U.S. patent application number 11/308965 was filed with the patent office on 2006-11-30 for valve actuating system for reciprocating machine.
This patent application is currently assigned to YAMAHA HATSUDOKI KABUSHIKI KAISHA. Invention is credited to Tsunero Hamada, Yasuo Okamoto.
Application Number | 20060266315 11/308965 |
Document ID | / |
Family ID | 36933415 |
Filed Date | 2006-11-30 |
United States Patent
Application |
20060266315 |
Kind Code |
A1 |
Hamada; Tsunero ; et
al. |
November 30, 2006 |
VALVE ACTUATING SYSTEM FOR RECIPROCATING MACHINE
Abstract
A number of cylinder head arrangements that provide low cost and
easy assembly of their various components with minimum labor and
reduced necessity for line boring to reduce both manufacturing and
assembly operation without adversely affecting performance.
Inventors: |
Hamada; Tsunero; (Iwata-shi,
JP) ; Okamoto; Yasuo; (Iwata-shi, JP) |
Correspondence
Address: |
ERNEST A. BEUTLER, ATTORNEY AT LAW
10 RUE MARSEILLE
NEWPORT BEACH
CA
92660
US
|
Assignee: |
YAMAHA HATSUDOKI KABUSHIKI
KAISHA
2500 Shingai
Iwata-shi
JP
|
Family ID: |
36933415 |
Appl. No.: |
11/308965 |
Filed: |
May 30, 2006 |
Current U.S.
Class: |
123/90.16 ;
123/90.27; 123/90.44 |
Current CPC
Class: |
F01L 1/185 20130101;
F01L 2001/0537 20130101; F01L 1/053 20130101 |
Class at
Publication: |
123/090.16 ;
123/090.27; 123/090.44 |
International
Class: |
F01L 1/18 20060101
F01L001/18; F01L 1/02 20060101 F01L001/02; F01L 1/34 20060101
F01L001/34 |
Foreign Application Data
Date |
Code |
Application Number |
May 31, 2005 |
JP |
2005-159297 |
Claims
1. A valve actuating mechanism for a reciprocating machine having a
cylinder head adapted to be affixed in closing relation to at least
one cylinder bore formed in a cylinder block, a cam shaft carrier
affixed to said cylinder head and defining a cam shaft bore for
journaling a bearing surface of a cam shaft, a rocker arm journal
formed by said cam shaft carrier in parallel relation to said cam
shaft bore and extending on at least one side of said cam shaft
bore, and a rocker arm journalled by said rocker arm journal and
having a follower surface engaged by a cam lobe of said cam
shaft.
2. A valve actuating mechanism as set forth in claim 1 wherein a
pair of rocker arm journals are formed by said cam shaft carrier,
each of which journals a respective rocker arm.
3. A valve actuating mechanism as set forth in claim 2 wherein the
pair of rocker arm journals formed by the cam shaft carrier are
coaxial.
4. A valve actuating mechanism as set forth in claim 3 wherein the
coaxial pair of rocker arm journals formed by said cam shaft
carrier are disposed on opposite axial sides of the cam shaft
bore.
5. A valve actuating mechanism as set forth in claim 2 wherein the
pair of rocker arm journals formed by the cam shaft carrier are
disposed on opposite sides of the cam shaft bore.
6. A valve actuating mechanism as set forth in claim 5 further
including a second pair of rocker arm journals formed by the cam
shaft carrier on opposite axial sides of the cam shaft bore to
receive and journal a total of four rocker arms.
7. A valve actuating mechanism as set forth in claim 1 wherein the
cylinder head closes a plurality of parallel, axially spaced
cylinder bores of an associated cylinder block and respective cam
shaft carriers are associated with the cylinder bores.
8. A valve actuating mechanism as set forth in claim 7 wherein a
pair of rocker arm journals are formed by each of the cam shaft
carriers, each of said journals journaling a respective rocker
arm.
9. A valve actuating mechanism as set forth in claim 8 wherein the
respective rocker arms operate valves associated with the same
cylinder closed by the cylinder head.
10. A valve actuating mechanism as set forth in claim 9 wherein the
valves operated by the rocker arms are both intake or exhaust
valves.
11. A valve actuating mechanism as set forth in claim 9 wherein one
of the valves operated by one of the rocker arms is an intake valve
and the other rocker arm operates an exhaust valves.
12. A valve actuating mechanism as set forth in claim 2 wherein the
pair of rocker arm journals formed by the cam shaft carrier are
parallel.
13. A valve actuating mechanism as set forth in claim 3 wherein the
parallel pair of rocker arm journals formed by said the shaft
carrier are disposed on opposite axial sides of the cam shaft
bore.
14. A valve actuating mechanism as set forth in claim 2 wherein the
pair of rocker arm journals formed by the cam shaft carrier are
disposed on opposite sides of the cam shaft bore.
15. A valve actuating mechanism as set forth in claim 5 further
including a second pair of rocker arm journals formed by the cam
shaft carrier on opposite axial sides of the cam shaft bore to
receive and journal a total of four rocker arms.
16. A valve actuating mechanism as set forth in claim 15 further
including slots formed in the cam shaft carrier for retaining
respective of the journalled rocker arms.
17. A valve actuating mechanism as set forth in claim 16 further
including pivot shafts for pivotally supporting pairs of said
rocker arms on the respective opposite axial sides.
18. A valve actuating mechanism as set forth in claim 9 wherein
there are spark plug receiving openings formed by the cylinder head
each generally aligned with the axis of the respective cylinder
bore and further including a plurality of spark plug receiving
collars affixed to the cylinder head for receiving respective ones
of said spark plugs.
19. A valve actuating mechanism as set forth in claim 18 wherein
the collars each cooperate with a respective one of the cam
carriers for fixing their positions relative to the cylinder
head.
20. A valve actuating mechanism as set forth in claim 19 wherein
the coefficients of thermal expansion of the collars and cam
carriers are different to effect interlocking therebetween under
operating conditions.
Description
BACKGROUND OF THE INVENTION
[0001] This invention relates to reciprocating machines such as
internal combustion engines or compressors of the type having a
cylinder block having one or more cylinder bores that reciprocally
support a piston or pistons that are connected a crankshaft at one
end. The opposite end of these cylinder bores is closed by a
cylinder head affixed to the cylinder block in a suitable manner.
The flow into and out of the cylinder bores is controlled by valves
reciprocally mounted in the cylinder head and operated by one or
more camshafts journalled therein. Frequently the valves are
operated from cams on the camshaft through pivotally supported
rocker arms.
[0002] Although this arrangement is generally effective, a
substantial number of machining and assembly steps are required to
complete the assembly. This adds to the cost and can, if not
closely controlled, present alignment problems that can introduce
inaccuracies and less than desirable operation.
[0003] As an example of a prior art construction of this type,
Japanese Published Application, Publication Number P2000-170506A
shows a construction wherein an intake side camshaft and an exhaust
side camshaft are journalled by underlying lower cam holders and
overlying upper cam holders. The lower cam holders condition are
fastened to the cylinder head via a first series of fasteners. In
addition, the upper cam holder and lower cam holder are fastened to
each other at positions spaced inward from the first fasteners. In
addition the second fastening members each have a smaller diameter
than the first fastening member.
[0004] It is also stated therein that that size reduction of the
cylinder head is possible and the first fastening members also
serve to resist undesired cocking of the rocker shafts. However
much fitting and precise location is required for machining and
assembly.
[0005] As a further disadvantage to this type of construction, to
secure the positional accuracy of the rocker shaft support section
formed on the lower cam carrier, line boring is necessary after the
lower cam carriers are mounted independently on each cylinder head.
Therefore, the scale of machining facilities for such line boring
become larger.
[0006] In addition, since the rigidity of hole machining tools
needs to be secured to secure the machining accuracy, size
reduction of the tool diameter is difficult. Therefore, weight
saving and size reduction of the rocker shaft are difficult and in
turn, weight saving and size reduction of the rocker arm are also
difficult.
[0007] Another prior art structure is shown in Japanese Patent
Publication B 2537205. As shown therein each rocker shaft is
configured to be supported pivotally on a respective one of a
plurality of cam carriers. Therefore, when the cam carriers are
assembled to the cylinder head, they need to be assembled in
succession while rocker arms are fitted on the rocker shafts,
causing complicated assembly work.
[0008] In addition, each rocker shaft should not to overlap the
opening that receives the respective spark plug insert. Therefore
the support section for each of the rocker shafts needs to be
separately machined for each cam carrier, making positional
accuracy is difficult to obtain.
[0009] Therefore it is a principal object of this invention to
provide a simplified, low cost and easily manufactured and
assembled arrangement for operating the valves of a multi cylinder
and valve reciprocating machine.
SUMMARY OF THE INVENTION
[0010] This invention is adapted to be embodied in a low cost,
easily manufactured and assembled valve actuating mechanism for a
reciprocating machine having a cylinder head adapted to be affixed
in closing relation to at least one cylinder bore formed in a
cylinder block. A cam shaft carrier is affixed to the cylinder head
and defines a cam shaft bore for journaling a bearing surface of a
cam shaft. A rocker shaft journal is formed by the cam shaft
carrier in parallel relation to the cam shaft bore and extends on
at least one side of the cam shaft bore. A rocker arm is journalled
by the rocker shaft journal and has a follower surface engaged by a
cam lobe of the cam shaft.
BRIEF DESCRIPTION OF THE DRAWINGS
[0011] FIG. 1 is a top plan view of the cylinder head of a
reciprocating machine constructed in accordance with a first
embodiment of the invention, with the cam cover removed to more
clearly show the construction.
[0012] FIG. 2 is a further enlarged view of this embodiment, with
the cam shafts removed.
[0013] FIG. 3 is a side elevational view looking in the direction
of the arrow 3 in FIG. 2 showing the valves operated in
phantom.
[0014] FIG. 4 is a cross sectional view taken along the line 4-4 in
FIG. 3.
[0015] FIG. 5 is a cross sectional view taken along the line 5-5 in
FIG. 3.
[0016] FIG. 6a is an enlarged view taken generally along the line
6-6 in FIG. 2 and shows the condition when the associated valve is
closed.
[0017] FIG. 6b is an enlarged view taken generally along the line
6-6 in FIG. 2 and shows the condition when the associated valve is
opened.
[0018] FIG. 7 is a view in part similar to FIG. 2 and shows another
embodiment of the invention.
[0019] FIG. 8 is a side elevational view looking in the direction
of the arrow 7 in FIG. 6 showing the valves operated in
phantom.
[0020] FIG. 9 is a top plan view, in part similar to FIG. 1, but
with the cylinder head reversed, and shows still another embodiment
of the invention.
[0021] FIG. 10 is a further enlarged view of the embodiment of FIG.
9, showing one of the center cam shaft carriers with the cam shafts
removed.
[0022] FIG. 11 is a side elevational view looking in the direction
of the arrow 11 in FIG. 10 showing the valves operated and the
operating cam lobes in phantom.
[0023] FIG. 12 is a cross sectional view taken along the line 12-12
in FIG. 11.
[0024] FIG. 13 is a top plan view, in part similar to FIGS. 2, 7,
and 10 showing only the two cam carriers of this embodiment
provided at the opposite ends of the cylinder head
[0025] FIG. 14 is a cross sectional view of the embodiment of FIG.
13 taken along a plane passing through the axes of the rocker arm
journals.
DETAILED DESCRIPTION
[0026] Referring now in detail to the drawings and initially to the
embodiment of FIGS. 1-6, a multi-cylinder reciprocating machine is
shown partially and is identified generally by the reference
numeral 21. As will be readily apparent to those skilled in the
art, the invention may be applied to either reciprocating internal
combustion engines or compressors. However to simplify the
disclosure only engine applications are illustrated.
[0027] In the illustrated embodiment of these figures (FIGS. 1-6),
a cylinder head, indicated generally at 22 is suitably affixed to a
cylinder block (not shown). Basically any number of cylinders and
any engine configuration may be employed such as in line, v type or
opposed.
[0028] In accordance with the invention, a plurality of cam
carriers 23 are provided on the cylinder head 22 in a manner to be
described shortly. The cam carriers 23 support for rotation an
intake cam shaft 24 and an exhaust cam shaft 25 disposed parallel
to each other. To this end, the cam carriers 23 are formed by a
single lower piece 23a having lower bearing recesses 23i and 23e
each associated with respective, axially spaced journal surfaces
24b and 25b of the respective intake and exhaust cam shafts 24 and
25
[0029] To further complete the journaling of the cam shafts 24 and
25, bearing caps 26i and 26e are affixed, in a manner to be
described shortly, to the single lower piece 23a and the cylinder
head 22. These bearing caps have bearing surfaces 26ib and 26eb
that are complementary to the lower bearing recesses 23i and 23e.
These bearing surfaces 26ib and 23i and 26eb and 23e embrace and
journal the axially spaced cam shaft bearing sections 24b and 25b
of the cam shafts 24 and 25, respectively.
[0030] The driven ends of the cam shafts 24 and 25 are also
journalled directly in the end of the cylinder head 22 by end
bearing caps also indicated by the reference numerals 26ie and
26ee.
[0031] Threaded fasteners 27 pass through bored holes 28 in the
bearing caps 26i, and 26e and aligned holes 29 formed in the single
lower pieces 23a to fix the elements together. At the driven end of
the camshafts 24 and 25 the end bearing caps 26ie and 26ee are
bored to cooperate with tapped holes formed in the cylinder head at
the driven end. Finally the lower ends 27e of all of these threaded
fasteners 27 are threaded into tapped holes formed in the cylinder
head 22 to complete the assembly.
[0032] In addition a further pair of bored holes 28 are formed in
axial alignment with the transverse center of the cylinder head 22
in the area of the single lower pieces 23a between the bearings 23i
and 23e above tapped holes in the cylinder head 22 to receive
further threaded fasteners 30 for additional security in retaining
the lower pieces 23a when the bearing caps 26i and 26e are
removed,
[0033] Continuing to refer primarily to FIG. 1, the intake cam
shaft 24 is formed with a plurality of intake cams 24c, and the
exhaust cam shaft 25 is formed with a plurality of exhaust cams
25c. These pluralities of cams 24c and 25c are each adapted to
operate the intake and exhaust valves, to be described shortly,
through respective intake and exhaust rocker arms 31 and 32.
[0034] To this end, the single piece 23a of each of the cam
carriers 23 is formed with an intake side rocker shaft journal
opening 23irj and an exhaust side rocker shaft opening 23erj in a
rocker shaft support section 23ras located between the intake cam
shaft bearing 23i and the exhaust cam shaft bearing 23e, as shown
in FIGS. 2 and 3.
[0035] Intake and exhaust rocker shafts 33, 34, respectively, are
supported by the rocker shaft support portions 23ras, as shown in
FIGS. 1-4. The rocker shaft support section 23ras is provided on
both sides of the cam shaft bearings 23i and 23e and extends in the
same direction as the cam shafts 24, 25 (see FIG. 1).
[0036] The rocker shaft journal openings 23irj, 23erj are formed in
the cam carrier 23 as through-holes passing through the rocker
shaft support section 23ras. The rocker shafts 33, 34 are inserted
in these rocker shaft through-holes 23irj, 23erj.
[0037] In addition to the structure as thus far described, the
single lower piece 23a of each of the cam carriers 23 is formed
with a hole 35 for a spark plug insert section between the intake
rocker arm support 23irj and the exhaust rocker arm support 23erj.
This hole extends in a direction perpendicular to the axial
direction of these shaft receiving sections 23irj, 23erj, as shown
in FIGS. 1, 2 and 4.
[0038] A cylindrical collar 36 is fitted In the hole 35 for each
ignition plug insert section formed in the cam carrier 23, as shown
in FIG. 1. Suitably mounted ignition plugs 37 serve the combustion
chambers formed in part by the cylinder head 22 through the collars
36.
[0039] In addition to this purpose, the collars 36 also have the
function of preventing the rocker shafts 33, 34 from slipping off
the cam carrier 23. This is accomplished by forming the rocker
shafts 33 and 34 with notches 33a and 34a, respectively to engage
parts of the collar 36 for the prevention of their
slipping-off.
[0040] It is arranged so that the linear thermal expansion
coefficient of the collar 36 is different (either larger or
smaller) than that of the cam carrier 23. This will insure that the
collar 36 can be attached to and detached from the cam carrier 23
in a cold or a hot environment and subsequently the collar 36 will
be prevented from slipping off the cam carrier 23 at room
temperature. Such an arrangement improves handling properties of
the cam carrier 23, as well as its assembling properties, and a
slipping-off prevention condition can be realized of a minimum
amount of play as compared with mechanical fasteners such as
bolts.
[0041] As best seen in FIGS. 2 and 4, the cam carrier lower pieces
23a are formed with slots 23 as and intake side rocker arms 31 and
exhaust side rocker arms, 32 are inserted in these slots 23 as. The
rocker arms 31, 32 are formed with shaft insert holes 31a, 32a,
respectively for journaling rocker arms 31 and 32 in the lower
pieces 23a on their shafts 33 and 34.
[0042] With the intake side rocker arms 31 fitted in the slots 23
as of the cam carrier 23, the intake side rocker shaft 33 is
inserted in the intake side rocker shaft through-holes 23irj and
shaft insert hole 31a. Likewise, with the exhaust side rocker arm
32 fitted in the slot 23 as of the cam carrier 23, the exhaust side
rocker shaft 34 is inserted in the exhaust side rocker shaft
through-hole 23erj and shaft insert hole 32a. The rocker shafts 33,
34 are supported independently for each cam carrier 23, and pass
through the rocker shaft support section 23ras of the cam carrier
23 and extend on both sides of the cam shaft bearing section 24b so
as to be disposed parallel to the cam shafts 24, 25. Thus the
rocker arms 31, 32 are supported for rotation by the rocker shafts
33, 34 on both sides of the cam shaft bearing section 26ib of the
cam carrier 23.
[0043] When the intake side cam shaft 24 and exhaust side cam shaft
25 are rotated, each of the intake side cams 24c and exhaust side
cams 25c depresses each of the intake side rocker arms 31 and
exhaust side rocker arms 32 for opening or the action of the
springs, to be described, releases the depression and permits the
rocker arms and associated valves to move to the closed
positions.
[0044] The cam carriers 23 are mounted approximately directly above
each respective cylinder and configured such that all of the
plurality of rocker arms 31, 32 supported on both sides of the cam
shaft bearing section 26ib of the cam carrier 23, correspond to
that respective cylinder. Thus and as best seen in FIG. 3, each of
the valves, indicated generally by the reference numeral 38,
serving a respective one cylinder are adapted to be opened/closed
by the movement of the four rocker arms 31, 32 supported on the two
rocker shafts 33, 34 of one cam carrier 23.
[0045] Referring now primarily to FIGS. 2-5, and 6a and 6b, it will
be seen that the upper bearing halves 26ib and 26eb have the
aforementioned aligned holes 29 through which the threaded
fasteners 27 pass along with the aligned bores 28 of the single
lower piece 23a for the fastening of these assemblies to the
cylinder head 22 in the desired relation to the associated
cylinder.
[0046] As another feature of the invention, the cam carriers 23
also cooperate to lubricate the valves and operating mechanism. To
this end, the single lower piece 23a of each cam carrier 23 is
formed with an oil passage, indicated generally at 39, shown in
FIGS. 2, 3 and 6a and 6b. This oil passage receives 39 pressurized
oil from the engine lubricating system in a suitable manner and
communicates with oil passages 41, 42, respectively, extending
toward the intake rocker shaft 33 and exhaust rocker shaft 34.
These passages 41 and 42 communicate respectively with coaxial oil
passages 43, 44, formed in the rocker arm shafts 33 and 34
respectively. To this end, the rocker shafts 33, 34 are each formed
hollow inside and closed at both ends to form the oil passages 43
and 44.
[0047] The valve gear lubricating system also includes oil delivery
notches 31d and 32d formed in the intake rocker arms 31 and exhaust
rocker arms 32, respectively. These oil delivery notches 31d and
32d are formed at the outer ends of delivery passages 43 and 44
that communicate with the rocker arm passages 41 and 42,
respectively and face toward the intake cams 24c and exhaust cams
25c, shown partially in FIGS. 6a and 6b. As best seen in FIG. 4,
the rocker shafts 33, 34 are retained axially by notches 33a, 34a
formed therein that are engaged by the collar 36.
[0048] The valves 38 associated with the structure already
described, their operation and construction will now be described
in more detail by reference to FIG. 3. Each valve 38 is of the
poppet type and has a valve stem 45 that is supported for
reciprocation in the cylinder head 22 by a respective valve guide
42 pressed or otherwise secured to the cylinder head 22. A valve
head 46 at the lower end of the respective stem cooperates with a
valve seat (not shown) fixed at the combustion chamber end of the
cylinder head 22 to control the flow through a respective intake or
exhaust port, not shown in this figure, but as well known to those
skilled in this art.
[0049] The valves 38 are normally retained in closed positions, as
also known in the art, by return springs 47 of a desired type, with
coil springs shown by way of example. These springs 47 are loaded
between retainers 48 engaged with the cylinder head 22 and keeper
retainers 49 fixed to the upper ends of the respective valve stem
45 to normally urge the valves 38 to their closed positions as
shown in FIGS. 3 and 6a.
[0050] As the respective cam shafts 24 and 25 rotate, their cam
lobes 24c and 25c will act to drive the respective valves 38 to
their opened positions as shown in FIG. 6b, with compression of the
springs 47. Upon continued rotation of the respective cam shaft 24
and 25 their lobes 24c and 25c will move away from the stems 45 and
the springs 47 will close the valves 38, as is well known in the
art.
[0051] As has also been noted, the oil delivery system for
lubricating the valve train including the cam shafts 24 and 25 and
specifically their respective cam lobes 24c and 25c, the contacted
surfaces of the rocker arms 31 and 32 and the stems of the operated
valves insures adequate lubrication. However a system is also
incorporated for controlling the amount of lubricant supplied to
these areas so as to prevent excess oil flow. This system is
described in connection with the exhaust valves but it should be
understood that the intake valves are lubricated by the same type
of flow controlling construction
[0052] The oil or other lubricant is delivered continuously to the
hollow interior of the respective rocker arm shaft, this being the
passage 44 in the case of the exhaust valves 45 from the carrier
base 23a through a delivery opening 44i that is continuously open
since the rocker arm shaft 34 does not rotate. However the rocker
arm 32 does rotate and its delivery passage 42 only overlaps a
discharge opening 44d in the associated rocker arm 32 only at the
time the associated rocker arm is moved toward the valve opening
positions, as shown by comparing FIG. 6b with FIG. 6a.
[0053] To summarize the operation of this embodiment, as the engine
21 operates and the cam shafts 24, 25 and their plurality of cams
24c, 25c rotate, and the cams 24c, 25c depress will sequentially
pivot the rocker arms 31, 32, and the valve stems 33 are lowered
along with their valve faces 32 air is taken in on the intake side
and combustion gas is exhausted on the exhaust side as is well
known in the art.
[0054] In a like manner, when the cams 24c, 25c rotate beyond the
condition of depressing the rocker arms 31, 32, the valve stems 33
are raised by the action of the springs 47 and the valve faces 32
are also raised to close their respective seats (not shown) so that
no air will be taken in on the intake side and no exhaust gas will
be exhausted on the exhaust side. The lubrication of the operating
mechanism is effected only when the valves are being operated so as
to avoid excess lubrication.
[0055] Thus, as should be readily apparent to those skilled in the
art, the embodiment of FIGS. 1-6 incorporates cam shafts 24, 25
having a plurality of cams 24c, 25c for depressing rocker arms 31,
32 journalled by a plurality of cam carriers 23 each formed
integrally with cam shaft bearing sections 26ib and 26eb for
supporting the cam shafts and rocker shaft support sections 23irj
and 23erj for supporting rocker shafts 33 and 34. The rocker shafts
33, 34 each supported independently by a cam carrier 23, positioned
in the rocker shaft support section 23ras of the cam carrier 23 and
extending on both sides of the cam shaft bearing section 26ib. Thus
the axes of the cam shafts 24, 25, support of the rocker arms 31,
32 on the rocker shafts 33, 34 on both sides of the cam bearing
section 26ib of the cam carrier 23 are also parallel.
[0056] Therefore, since a plurality of cam carriers 23 are provided
and the rocker shaft 33, 34 are adapted to pass independently
through respective of the rocker shaft support sections 23ras of
the cam carriers 23, not all the plurality of rocker shafts 33, 34
need be centered to facilitating assembly. Further, since the
rocker shaft 33, 34 are divided for each cam carrier 23 and small
in length, weight saving and size reduction can be effected.
Further, smaller scale, machining facilities for the cam carriers
23 can be employed. In addition, the positional accuracy of the
holes for supporting rocker shafts 33, 34 to the cam shaft bearing
sections 26ib 26eb can be obtained easily, resulting in improvement
in reliability. Moreover, the work in mounting the rocker shafts
33, 34 to the arm carrier 33 is decreased.
[0057] As added advantages, the rocker shaft support section 23ras
extend on both sides of the cam shaft bearing section 26ib in the
same direction as the cam shafts 24, 25 and is formed with slots 23
as for supporting the rocker arms 31, 32. The rocker shaft support
section 23ras is formed with through-holes 23irj, 23erj passing
therethrough across the slots 23 as, and the rocker shafts 33, 34
are inserted in the through-holes 23irj, 23erj. Therefore, since
the rocker arms 31, 32 are held by the slots 23 as on both sides in
the vicinity of the shaft insert holes 31a, 32a, the rigidity of
the mounting of the rocker arms 31, 32 along with accurate movement
of the rocker arms 31, 32, effecting higher rotation speed and
improvement in reliability.
[0058] As a further advantage, the cam carriers 23, the rocker
shafts 33, 34 and the rocker arms 31, 32 have passages 39, 41, 42,
43, 44 for oil supplied from the cylinder head 22 and the rocker
shaft 33, 34 are hollow inside and closed at both ends with the
notches 33a, 34a being covered by the collar 36. Therefore, leakage
of oil passing through the rocker shafts 33, 34 from the notches
33a, 34a can be suppressed. This structure allows the hollow
portions inside the rocker shaft 33, 34 to be increased in size,
effecting weight saving of the rocker shafts 33, 34.
[0059] Although in the multi-cylinder internal combustion engine 21
according to the embodiment of FIGS. 1-6b, the rocker shafts 33, 34
also pass through the rocker shaft support section 23ras, this
invention is not limited to that specific way the rocker shafts 33,
34 are supported. Also, although in this first embodiment, the
rocker shafts 33, 34 extending on both axial sides of the cam shaft
bearing section 26ib to be disposed parallel to the cam shafts 24,
25, this invention is not limited to the foregoing embodiment.
Embodiment of FIGS. 7 and 8
[0060] To this end, FIGS. 7 and 8 show another embodiment of the
invention. In describing this embodiment as well as those
following, the same parts as in previous embodiments of the
invention are designated by same reference numerals and description
will not be repeated, except as necessary for those skilled in the
art to understand and practice this and other additional
embodiments to be described.
[0061] This embodiment employs cam carriers identified generally by
the reference numeral 123 (only one of which is shown). In this
embodiment rocker shaft through-holes 123e, 123i are formed in
respective rocker shaft support sections 123erj and 123irj
positioned transversely outside a cam shaft bearing section,
indicated generally at 124. The central part of this cam shaft
bearing section 124 includes a portion defining a cylindrical
opening 125 for receiving a respective collar (not shown) like the
collars 36 of the previously described embodiment to hold a
respective spark plug. These components are formed so that the
linear thermal expansion coefficient of the collar 36 is different
(either larger or smaller) than that of the cam carrier 123, as
described in the previous embodiment. This will insure that the
collar 36 can be attached to and detached from the cam carrier 123
in a cold or a hot environment and subsequently the collar 36 will
be prevented from slipping off the cam carrier 123 at room
temperature.
[0062] In this embodiment, unlike that of FIGS. 1-6 the spark plug
collar receiving opening 125 is separated from the rocker arm
support sections 123irj and 123erj by the remainder of the cam
shaft bearing section 124. Other effects and functions are
substantially the same as in the first described embodiment of this
FIGS. 1-6, except that while the rocker shafts 33, 34 on which the
rocker arms 31, 32 rotate, are disposed inwardly in the first
embodiment, they are dispose outwardly in this embodiment.
Embodiment of FIGS. 9-14
[0063] Another embodiment of the invention is illustrated in FIGS.
9-14. Again where the elements of this embodiment are the same or
substantially the same as components already described, those
components have been identified by the same reference numerals as
previously employed. Also and for the sake of brevity these
components will be described only insofar as is necessary for those
skilled in the art to practice this embodiment.
[0064] The engine associated with this embodiment and more
particularly a cylinder head assembly thereof is indicated
generally by the reference numeral 201. The cylinder head 201 of
the multi-cylinder internal combustion engine in this embodiment is
different from the multi-cylinder internal combustion engine 21 of
first described embodiment of FIGS. 1-6b in the following aspects
and is also shown in a reversed position therefrom.
[0065] Primarily, rather than operating all of the intake and
exhaust valves associated with the same cylinder, the cam carriers,
except for those at the ends of the of the cylinder head, as to be
described shortly, operate one intake valve and one exhaust valve
of pairs of the adjacent cylinders spanned by these paired, middle
or central cam carriers, each of which is indicated generally by
the reference numeral 223m.
[0066] Like the previous embodiments and as best seen in FIGS.
10-12, these middle cam carriers 223m are comprised of a single
lower piece 223ma to which a pair of respective upper bearing
halves 223mib and 223meb is affixed by threaded fasteners 227.
These middle cam carriers 223m are each disposed between adjacent
centermost cylinders, as should be readily apparent from FIG. 9.
The construction for the support at the ends of the cylinder head
assembly 201 will, as has been noted, described later.
[0067] Continuing to refer primarily to FIGS. 10-12, pairs of
adjacent middle intake rocker arms 231c are supported on an intake
pivot shaft 224 received in a suitable bore formed in single lower
pieces 223ma of the middle cam carriers 223m. The inner ends of
these middle intake rocker arms 231c are retained in slots 223mas
formed at one side of the single lower piece 223ma.
[0068] In a like manner adjacent middle exhaust rocker arms 232c
are supported on an exhaust pivot shaft 234 recieved in a suitable
bore formed in the single lower pieces 223ma of the middle cam
carriers 223m. The inner ends of these middle exhaust rocker arms
232c are also retained in slots 223mas formed in the single lower
pieces 223ma of the middle cam carriers 223m.
[0069] The middle intake rocker arm shafts 224 and the middle
exhaust rocker arm shafts 234 are retained in axial position in the
slots 223mas and the single lower pieces 223ma of the middle cam
carriers 223m in the manner now to be described. As with all of the
embodiments described, threaded fasteners pass through bored holes
in the respective components of the cam carriers of the
embodiments. These bored holes in this embodiment are identified by
the reference numerals 228. As with the previously described
embodiments, the body of the cylinder head (201 in this embodiment)
has tapped holes to threadingly engage and retrain the threaded
lower ends of the fasteners 227. In addition and as best shown in
FIG. 12, these fasteners 227 pass through a portion of the bores
228 which intersect the pivot shafts 224 and 234 and around which
sleeves 229 are positioned to axially restrain them axially. These
sleeves 229 are also received in notches 230 formed in the pins 224
and 234 to axially restrain them within their respective bores.
[0070] From the description of this embodiment as already made, it
should be obvious to those skilled in the art, that provision must
be made for operating one intake valve and one exhaust valve for
the cylinders at opposite ends of the cylinder head 201. This
structure may be best understood by reference to FIGS. 13 and 14.
As already noted, FIG. 13 is a top plan view showing only this
portion of the structure of this embodiment and FIG. 14 is a cross
sectional view of the structure shown in FIG. 13 taken through the
pivotal axes of the rocker arms. The end intake rocker arms are
identified by the reference numerals 231e and the end exhaust
rocker arms are identified by the reference numeral 232e.
[0071] Referring now first to FIG. 13 and remembering its relation
to FIG. 9, at the respective left and right ends of the cylinder
head 201, end cam carriers 223el and 223er are provided to support
the respective end intake rocker arms 231e and end exhaust rocker
arms 232e for the cylinders provided at the left and right ends of
the cylinder head 201. These cam carriers 223el, 223er are each
formed generally in the same shape as the middle cam carriers 223m
but are shorter and less complex in some regards because they each
only journal one intake rocker arm 231e and one exhaust rocker arm
232e. Furthermore and as best seen in FIG. 14, the respective
rocker shafts 224e and 234e are shorter in length than the rocker
shafts 224 and 234 of the middle cam carriers since they only carry
one rocker arm.
[0072] Since the end cam carriers 223el and 223er journal
respective ends of the camshafts 24 and 25 they are each provided
with respective upper pieces 223eib and 223eeb that are fixed in
place by the fasteners 227 in the manner as discussed with the
other embodiments.
[0073] The lubrication system associated with the end cam carriers
223el and 223er is generally the same as that for the middle cam
carriers and their associated components, as shown in FIG. 14,
except for the fact that it is only for two valves rather than four
valves and thus it will not be described again in detail, but like
components are identified by like reference numerals.
[0074] In the multi-cylinder internal combustion engine of the
previous embodiments the cam carriers have been associated
respectively with a single cylinder. They have thus been centered
over the axis of the associated cylinder bore of the cylinder
block. Thus the collars 36 have passed through the central openings
that receive them. Also, as has been noted, this affords the
opportunity to use materials of different thermal expansion to
assure retention. The same effect is obtained with this embodiment,
as will now be described.
[0075] As described, the middle cam carriers 223m are each mounted
between adjacent cylinders. In addition these middle cam carriers
223m have a length that is somewhat less than the distance between
adjacent cylinder axes. Thus there is in fact a gap between
adjacent ends of the middle cam carriers 223m. In addition there is
a like gap between the end cam carriers 223el 223er and their
adjacent middle cam carriers 223m. Thus the adjacent ends are
formed with semi-cylindrical notches 241 that are complimentary to
the lower portions of the cylindrical collars 36. Therefore, even
in the multi-cylinder internal combustion engine 201 having an
ignition plug 37 dispose above each cylinder, the cam carriers 223m
can be configured such that they don't obstruct the disposition of
ignition plugs 37. Thus, the degree of freedom in designing can be
increased for the disposition of cam carriers 223m in the
multi-cylinder internal combustion engine 201.
[0076] As has already been described in detail and thus to
summarize, the connection between the collars 216, cylinder head
201 and various cam carriers 223m, 223el and 223er as well as the
interengagement between the various rocker arm shafts and the
fasteners maintains all of the components in their desired
relationship and reduces the labor and machining to produce the
engines, as described
[0077] Of course those skilled in the art will readily understand
that the described embodiments are only exemplary of forms that the
invention may take and that various changes and modifications may
be made without departing from the spirit and scope of the
invention, as defined by the appended claims.
* * * * *