke. Valve 62 communicates with passage 56 and
opens responsive to a differential pressure as a result of
reduction in combustion chamber pressure as the exhaust ports are
uncovered.
The one-way flow valves 46, 53 controlling flow into the pumping
chambers 28, 29 preferably comprise pressure responsive valves
which include a valve element 63 and integral plunger or stem 64
mounted for axial sliding movement within a valve body 66. The
valve element moves to and from a valve seat 67 responsive to
differential pressure across the valve element due to variation in
pressures within the pumping chamber. Thus, valve 53 is closed due
to the increasing pressure in pumping chamber 28 as the piston
moves downwardly along its power stroke. After the volume of air
within the pumping chamber has been released through ports 58 and
54 upward movement of the piston along its compression stroke
reduces pumping chamber pressure to a level at which the greater
atmospheric pressure opens valve element 63 for inducting
additional air. The operation of one-way valve 46 is similar to
that described for valve 53.
Blow-by gases which enter the interior of casing 13 from the
cylinders 11, 12 are removed by means of a passage 65 formed in
cylinder block 14 and providing communication between the casing
and flow valve 53. Induction of air through this valve draws
blow-by gases from the passage 65 into air pumping chamber 28 for
recycling in the engine.
The air injection valve 62 and one-way flow valve 49, 57 in the
cylinder head preferably comprise pressure operated valves
assembled in relatively small cartridges which afford simplified
valve lift adjustment and which also can be readily inserted and
removed for replacement purposes. FIGS. 4 and 5 illustrate details
of a valve cartridge assembly for the typical valve 62, and it is
understood that the construction and operation of the valves 49, 57
is similar thereto. The valve 62 comprises a valve body 68 formed
with external threads adapted for engagement with internal threads
formed in a bore through the walls of the passage 56 and cylinder
wall 16. The end of the body 68 forms a valve seat 69 which
communicates through passages 71 with a plurality of openings 72
which are formed in the body side walls. A valve element 73
comprising a circular valve head 74 and integral plunger 76 is
mounted for axial sliding movement within a central bore in the
body. A differential gas pressure across the valve head moves the
same between the valve seat and a fixed stop 79 which is recessed
in the cylinder wall. The position of the valve cartridge may be
axially adjusted with respect to the fixed stop by turning the
valve body within the threaded bore. This in turn varies the amount
of valve lift, i.e. the clearance between the valve head and seat
when the valve is in its fully open position. This permits
selective variation of the flow rate of scavenging air which is
injected through valve 62. Similar fixed stops 78, 79 are mounted
within the pre-combustion chambers adjacent valves 49, 57 for
selective variation of charge and air flow rates into these
chambers by turning the respective valve bodies.
This use and operation of engine 10 will be explained assuming that
a carburetor, not shown, is provided to supply an air-fuel charge
through manifold 45 into the passages 43, 44 for the two cylinders.
With power shaft 41 initially turned by a suitable starter motor,
not shown, the pistons are reciprocated through action of the
cylindrical cam 37 and cam followers. Movement of piston 26
upwardly along its compression stroke within cylinder 11 causes a
pressure reduction within the two pumping chambers 28, 29. The
resulting pressure differential across the flow valves 46, 53
causes these valves to open to induct atmospheric air and the
combustible charge into respective air and charge pumping chambers.
This phase continues until the piston reaches the top of its
compression stroke, as illustrated for the right-hand cylinder 81
in FIG. 1. As piston 26 then moves downwardly along its power
stroke the volumes of gas within the two pumping chambers are
compressed so that the higher internal pressure closes flow valves
46, 53. Compression of the two volumes within the pumping chambers
continues until the piston ports 52, 58 move into register with
respective outlet ports 47, 54 as the piston reaches the end of its
power stroke. The compressed combustible charge is then exhausted
from pumping chamber 29 into passage 48 where it travels upwardly
to act against and open the valve element of flow valve 49. The
relatively rich charge mixture then flows into primary
pre-combustion chamber 17. A portion of this flow is directed
through by-pass port 19 and into secondary pre-combustion chamber
18.
The volume of air which is compressed within pumping chamber 28 is
also exhausted into outlet port 54 and passage 56 from piston port
58. The pressure of this air acts against and opens the valve
element of flow valve 62 to inject a portion of the flow into
combustion chamber 21 for scavenging exhaust gases and form a
stratified layer, while the remaining portion flows upwardly to act
against and open the valve element of flow valve 57. This air flows
into secondary pre-combustion chamber 18 where it mixes with the
portion of the charge entering from port 19 to form a relatively
lean fuel-air mixture.
As piston 26 then moves upwardly on its compression stroke a
stratified charge is formed within cylinder 21 comprising the lower
layer of fresh air introduced from injection valve 62 together with
residual products of combustion which have not been exhausted, and
an upper layer comprising the rich fuel-air mixture of chamber 17
and the relatively leaner mixture of chamber 18. Continued movement
of the piston toward the top of this stroke compresses the gases
within main combustion chamber 21 and the pre-combustion chambers.
The ignition system, operating in timed relationship with rotation
of power shaft 41, then energizes spark plug 24 to ignite the
compressed charge within the primary pre-combustion chamber. The
flame front propagates across this chamber and through by-pass port
19 to ignite the lean mixture within secondary chamber 18. The
flames from the two pre-combustion chambers emerge through ports
22, 23 and continue burning with the rich source of oxygen supplied
from the lower portion of the stratified charge. The rapidly
burning and expanding gases within the main combustion chamber
drive the piston downwardly through its power stroke, and this in
turn drives power shaft 41 through rolling contact between cam
follower 34 and cam 37.
As piston 26 nears the end of its power stroke the exhaust ports
59, 60 are uncovered for exhausting the products of combustion from
the combustion chamber. Air injection valve 62 opens in the manner
explained above, and the current of air which is injected from this
valve both scavenges exhaust gases out through the exhaust ports
and also acts as a shield between the exhaust ports and the
combustible charge entering the chamber through ports 22, 23. At
the same time the gases within the air and charge pumping chambers
are released into the passages 48 and 56 for the next cycle of
operation.
From the foregoing it is apparent that there has been provided
herein a new and improved two-stroke, four-cycle internal
combustion engine. The split piston arrangement provides a novel
air and combustible charge pumping mechanism for injecting air for
exhaust scavenging and to form a stratified charge within the
combustion chamber. The two pre-combustion chambers provide for
burning separate volumes of rich and lean mixtures which may be
controlled by simple adjustment of the one-way flow valves. The
cycle of operation closely approaches complete expansion of the
burning charge. The rich fuel mixture burns relatively fast and at
a high temperature, but the mixture is low in oxygen so that
formation of NO.sub.x products is minimal. The lean mixture burns
relatively slower and at a lower temperature, and when the flame
fronts emerge from the pre-combustion chambers into the main
combustion chamber the gases burn slower at a relatively high
temperature because of the presence of residual products of
combustion from the previous cycle. As the exhaust ports are
exposed by movement of the pistons the products of combustion are
subjected to a cooling flow of the injected air which oxidizes any
remaining hyrocarbons and carbon monoxide into water and harmless
carbon dioxide.
While the foregoing embodiments are at present considered to be
preferred it is understood that numerous variations and
modifications may be made therein by those skilled in the art and
it is intended to cover in the appended claims all such variations
and modifications as fall within the true spirit and scope of the
invention.
* * * * *