U.S. patent number 3,897,768 [Application Number 05/416,977] was granted by the patent office on 1975-08-05 for compression relief mechanism.
This patent grant is currently assigned to Tecumseh Products Company. Invention is credited to Wallace E. Thiel.
United States Patent |
3,897,768 |
Thiel |
August 5, 1975 |
Compression relief mechanism
Abstract
An automatic compression relief mechanism for an internal
combustion engine with a yoke pivotally mounted on a camshaft by a
plunger extending transversely through the cam shaft and underlying
an exhaust valve cam follower of the engine. The plunger is
extended and retracted by pivotal movement of the yoke in response
to spring and centrifugal forces acting thereon to partially open
the exhaust valve and thereby reduce the cranking effort required
to start the engine and to allow the exhaust valve to function in a
conventional manner when the engine is running under its own
power.
Inventors: |
Thiel; Wallace E. (New
Holstein, WI) |
Assignee: |
Tecumseh Products Company
(Tecumseh, MI)
|
Family
ID: |
23652090 |
Appl.
No.: |
05/416,977 |
Filed: |
November 19, 1973 |
Current U.S.
Class: |
123/182.1 |
Current CPC
Class: |
F01L
13/085 (20130101); F02B 2075/027 (20130101); F02B
2275/22 (20130101) |
Current International
Class: |
F01L
13/08 (20060101); F02B 75/02 (20060101); F01l
013/08 () |
Field of
Search: |
;123/182,113,90.15,90.16
;74/568R |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Rutledge, Jr.; W.
Attorney, Agent or Firm: Barnes, Kisselle, Raisch &
Choate
Claims
I claim:
1. In an internal combustion engine having a cylinder, a piston
reciprocable in the cylinder and defining therewith a combustion
chamber, a camshaft with a fixed cam thereon having a fixed profile
for operating an exhaust valve, the camshaft and the exhaust cam
being driven in timed relation with the speed of reciprocation of
the piston, a poppet-type exhaust valve yieldably biased to a
normally closed position and operable to control the flow of gases
from the combustion chamber to an atmosphere external of the
engine, and a follower operatively associated with the exhaust
valve in tracking relation with the cam such that rotation of the
cam by the camshaft opens and closes the valve in timed relation
with reciprocation of the piston, a compression relief mechanism
comprising in combination; a passage extending transversely through
the camshaft adjacent the cam, a plunger received in said passage
with an end underlying at least a portion of the follower tracking
the cam, a yoke adjacent and partially surrounding at least a
portion of the camshaft, said plunger in assembly continuously
extending through a portion of said yoke to mount said yoke on the
camshaft for pivotal movement in a plane generally transverse to
the axis of rotation of the cam, first and second radially and
circumferentially spaced seats adapted to receive the other end of
said plunger, said first and second seats being carried by said
yoke to be generally transverse to the axis of rotation of said
cam, bias means operably connected with said yoke to yieldably urge
said yoke to a first position wherein said first seat underlies
said other end of said plunger when said camshaft is rotated below
a predetermined maximum engine cranking speed, and a flyweight
carried by said yoke to pivotally move said yoke against the bias
of said bias means in a plane generally transverse to the axis of
rotation of the cam to a second position wherein said second seat
underlies said other end of said plunger when the camshaft rotates
at a speed above said predetermined maximum cranking speed, said
plunger having an axial length such that when said other end
thereof is received on said first seat said one end thereof extends
radially beyond the cam to engage the follower to open the exhaust
valve when it would normally be closed during cranking of the
engine, and said second seat being sufficiently generally radially
offset with respect to said first seat so that when said other end
of said plunger is received on said second seat said one end of
said plunger does not extend radially beyond the cam so that when
the engine is running at a speed above said predetermined maximum
cranking speed the exhaust valve is not opened by the plunger when
it should be normally closed.
2. The combination of claim 1 wherein said plunger has a
counterweight adjacent said other end thereof.
3. The combination of claim 1 wherein said transverse passage
through the camshaft has a counterbore in one end thereof and said
plunger has a shank and an enlarged integral head adjacent said
other end thereof with said shank being received in said passage
and said head being received at least partially within said
counterbore.
4. The combination of claim 1 wherein said yoke has a retainer with
a generally C-shaped configuration with a generally axially
extending integral tang thereon having a slot therethrough forming
in assembly a pair of axially extending tabs with said plunger
extending through said slot between said tabs to pivotally mount
said yoke on the camshaft.
5. The combination of claim 4 wherein at least one of said tabs is
bendable from a position extending generally transversely of the
axis of the cam to a position extending generally axially, whereby
said yoke can be readily assembled on the camshaft with said
plunger already received in said passage.
6. The combination of claim 1 wherein said yoke has a body
partially surrounding a generally axially extending portion of the
camshaft adjacent the cam thereof and terminating in a pair of
spaced apart free ends and said biasing means comprises a spring
connected to said body adjacent said free ends thereof and
extending between said free ends so that together said body and
spring completely extend around said portion of the camshaft
adjacent the cam thereof.
7. The combination of claim 6 wherein said spring comprises a
tension coil spring.
8. The combination of claim 4 wherein said retainer partially
surrounds a generally axially extending portion of the camshaft
adjacent the cam thereof and terminates in a pair of spaced apart
free ends, and said biasing means comprises a spring connected to
said retainer adjacent said free ends thereof and extending between
said free ends so that together said retainer and spring completely
extend around said portion of the camshaft adjacent the cam
thereof.
9. The combination of claim 1 wherein said yoke comprises a sheet
metal retainer partially surrounding a generally axially extending
portion of the camshaft adjacent the cam and terminates in a pair
of spaced apart free ends, said sheet metal retainer having an
integral flange adjacent one free end thereof with generally
axially extending radially and circumferentially spaced portions
thereof providing said first and second seats.
10. The combination of claim 9 wherein said sheet metal retainer
also has a generally axially extending integral tang thereon
adjacent the other free end thereof with said tang having a slot
therethrough forming in assembly a pair of axially extending tabs
with said plunger extending through said slot between said tabs to
pivotally mount said yoke on the camshaft.
11. The combination of claim 4 wherein at least one of said tabs is
bendable from a position extending generally transversely of the
axis of the cam to a position extending generally axially, whereby
said yoke can be readily assembled on the cam with said plunger
already received in said passage.
12. The combination of claim 9 wherein said sheet metal retainer
comprises a stamping.
13. The combination of claim 9 wherein said flyweight comprises at
least one sheet metal plate fixed to said sheet metal retainer of
said yoke.
14. The combination of claim 10 wherein said flyweight comprises at
least one sheet metal plate fixed to said sheet metal retainer of
said yoke.
15. The combination of claim 4 wherein the camshaft also comprises
a generally transversely extending flange thereon axially spaced
from the cam with said retainer received between said flange and
the cam to limit generally axial displacement of said retainer with
respect to the camshaft such that when said plunger and retainer
are assembled on the camshaft they will both be retained
thereon.
16. The combination of claim 9 wherein the camshaft also comprises
a generally transversely extending flange thereon axially spaced
from the cam with said retainer received between said flange and
the cam to limit generally axial displacement of said retainer with
respect to the camshaft such that when said plunger and retainer
are assembled on the camshaft they will both be retained
thereon.
17. In an internal combustion engine having a cylinder, a piston
reciprocable in the cylinder and defining therewith a combustion
chamber, a camshaft with a fixed cam thereon having a fixed profile
for operating an exhaust valve, the camshaft and the cam being
driven in timed relation with the speed of reciprocation of the
piston, a poppet-type exhaust valve yieldably biased to a normally
closed position and operable to control the flow of gases from the
combustion chamber to an atmosphere external of the engine, and a
follower operatively associated with the exhaust valve in tracking
relation with the cam such that rotation of the cam by the camshaft
opens and closes the exhaust valve in timed relation with
reciprocation of the piston, a compression relief mechanism
comprising in combination; a yoke partially surrounding at least a
portion of the camshaft adjacent the cam and terminating in a pair
of spaced apart free ends, said yoke being pivotally mounted
adjacent one free end thereof on the camshaft adjacent the cam for
pivotal movement in a plane generally transverse to the axis of
rotation from a first position to a second position in response to
a centrifugal force acting on said yoke when the engine operates a
a running speed in excess of a predetermined maximum cranking
speed, a spring having generally opposed ends and being connected
adjacent said opposed ends thereof to said yoke adjacent said free
ends of said yoke and extending between said free ends such that
together said yoke and said spring completely surround said portion
of the camshaft adjacent the cam, said spring yieldably retaining
said yoke in said first pivotal position when the engine is driven
at a speed below said predetermined maximum cranking speed, and an
actuator carried by the camshaft for engagement with the follower
and responsive to movement of said yoke to said first position to
lift the follower and partially open the exhaust valve when it
would otherwise normally be closed during the compression stroke of
the engine and to movement of said yoke to said second position to
move the actuator out of operable engagement with the follower.
18. The combination of claim 17 wherein said spring comprises a
tension coil spring.
19. The combination of claim 17 wherein said actuator comprises a
plunger underlying at least a portion of the follower tracking the
cam and being slidably received in a passage extending transversely
through the camshaft adjacent the cam with said plunger in assembly
continuously extending through a portion of said yoke adjacent one
free end thereof to pivotally mount said yoke on the camshaft.
20. The combination of claim 19 wherein said yoke comprises a sheet
metal body with a generally axially extending integral tang thereon
having a slot therethrough forming in assembly a pair of axially
extending tabs with said plunger extending through said slot
between said tabs to pivotally mount said yoke on the camshaft.
21. The combination of claim 20 wherein at least one of said tabs
is bendable from a position extending generally transversely to the
axis of rotation of the cam to a position extending generally
axially, whereby said yoke can be readily assembled on the camshaft
with said plunger already received in said passage.
22. The combination of claim 17 wherein said yoke comprises a sheet
metal stamping.
23. The combination of claim 17 wherein said yoke also comprises a
flyweight fixed thereto.
24. The combination of claim 19 wherein said yoke comprises a body
having an integral flange adjacent one end thereof with axially
extending generally radially and circumferentially spaced portions
thereof providing first and second seats with said first seat being
generally axially aligned with said plunger when said yoke is in
said first pivotal position and said second seat being generally
axially aligned with said plunger when said yoke is in said second
position, and said plunger having an axial length such that when
one end thereof is received on said first seat the other end
thereof extends radially beyond the cam to engage the follower to
open the exhaust valve when it would otherwise normally be closed
during the compression stroke of the engine and said second seat
being sufficiently generally radially offset with respect to said
first seat so that when the one end of said plunger is received on
said second seat, the other end of said plunger does not extend
radially beyond the cam so that when the engine is operating at a
running speed above said predetermined maximum cranking speed the
exhaust valve is not opened by the plunger when it should be
normally closed during the compression stroke of the engine.
25. The combination of claim 20 wherein said sheet metal body has
an integral flange with generally axially extending radially and
circumferentially spaced portions thereof providing first and
second seats with said first seat lapping one end of said plunger
when said yoke is in said first pivotal position and said second
seat lapping said one end of said plunger when said yoke is in said
second position, and said plunger having an axial length such that
when one end thereof is received on said first seat the other end
thereof extends radially beyond the cam to engage the follower to
open the exhaust valve when it would otherwise normally be closed
during the compression stroke of the engine and said second seat
being sufficiently generally radially offset with respect to said
first seat so that when the one end of said plunger is received on
said second seat the other end of said plunger does not extend
radially beyond the cam so that when the engine is operating at a
running speed above said cranking speed the exhaust valve is not
opened by the plunger when it should be normally closed during the
compression stroke of the engine.
26. The combination of claim 1 which also comprises an abutment on
said yoke adapted to bear on said plunger when the camshaft rotates
at a speed exceeding said predetermined maximum cranking speed to
limit the extent of the pivotal movement of said yoke away from the
camshaft.
27. The combination of claim 17 which also comprises an abutment on
said yoke adapted to bear on said actuator when the camshaft
rotates at a speed exceeding said predetermined maximum cranking
speed to limit the extent of the pivotal movement of said yoke away
from the camshaft.
28. The combination of claim 1 which also comprises a stop carried
by the camshaft and an abutment carried by said yoke to bear on
said stop when the camshaft rotates at a speed exceeding said
predetermined maximum cranking speed to limit the extent of pivotal
movement of said yoke away from the camshaft.
29. The combination of claim 17 which also comprises a stop carried
by the camshaft and an abutment carried by said yoke to bear on
said stop when the camshaft rotates at a speed exceeding said
predetermined maximum cranking speed to limit the extent of pivotal
movement of said yoke away from the camshaft.
30. The combination of claim 28 wherein said stop comprises a pin
fixedly carried by the exhaust cam of the camshaft.
31. The combination of claim 29 wherein said stop comprises a pin
fixedly carried by the exhaust cam of the camshaft.
32. The combination of claim 17 wherein a portion of said spring
intermediate said ends thereof bears on said portion of the
camshaft adjacent the cam.
33. In an internal combustion engine having a combustion chamber,
an exhaust valve yieldably biased to a normally closed position and
operable to an open position to permit the flow of gases from the
combustion chamber to an atmosphere external of the engine, and a
camshaft with a cam thereon having a profile for operating the
exhaust valve to its open and closed positions, a compression
relief mechanism comprising in combination: a passage extending
transversely through the camshaft adjacent the cam, a plunger
received in said passage, a yoke adjacent the cam, said plunger in
assembly continuously extending through a portion of said yoke to
mount said yoke on the camshaft for pivotal movement in a plane
generally transverse to the axis of rotation of the cam from a
first position to a second position in response to a centrifugal
force acting on said yoke when the engine operates at a running
speed in excess of the cranking speed of the engine, means
yieldably retaining said yoke in said first position when the
engine is driven at said cranking speed, and means operably
connecting said plunger and said yoke and responsive to movement of
said yoke to its first position to move said plunger to a first
position to at least partially open the exhaust valve when the cam
would otherwise allow it to close and responsive to movement of
said yoke to its second position to move the plunger to a second
position permitting the exhaust valve to close when allowed to do
so by the cam.
34. The combination of claim 33 wherein said plunger has a
counterweight adjacent one end thereof.
35. The combination of claim 33 wherein said yoke comprises a sheet
metal body with a generally axially extending integral tang thereon
having a slot therethrough forming in assembly a pair of axially
extending tabs with said plunger continuously extending through
said slot between said tabs to pivotally mount said yoke on the
camshaft.
36. The combination of claim 35 wherein at least one of said tabs
is bendable from a position extending generally transverse to the
axis of rotation of the cam to a position extending generally
axially, whereby said yoke can be readily assembled on the camshaft
with said plunger already received in said passage.
37. The combination of claim 33 wherein said yoke comprises a body
and said last-mentioned means comprises radially and
circumferentially spaced first and second seats carried by said
body with said first seat being generally axially aligned with said
plunger when said yoke is in its first position and said second
seat being generally axially aligned with said plunger when said
yoke is in its second position, said plunger having an axial length
such that when one end thereof is received on said first seat the
other end thereof extends radially beyond the cam to open the
exhaust valve when it would otherwise normally be closed during the
compression stroke of the engine when driven at said cranking speed
and said second seat being sufficiently generally radially offset
with respect to said first seat such that when said one end of said
plunger is received on said second seat the other end of said
plunger does not extend radially beyond the cam so that when the
engine is operating at a running speed the exhaust valve is not
opened by said plunger when it should be normally closed during the
compression stroke of the engine.
38. The combination of claim 33 which also comprises an abutment on
said yoke adapted to bear on said plunger when the engine is
operating at a running speed to limit the extent of the pivotal
movement of said yoke away from the camshaft.
39. The combination of claim 38 wherein said plunger has a
counterweight adjacent said one end thereof.
Description
This invention relates to internal combustion engines and more
particularly to automatic compression relief during cranking for
starting of internal combustion engines with cam operated cylinder
valves.
Mechanisms for significantly reducing the cranking effort required
to start an internal combustion engine by partially relieving the
compression thereof during cranking are known. For example U.S.
Campen Pat. No. 3,381,676, issued May 7, 1968 discloses an
automatic compression relief mechanism for four-stroke
single-cylinder engines in which a poppet-type exhaust valve is
partially opened during the compression stroke only during starting
of the engine by a plunger projecting radially outwardly of the
exhaust cam to engage a follower operably associated with the
exhaust valve. This plunger is retracted during running and
projected during starting of the engine by a yieldably biased
fly-weight received on the camshaft of the engine and responsive to
centrifugal force acting thereon.
Objects of this invention are to provide an improved automatic
compression relief mechanism of simplified design which can be
economically manufactured and readily assembled and which has a
long, maintenance free, useful life.
These and other objects, features and advantages of this invention
will be apparent from the following detailed description and the
accompanying drawings in which:
FIG. 1 is a fragmentary vertical section of a single cylinder
four-stroke internal combustion engine embodying this
invention.
FIG. 2 is an isometric view of the camshaft of the engine of FIG. 1
with the compression relief mechanism of this invention assembled
thereon.
FIG. 3 is an exploded isometric view of the component parts of the
compression relief mechanism and a portion of the camshaft on which
they are assembled.
FIG. 4 is a fragmentary enlarged side view of some of the component
parts of the engine of FIG. 1 showing in assembled relation the
camshaft and compression relief mechanism associated with the valve
push rods of the engine.
FIG. 5 is a semi-schematic view of the positions assumed by the
component parts of the automatic compression relief mechanism when
the engine is running and being cranked for starting in phantom and
solid lines respectively.
FIG. 6 is a fragmentary view partially in section of the camshaft
of the engine of FIG. 1 with a modified compression relief
mechanism embodying this invention assembled thereon.
FIG. 7 is an exploded isometric view of the modified compression
relief mechanism and a portion of the camshaft of FIG. 6.
FIG. 8 is a sectional view on line 8--8 of FIG. 6.
Since this invention is primarily concerned with, but not
necessarily limited to, single cylinder four-stroke cycle internal
combustion engines, the drawings illustrate the invention as
embodied in such an engine. As is customary the engine shown in
FIG. 1 has a cylinder 10, a crankshaft 12 and a piston 14
operatively connected with the crankshaft through a connecting rod
16. The piston coacts with the cylinder and a cylinder head 18 to
define a combustion chamber 20. A spark plug 22 secured in the
cylinder head ignites the fuel charge after it has been drawn into
the combustion chamber during the intake stroke and then compressed
during the compression stroke of the piston, the spark normally
being timed to ignite the fuel charge just before the piston
completes its ascent on the compression stroke. The fuel charge is
drawn into the combustion chamber from the carburetor of the engine
through an intake passage controlled by a conventional intake valve
(not shown), and the products of combustion are expelled from the
cylinder during the exhaust stroke through an exhaust port 24
controlled by a poppet-type exhaust valve 26.
The conventional parts of the valve operating mechanism include a
timing gear 27 mounted on crankshaft 12 for rotation therewith and
a timing gear 28 mounted on a camshaft 30 and rotatably driven by
gear 27 to thereby rotate the camshaft at one-half crankshaft
speed. Camshaft 30 carries conventional pear-shaped intake and
exhaust cams 32 and 34 (FIGS. 2 and 4) which rotate with the
camshaft to impart reciprocating motion to the intake and exhaust
valves via flat-footed push rods 36 and 38 respectively. The
complete exhaust valve train is shown in FIG. 1 and includes push
rod 38 which has a circular follower 40 with a flat underface 42
adapted to bear tangentially against and track upon the periphery
44 of cam 34. A stem 46 of the push rod slides in a guide boss 48
of crankcase 50 and butts its upper end against the stem 52 of
exhaust valve 26. A valve spring 54 encircles stem 52 between a
valve guide 56 and a spring retainer 58 carried on the stem, spring
54 biasing valve 26 closed and also biasing push rod 38 into
tracking contact with cam 34.
The above-described engine and valve train parts are conventional,
as is the fixed profile of exhaust cam 34 which consists of a base
circle 60 and a lobe 62. When the compression relief mechanism
described hereinafter is in its inoperative or run position,
rotation of cam 34 with camshaft 30 causes normal operation of
valve 26 so that it opens and closes in timed relation with the
travel of the piston 14 according to conventional engine timing
practice. Thus cam lobe 62 is adapted to open valve 26 near the end
of the power stroke and to hold the same open during ascent of the
piston on the exhaust stroke until the piston has moved slightly
past top dead center. When follower 40 contacts base circle 60,
spring 58 reseats valve 26 and holds the same closed during the
ensuing intake, compression and power strokes. Intake cam 32 is
likewise of conventional fixed configuration to control the intake
valve such that it closes completely shortly after the piston
begins its compression stroke and remains closed through the
subsequent power and exhaust strokes, reopening to admit the fuel
mixture on the intake stroke.
Since in a conventional engine the intake and exhaust valves are
normally closed for the major portion of the compression stroke,
cranking of the engine would be difficult unless some provision is
made to vent the combustion chamber 20 during part or all of the
compression stroke during cranking of the engine. However, by
modifying a conventional engine to incorporate the improved
compression relief mechanism in accordance with the present
invention, compression relief is automatically obtained at cranking
speeds to greatly reduce cranking effort and thereby facilitate
starting. In addition, the mechanism is responsive to engine speed
such that it is automatically rendered inoperative at engine
running speeds so that there is no compression loss to decrease the
efficiency of the engine when it is running under its own
power.
As shown in FIGS. 2 and 4, compression relief mechanism 70 is
received on camshaft 30 between exhaust cam 34 and an integral
flange 72 which limits the axial displacement of relief mechanism
70 relative to camshaft 30. Relief mechanism 70 has a yoke 74 and a
tension coil spring 76 received on a cylindrical portion 78 of
camshaft 30, the yoke being retained thereon by a plunger 80
extending transversely through the cylindrical portion. Plunger 80
is slidably received in a bore 82 with a counterbore 84 adjacent
one end thereof. Bore 82 extends radially through camshaft 30
closely adjacent exhaust cam 34 and underlies cam follower 40.
Plunger 80 has a shank 85 with an enlarged head 86 at one end
thereof and preferably a chamfer 87 on the other end thereof. To
provide an adequate flow of lubricating oil through an axial
lubricating passage 88 in camshaft 30, the diameter of shank 85 of
plunger 80 should be substantially smaller than the diameter of
axial bore 88.
Yoke 74 has a generally C-shaped retainer 90 mounted on camshaft 30
by plunger 80 for pivotal movement in a plane generally transverse
to the axis of rotation of exhaust cam 62. Retainer 90 is
preferably a one piece sheet metal stamping with an integral
generally axially extending flange 92 thereon with a tang adjacent
one end thereof having a slot 94 therethrough forming a pair of
circumferentially spaced tabs 96 and 96'. As shown in FIG. 3, prior
to assembly, tab 96 extends generally radially outwardly relative
to the axis of the camshaft and in assembly is bent to extend
generally axially with plunger 80 received in slot 94 between tabs
96 and 96' to pivotally mount yoke 74 on camshaft 30. Adjacent the
other end of retainer 90, flange 92 forms axially extending
generally circumferentially and radially spaced seats 98 and 100
for receiving the head 86 of plunger 80 thereon with a cam surface
102 therebetween for axially shifting plunger 80. The extent of
pivotal movement of retainer 90 is limited by a generally radially
extending tab 104 and an abutment portion 106 of flange 92. The
axial movement of retainer 90 on camshaft 30 is limited by tangs
107 and tabs 96, 96' on flange 92, which abut on an adjacent side
face of exhaust cam 34, and the distal side face of the retainer
which abuts flange 72 of the camshaft. The free ends of retainer 90
have holes 108 therethrough for connection of coil spring 76
thereto. Yoke 74 has a fly-weight provided by two crescent shaped
plates 110 and 112 which are preferably sheet metal stampings
located on retainer 90 by projections 114 and brazed thereto.
Preferably, compression relief mechanism 70 is subassembled on
camshaft 30 prior to assembly thereof into the engine. Plunger 80
is inserted into bore 82 in the camshaft and then the open throat
of C-shaped retainer 90 of yoke 74 with tab 96 thereof extending
radially (FIG. 3) is slipped generally radially or transversely
over cylindrical portion 78 of the camshaft. In slipping retainer
90 over the camshaft, seat 100 is first lapped with head 86 of the
plunger and then the retainer with tab 104 engaging the far side of
head 86 is pivoted into position so the plunger bears on tab 96'.
Tab 96 is then bent (to the position shown in phantom in FIG. 3) to
extend axially to retain the plunger in slot 94 between the tabs.
As thus assembled, retainer 90 is mounted on camshaft 30 for
limited pivotal movement by the cooperation of plunger 80 therewith
and the plunger is entrapped in the camshaft by the retainer. The
hooks on the free ends of tension spring 76 are inserted into holes
108 in the free ends of retainer 90 so that, in assembly, the
spring extends generally circumferentially between the free ends of
the retainer around cylindrical portion 78 of camshaft 30 generally
opposite the retainer.
In operation of compression relief mechanism 70, yoke 74 is
retained by spring 76 immediately adjacent cylindrical portion 78
in the position shown in solid lines in FIG. 5 when the engine is
rotated at a relatively low cranking speed which is usually less
than 600 revolutions per minute. In this position, the head 86 of
plunger 80 bears on seat 98 of yoke 74 and the other end of the
plunger projects radially outward of base circle 60 of exhaust cam
34 to partially open exhaust valve 26 when it would normally be
closed if the engine were running. Thus, the free end of plunger 80
will bear on the underface 42 of follower 40 and lift it a
predetermined distance (which preferably is a fraction of the full
or maximum lift provided by cam 34) thereby lifting exhaust valve
26 off its seat for a portion of each compression stroke to relieve
compression during starting as long as the engine speed does not
exceed a predetermined maximum cranking speed.
As soon as the engine starts and obtains a running speed under its
own power the rotational speed of camshaft 30 increases above a
predetermined maximum cranking speed and centrifugal force acting
on yoke 74 (including the flyweight thereof) overcomes the bias of
spring 76 and pivots the yoke clockwise (as viewed in FIG. 5) so
that the head 86 of plunger 80 can bear on seat 100, as shown in
phantom in FIG. 5. When the plunger 80 assumes the position shown
in phantom in FIG. 5, its free end is retracted so that it does not
project beyond base circle 60 of cam 34 and thus valve 26 is not
partially opened by the plunger and functions in the conventional
manner when the engine is running under its own power. The point at
which yoke 74 moves pivotally outward is dependent on the mass
thereof and particularly the mass of the flyweight provided by
plates 110 and 112 which can be selected to produce this pivotal
movement at a predetermined maximum cranking speed, which is
typically in the range of 750 to 1000 engine revolutions per
minute. This predetermined maximum cranking speed is above the
normal engine cranking speed and below the usual idling speed of
1200 to 1500 engine revolutions per minute for a single-cylinder,
four-cycle engine. When the running engine is shut down, yoke 74 is
pivoted inwardly toward camshaft 30 by spring 76 as the engine
slows down below the predetermined maximum cranking speed in
coasting to a stop. This pivotal movement of yoke 74 toward
camshaft 30 causes cam surface 102 between seats 98 and 100 to
engage head 86 of plunger and shift the free end of the plunger
radially outward so that head 86 bears on seat 98. This repositions
plunger 80 to relieve the compression of the engine when it is next
rotated at a cranking speed for starting. Plunger 80 is
counterweighted by head 86 so that centrifugal force acting on the
plunger tends to urge it into engagement with seats 98 and 100 of
yoke 74 whenever shaft 30 is rotated. This assures that plunger 80
will remain firmly engaged with the seats whenever the camshaft is
rotating.
FIG. 6 shows a modified form of a compression relief mechanism 70'
with a modified yoke 74' assembled on camshaft 30. As shown in FIG.
7, yoke 74' is the same as yoke 74 except that tab 96" extends
generally axially rather than radially and tab 104' extends
generally radially outwardly rather than inwardly. To limit the
extent to which yoke 74' can pivot about pin 80 generally radially
outwardly from the camshaft, tab 104' abuts on a positive stop
provided by a roll pin 116 which is received with an interference
fit in a hole 118 through cam lobe 34.
Compression relief mechanism 70' is assembled on camshaft 30 by
inserting plunger 80 through bore 82 in the camshaft and then
manipulating yoke 74' to slip the shank end of plunger 80 through
slot 104 between tabs 96" and 96'. Yoke 74' is then pivoted
generally radially inwardly so that seat 98 or 100 underlies head
86 of the plunger and roll pin 116 is pressed into hole 118 through
cam lobe 34 to retain yoke 74' on the camshaft as shown in FIGS. 6
and 8. The ends of spring 76 are then hooked through holes 108 in
yoke 74' to yieldably bias the yoke toward the start position as
shown in FIG. 8.
In use compression relief assembly 70' operates in the same manner
as compression relief assembly 70 with tab 104' abutting on roll
pin 116 when yoke 74' is in the run position to limit the extent of
generally pivotal movement of the yoke away from the camshaft.
Compression relief assembly 70 is believed to be more economical to
manufacture although compression relief assembly 70' is somewhat
easier to assemble on the camshaft without any special assembly
fixtures since tab 96" does not have to be bent during assembly
after the yoke is received on the camshaft.
This invention provides a compression relief mechanism of
simplified design in which the plunger and yoke retainer cooperate
to pivotally mount the yoke on the camshaft and to retain the
plunger therein. The compact design with a minimum number of
component parts of this invention provides a compression relief
mechanism of economical manufacture particularly since the yoke can
be made of sheet metal stampings. The use of a retainer in this
invention which can be manually slipped over the plunger and
camshaft and pivotally mounted on the camshaft by simply bending
down one of the tabs provides a compression relief mechanism which
can be easily and economically assembled. The simplified design
with the minimum number of component parts of this invention also
provides a rugged and durable compression relief mechanism with a
long maintenance-free, useful life.
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