U.S. patent application number 15/337243 was filed with the patent office on 2017-05-18 for outboard motor.
The applicant listed for this patent is YAMAHA HATSUDOKI KABUSHIKI KAISHA. Invention is credited to Satoru HAMADA, Kazuya TAKEUCHI.
Application Number | 20170137102 15/337243 |
Document ID | / |
Family ID | 58691990 |
Filed Date | 2017-05-18 |
United States Patent
Application |
20170137102 |
Kind Code |
A1 |
HAMADA; Satoru ; et
al. |
May 18, 2017 |
OUTBOARD MOTOR
Abstract
In an outboard motor, a feed passage, through which a
lubricating oil that flows upward from a gear mechanism due to
rotation of the gear mechanism is fed upward from a gear chamber,
includes a first feed passage, extending from the gear chamber to a
connection passage via a first upstream passage, a spiral passage,
and an interior of an upper bearing, in that order, and a second
feed passage, extending from the first upstream passage to the
connection passage while bypassing the spiral passage via a bypass
passage. The bypass passage is positioned farther outward than the
spiral passage in a radial direction of the driveshaft. A diameter
of a cross section of the bypass passage that is orthogonal or
substantially orthogonal to a center line of the driveshaft is
smaller than a maximum diameter of the driveshaft.
Inventors: |
HAMADA; Satoru; (Shizuoka,
JP) ; TAKEUCHI; Kazuya; (Shizuoka, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
YAMAHA HATSUDOKI KABUSHIKI KAISHA |
Iwata-shi |
|
JP |
|
|
Family ID: |
58691990 |
Appl. No.: |
15/337243 |
Filed: |
October 28, 2016 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B63H 23/04 20130101;
F16N 7/366 20130101; F16N 2013/205 20130101; F01M 2011/026
20130101; F01M 11/02 20130101; B63H 20/002 20130101 |
International
Class: |
B63H 20/00 20060101
B63H020/00; F01M 11/02 20060101 F01M011/02; B63H 23/04 20060101
B63H023/04 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 12, 2015 |
JP |
2015-222386 |
Claims
1. An outboard motor comprising: a prime mover; a driveshaft
extending in an up/down direction below the prime mover and to
which a rotation of the prime mover is transmitted; a gear
mechanism coupled to a lower end portion of the driveshaft and to
which a rotation of the driveshaft is transmitted; a propeller
shaft to which a rotation of the gear mechanism is transmitted; a
lower case in which the driveshaft is inserted and defining a gear
chamber that houses the gear mechanism and a lubricating oil; an
upper bearing positioned above the gear mechanism and rotatably
supporting the driveshaft inside the lower case; a feed passage
through which the lubricating oil that is made to flow upward from
the gear mechanism by rotation of the gear mechanism is fed upward
from the gear chamber; a return passage separate from the feed
passage and returning the lubricating oil, fed by the feed passage,
to the gear chamber; and a connection passage guiding the
lubricating oil from the feed passage to the return passage;
wherein the feed passage includes: a first feed passage including a
first upstream passage extending upward from the gear chamber and a
spiral passage spirally surrounding the driveshaft below the upper
bearing, the first feed passage extending from the gear chamber to
the connection passage via the first upstream passage, the spiral
passage, and an interior of the upper bearing in that order; and a
second feed passage including a bypass passage separated from the
spiral passage, the second feed passage extending from the first
upstream passage to the connection passage and bypassing the spiral
passage by the bypass passage; the bypass passage is positioned
farther outward than the spiral passage in a radial direction of
the driveshaft; and a diameter of a cross section of the bypass
passage that is orthogonal or substantially orthogonal to a center
line of the driveshaft is smaller than a maximum diameter of the
driveshaft.
2. The outboard motor according to claim 1, wherein a flow passage
area of the bypass passage is greater than a flow passage area of
the spiral passage.
3. The outboard motor according to claim 1, wherein the feed
passage includes a merging portion disposed on an upstream side of
the connection passage and connecting the first feed passage and
the second feed passage to each other.
4. The outboard motor according to claim 3, wherein the merging
portion connects the first feed passage and the second feed passage
to each other at a position that is upstream of the upper bearing
and downstream of the spiral passage.
5. The outboard motor according to claim 1, wherein the second feed
passage includes at least one outer peripheral passage that
bypasses the interior of the upper bearing.
6. The outboard motor according to claim 5, wherein a portion of
the at least one outer peripheral passage is defined by an outer
peripheral surface of the upper bearing.
7. The outboard motor according to claim 5, wherein the at least
one outer peripheral passage includes a plurality of outer
peripheral passages spaced apart in a circumferential direction of
the driveshaft.
8. The outboard motor according to claim 1, wherein the connection
passage includes a first connection passage and a second connection
passage that differ from each other; the first connection passage
guides the lubricating oil from the first feed passage to the
return passage; and the second connection passage guides the
lubricating oil from the second feed passage to the return
passage.
9. The outboard motor according to claim 8, wherein the second feed
passage is connected to both the first connection passage and the
second connection passage.
10. The outboard motor according to claim 1, wherein the spiral
passage includes a spiral groove extending in the up/down direction
and spirally surrounds the center line of the driveshaft; and at
least a portion of the bypass passage is positioned at a height
between an upper end and a lower end of the spiral groove.
11. The outboard motor according to claim 10, wherein both an upper
end and a lower end of the bypass passage are positioned at heights
between the upper end and the lower end of the spiral groove.
12. The outboard motor according to claim 1, wherein the bypass
passage is integral and unitary with the lower case.
13. The outboard motor according to claim 1, wherein the connection
passage includes an upstream end connected to the feed passage and
a downstream end connected to the return passage; and at least one
of either of the upstream end and the downstream end of the
connection passage is positioned above an oil surface of the
lubricating oil when the prime mover is stopped.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to an outboard motor.
[0003] 2. Description of the Related Art
[0004] US2013/0052891A1 discloses an outboard motor including a
gear case disposed underwater and a gear mechanism housed inside
the gear case and lubricated by a lubricating oil. The lubricating
oil is stored in a gear chamber provided in the gear case. The
lubricating oil inside the gear chamber is thrown upward by
rotation of a bevel gear included in the gear mechanism and fed
upward to an oil slinger provided at a driveshaft. The lubricating
oil suppled to the oil slinger is guided upward along a spiral oil
groove by rotation of the driveshaft. The lubricating oil is thus
supplied to an internal gap of a tapered roller bearing that
rotatably supports the driveshaft. The lubricating oil that has
passed upwardly through the tapered roller bearing is returned to
the gear chamber by a main lubrication circulation portion and a
sub lubrication circulation portion.
[0005] JP S57182595 A discloses an example of a conventional
circulation path for a lubricating oil. As in US2013/0052891A1, the
lubricating oil inside a gear chamber of JP S57182595 A is fed
upward by rotations of a pinion, a forward drive gear, and a
reverse drive gear. The lubricating oil is fed from the gear
chamber to an insertion space via a lower communication passage
extending upward from the gear chamber. A sleeve surrounding a
driveshaft is disposed at the insertion space. The lubricating oil
supplied to the insertion space enters inside the sleeve from an
opening portion that opens at an outer peripheral surface of the
sleeve and is fed upward by a spiral lead portion provided on an
inner peripheral surface of the sleeve. The lubricating oil is
supplied to an upper bearing via an oil feed portion extending
upward from the lead portion. The lubricating oil supplied to the
upper bearing flows downward between an inner peripheral surface of
the insertion space and the outer peripheral surface of the sleeve
and is discharged from the insertion space via an upper
communication passage positioned at a height between the upper
bearing and the lead portion. An outer diameter of a passage
defined between the inner peripheral surface of the insertion space
and the outer peripheral surface of the sleeve is greater than an
outer diameter of the driveshaft.
[0006] With a conventional outboard motor, a lubricating oil is
circulated in a circulation path provided in an interior of a lower
case that is disposed underwater. Gears, bearings, etc., are thus
lubricated and these members are cooled by the lubricating oil. The
lubricating oil that has cooled the gears, etc., is cooled by the
lower case, etc., while circulating through the circulation path. A
temperature of the lubricating oil is thus maintained within an
appropriate range. However, since a heat amount generated at the
lower case increases as gears and other rotating bodies are made
larger and outboard motors are made higher in output, a temperature
increase of the lubricating oil must be minimized to prevent the
temperature of the lubricating oil from exceeding the appropriate
range.
[0007] A temperature increase of the lubricating oil is suppressed
by increasing a total amount of the lubricating oil circulating
inside the lower case because a heat capacity of the lubricating
oil as a whole is thus increased. Also, a temperature increase of
the lubricating oil is decreased without increasing the total
amount of the lubricating oil by improving circulation efficiency
of the lubricating oil, that is, by preventing stagnation of the
lubricating oil or increasing a circulation flow rate of the
lubricating oil because heat radiation from the lubricating oil
will then be performed effectively.
[0008] However, with the method of increasing the total amount of
the lubricating oil, an oil storage chamber storing the lubricating
oil inside the lower case must be enlarged. Depending on the
outboard motor, it may not be possible to provide a lower case with
such a large oil storage chamber. Also, when the lower case is
enlarged to enlarge the oil storage chamber, the outboard motor is
lowered in propulsion efficiency because of increased resistance of
water applied to the outboard motor.
[0009] With the outboard motor of US2013/0052891A1, two lubrication
circulation portions (the main lubrication circulation portion and
the sub lubrication circulation portion) that return the
lubricating oil that has lubricated the tapered roller bearing to
the gear chamber are provided to smoothly circulate the lubricating
oil without enlarging the gear case. However, the circulation flow
rate of the lubricating oil is dependent on a supply capacity of
the oil slinger that feeds the lubricating oil to the tapered
roller bearing and therefore the lubricating oil cannot be
circulated at a flow rate exceeding the supply capacity of the oil
slinger. That is, unless the lubricating oil supply capacity at the
oil slinger is increased, the circulation flow rate of the
circulation system as a whole cannot be increased even if the sub
lubrication circulation portion is added.
[0010] A flow rate of the lubricating oil supplied to the oil
slinger by rotation of the bevel gear and a flow rate of the
lubricating oil fed by the oil slinger both increase with increase
of engine speed. However, during high speed rotation, the flow rate
of the lubricating oil supplied to the oil slinger by rotation of
the bevel gear becomes greater than the flow rate of the
lubricating oil fed by the oil slinger. Even when the flow rate of
the lubricating oil supplied to the oil slinger exceeds the flow
rate of the lubricating oil fed by the oil slinger, the lubricating
oil will not be circulated at a flow rate exceeding the supply
capacity of the oil slinger. Further, in this case, the lubricating
oil stagnates between the bevel gear and the oil slinger, so that a
pressure of the lubricating oil increases and the temperature of
the lubricating oil increases.
[0011] Similarly with the outboard motor of JP S57182595 A, the
lubricating oil cannot be circulated at a flow rate exceeding a
supply capacity of the spiral lead portion.
SUMMARY OF THE INVENTION
[0012] In order to overcome the previously unrecognized and
unsolved challenges described above, a preferred embodiment of the
present invention provides an outboard motor including a prime
mover, a driveshaft extending in an up/down direction below the
prime mover and to which a rotation of the prime mover is
transmitted, a gear mechanism coupled to a lower end portion of the
driveshaft and to which a rotation of the driveshaft is
transmitted, a propeller shaft to which a rotation of the gear
mechanism is transmitted, a lower case defining a gear chamber
housing the gear mechanism and a lubricating oil and in which the
driveshaft is inserted, an upper bearing positioned above the gear
mechanism and rotatably supporting the driveshaft inside the lower
case, a feed passage through which the lubricating oil that is made
to flow upward from the gear mechanism by rotation of the gear
mechanism is fed upward from the gear chamber, a return passage
separate from the feed passage and returning the lubricating oil,
fed by the feed passage, to the gear chamber, and a connection
passage guiding the lubricating oil from the feed passage to the
return passage.
[0013] The feed passage includes a first feed passage, including a
first upstream passage, extending upward from the gear chamber, and
a spiral passage, spirally surrounding the driveshaft below the
upper bearing, and extending from the gear chamber to the
connection passage via the first upstream passage, the spiral
passage, and an interior of the upper bearing in that order, and a
second feed passage, including a bypass passage, separated from the
spiral passage, and extending from the first upstream passage to
the connection passage while bypassing the spiral passage by the
bypass passage. The bypass passage is positioned farther outward
than the spiral passage in a radial direction of the driveshaft. A
diameter of a cross section of the bypass passage that is
orthogonal or substantially orthogonal to a center line of the
driveshaft is smaller than a maximum diameter of the driveshaft.
The "diameter of a cross section of the bypass passage that is
orthogonal or substantially orthogonal to a center line of the
driveshaft" means a maximum value of a straight line joining two
points on a contour line of the cross section of the bypass
passage. The cross section of the bypass passage may be circular,
elliptical, or polygonal or may have a C shape extending in a
circumferential direction of the driveshaft.
[0014] With the present arrangement, when the prime mover rotates
the driveshaft, the gear mechanism housed in the gear chamber of
the lower case rotates and the lubricating oil inside the gear
chamber is fed upward. The lubricating oil is thus made to flow
through the first upstream passage, the spiral passage, and the
interior of the upper bearing of the first feed passage, in that
order. The second feed passage extends from the first upstream
passage to the connection passage while bypassing the spiral
passage by the bypass passage. A portion of the lubricating oil
flowing upward from the gear mechanism flows through the bypass
passage toward the connection passage without passing through the
spiral passage.
[0015] The bypass passage bypassing the spiral passage is thus
provided in the second feed passage and therefore a flow rate of
the lubricating oil flowing through a circulation path including
the gear chamber, the feed passage, the connection passage, and the
return passage is not restricted by the spiral passage. The
lubricating oil is thus circulated at a flow rate exceeding a
supply capacity of the spiral passage. Circulation efficiency of
the lubricating oil flowing through the circulation path is thus
improved and the lubricating oil inside the lower case is cooled
effectively.
[0016] A flow passage area of the bypass passage is preferably
greater than a flow passage area of the spiral passage.
[0017] With the present arrangement, the flow passage area of the
bypass passage bypassing the spiral passage is greater than the
flow passage area of the spiral passage. The lubricating oil is
thus guided through the bypass passage at a flow rate greater than
a flow rate of the lubricating oil flowing through the spiral
passage. The circulation efficiency of the lubricating oil is thus
improved.
[0018] The feed passage preferably includes a merging portion
disposed on an upstream side of the connection passage and
connecting the first feed passage and the second feed passage to
each other. The merging portion may connect the first feed passage
and the second feed passage to each other either upstream or
downstream the upper bearing.
[0019] With the present arrangement, the first feed passage and the
second feed passage are connected to each other by the merging
portion at a position upstream of the connection passage and
therefore excess lubricating oil is released from one of either of
the first feed passage and the second feed passage to the other of
either of the first feed passage and the second feed passage. An
increase in pressure of the lubricating oil at the first feed
passage and the second feed passage is thus significantly reduced
or prevented.
[0020] The merging portion preferably connects the first feed
passage and the second feed passage to each other at a position
that is upstream the upper bearing and downstream the spiral
passage.
[0021] With the present arrangement, the lubricating oil that has
bypassed the spiral passage is supplied from the second feed
passage to the first feed passage at a position that is upstream
the upper bearing and downstream the spiral passage. The
lubricating oil supplied to the first feed passage at the merging
portion is supplied to an internal gap of the upper bearing that is
positioned downstream the merging portion. A flow rate of the
lubricating oil supplied to the upper bearing is thus increased.
Further, the excess lubricating oil is released from the first feed
passage to the second feed passage via the merging portion, so that
the pressure of the lubricating oil is prevented from increasing at
a portion between the upper bearing and the spiral passage.
[0022] The second feed passage preferably further includes at least
one outer peripheral passage that bypasses the interior of the
upper bearing. Preferably, a flow passage area of the at least one
outer peripheral passage is greater than the internal gap of the
upper bearing. Specifically, if the at least one outer peripheral
passage is a plurality of outer peripheral passages, a sum of flow
passage areas of the plurality of outer peripheral passages is
preferably greater than the internal gap of the upper bearing. If
the at least one outer peripheral passage is a single outer
peripheral passage, the flow passage area of the outer peripheral
passage is preferably greater than the internal gap of the upper
bearing.
[0023] With the present arrangement, the second feed passage
extends toward the connection passage while bypassing the internal
gap of the upper bearing by the outer peripheral passage. By
bypassing the internal gap of the upper bearing that is small in
flow passage area, a flow rate of the lubricating oil flowing
through the second feed passage is prevented from being restricted
by the internal gap of the upper bearing. The circulation
efficiency of the lubricating oil is thus improved and the
lubricating oil is cooled effectively.
[0024] A portion of the outer peripheral passage is preferably
defined by an outer peripheral surface of the upper bearing.
[0025] With the present arrangement, an inner wall surface of the
outer peripheral passage that defines the outer peripheral passage
includes the outer peripheral surface of the upper bearing, and the
outer peripheral surface of the upper bearing defines a portion of
the outer peripheral passage. The lubricating oil inside the outer
peripheral passage flows while being in contact with the outer
peripheral surface of the upper bearing. The upper bearing is thus
cooled by the lubricating oil flowing through the outer peripheral
passage. The upper bearing is thus cooled while improving the
circulation efficiency of the lubricating oil.
[0026] The at least one outer peripheral passage preferably
includes a plurality of outer peripheral passages spaced apart in
the circumferential direction of the driveshaft.
[0027] With the present arrangement, the second feed passage is
provided with the plurality of outer peripheral passages that
bypass the interior of the upper bearing. A flow passage area of
the second feed passage is thus increased and the circulation
efficiency of the lubricating oil is thus improved further.
[0028] The connection passage preferably includes a first
connection passage and a second connection passage that differ from
each other. The first connection passage guides the lubricating oil
from the first feed passage to the return passage and the second
connection passage guides the lubricating oil from the second feed
passage to the return passage.
[0029] With the present arrangement, the lubricating oil inside the
first feed passage is guided to the return passage by the first
connection passage and the lubricating oil inside the second feed
passage is guided to the return passage by the second connection
passage. The first connection passage and the second connection
passage are separate passages that do not intersect each other. A
flow passage area of the connection passage is thus increased and
the flow rate of the lubricating oil flowing through the
circulation path is prevented from being restricted by the
connection passage.
[0030] The first feed passage is preferably connected to just the
first connection passage and the second feed passage may be
connected to just the second connection passage. Or, the second
feed passage may be connected to both the first connection passage
and the second connection passage.
[0031] When the second feed passage is connected to both the first
connection passage and the second connection passage, the second
feed passage includes a portion intersecting the first connection
passage and a portion intersecting the second connection passage.
When the amount of lubricating oil flowing through the second feed
passage is high, a portion of the lubricating oil flows from the
second feed passage to the second connection passage and the
remaining lubricating oil flows from the second feed passage to the
first connection passage. A portion of the lubricating oil flowing
through the second feed passage is thus released to the first
connection passage and the circulation flow rate of the lubricating
oil is thus prevented from being restricted by the second
connection passage.
[0032] The spiral passage preferably includes a spiral groove
extending in the up/down direction while spirally surrounding the
center line of the driveshaft. At least a portion of the bypass
passage is preferably positioned at a height between an upper end
and a lower end of the spiral groove. For example, both an upper
end and a lower end of the bypass passage may be positioned at
heights between the upper end and the lower end of the spiral
groove. The spiral groove may be provided at an outer peripheral
surface of the driveshaft or may be provided on a circular or
substantially circular cylindrical surface surrounding the
driveshaft. The circular cylindrical surface may be a portion of
the lower case or may be a portion of a member separate from the
lower case.
[0033] The bypass passage is preferably integral and unitary with
the lower case.
[0034] The connection passage preferably includes an upstream end
connected to the feed passage and a downstream end connected to the
return passage. At least one of either of the upstream end and the
downstream end of the connection passage may be positioned above an
oil surface of the lubricating oil when the prime mover is
stopped.
[0035] The above and other elements, features, steps,
characteristics and advantages of the present invention will become
more apparent from the following detailed description of the
preferred embodiments with reference to the attached drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0036] FIG. 1 is a schematic view of a left side of an outboard
motor according to a preferred embodiment of the present
invention.
[0037] FIG. 2 is a vertical sectional view showing an interior of a
lower case provided in the outboard motor.
[0038] FIG. 3 is a partially enlarged view of FIG. 2.
[0039] FIG. 4A is a view of a vertical section, including a center
line of a driveshaft and orthogonal or substantially orthogonal to
a center line of a propeller shaft, as viewed from the rear.
[0040] FIG. 4B is a horizontal section taken along line B-B in FIG.
4A.
[0041] FIG. 4C is a horizontal section taken along line C-C in FIG.
4A.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0042] An outboard motor 2 in a reference orientation shall be
described below. The reference orientation is an orientation where
a rotational axis of a propeller shaft 7 extends horizontally in a
front/rear direction.
[0043] FIG. 1 is a schematic view of a left side of an outboard
motor 2 according to a preferred embodiment of the present
invention. FIG. 2 is a vertical sectional view showing an interior
of a lower case 17 provided in the outboard motor 2. FIGS. 1 and 2
show a state in which the outboard motor 2 is in the reference
orientation.
[0044] As shown in FIG. 1, a vessel propulsion device 1 includes
the outboard motor 2 that generates a thrust that propels a vessel
and a suspension system mounting the outboard motor 2 to a hull
H1.
[0045] The outboard motor 2 includes a prime mover 3 that generates
motive power to rotate a propeller 8, and a power transmission
apparatus that transmits the motive power of the prime mover 3 to
the propeller 8. Rotation of the prime mover 3 is transmitted to
the propeller 8 via a driveshaft 5, a gear mechanism 6, and a
propeller shaft 7 of the power transmission apparatus. The
propeller 8 is thus made to rotate together with the propeller
shaft 7 to generate a thrust that propels a vessel forward or
rearward.
[0046] The suspension system includes a pair of clamp brackets 9,
fixed to a transom provided at a rear portion of the hull H1, and a
tilting shaft 10, supported by the pair of clamp brackets 9 in an
orientation of extending horizontally in the right/left direction.
The suspension system further includes a swivel bracket 11,
supported by the pair of clamp brackets 9 via the tilting shaft 10,
and a steering shaft 12, supported by the swivel bracket 11 in an
orientation of extending vertically in an up/down direction.
[0047] The outboard motor 2 is coupled to an upper end portion and
a lower end portion of the steering shaft 12. The steering shaft 12
is rotatable with respect to the swivel bracket 11 around a center
line of the steering shaft 12 that extends in the up/down
direction. The swivel bracket 11 is rotatable with respect to the
clamp brackets 9 around a center line of the tilting shaft 10 that
extends in the right/left direction. The outboard motor 2 is
rotatable in the right/left direction with respect to the hull H1
and is rotatable in the up/down direction with respect to the hull
H1.
[0048] The vessel propulsion device 1 includes a steering mechanism
pivoting the outboard motor 2 around the steering shaft 12 with
respect to the clamp brackets 9, and a power trim and tilt
mechanism (hereinafter referred to as "PTT") pivoting the outboard
motor 2 around the tilting shaft 10 with respect to the clamp
brackets 9. A hydraulic cylinder 13 of the PTT is disposed between
the pair of clamp brackets 9. The PTT positions the outboard motor
2 at any position from a tilt-down position (position shown in FIG.
1) at which the propeller 8 is positioned underwater to a tilt-up
position at which the propeller 8 is positioned above a water
surface.
[0049] The outboard motor 2 includes a cowling 14 that accommodates
the prime mover 3 and a casing that accommodates the power
transmission apparatus. The casing includes an exhaust guide 15
disposed below the prime mover 3, an upper case 16 disposed below
the exhaust guide 15, and a lower case 17 disposed below the upper
case 16. The lower case 17 includes a circular or substantially
circular cylindrical torpedo portion 17a extending in the
front/rear direction. The torpedo portion 17a is a portion that is
disposed underwater. The torpedo portion 17a includes a closed
front end, a rearwardly open rear end, and a tapered outer surface
that narrows as the front end is approached.
[0050] The driveshaft 5 extends in the up/down direction inside the
exhaust guide 15, the upper case 16, and the lower case 17. The
gear mechanism 6 is coupled to a lower end portion of the
driveshaft 5. The propeller shaft 7 extends in the front/rear
direction inside the torpedo portion 17a. The gear mechanism 6 is
coupled to a front end portion of the propeller shaft 7. The
propeller 8 is removably mounted to a rear end portion of the
propeller shaft 7 that projects rearward from a rear end of the
torpedo portion 17a. The driveshaft 5 is rotatable with respect to
the casing around a center line (drive axis Ad) of the driveshaft
5. The propeller shaft 7 is rotatable with respect to the casing
around a center line (propeller axis Ap) of the propeller shaft
7.
[0051] The prime mover 3 is an engine (internal combustion engine).
The prime mover 3 may be an electric motor or may include both an
engine and an electric motor. A rear end portion of the propeller 8
defines an exhaust port 19 that discharges exhaust gas underwater.
The exhaust gas generated at the prime mover 3 is discharged
underwater from the exhaust port 19 via an exhaust passage 18
provided in an interior of the outboard motor 2. The prime mover 3
is disposed on the exhaust guide 15 defining a prime mover
supporting member in an orientation where the rotational axis Ac of
the crankshaft 4 is vertical or substantially vertical. A direction
of the rotation transmitted from the driveshaft 5 to the propeller
shaft 7 is switched by the gear mechanism 6. The propeller 8
rotates in the same direction as the propeller shaft 7. A direction
of rotation of the propeller 8 is thus switched between a forward
rotation direction and a reverse rotation direction. A direction of
the thrust is thus switched.
[0052] As shown in FIG. 2, the gear mechanism 6 includes a
cylindrical or substantially cylindrical pinion 21 that rotates
around the drive axis Ad together with the driveshaft 5, a
cylindrical or substantially cylindrical front gear 22 and rear
gear 23 engaged with the pinion 21, and a cylindrical or
substantially cylindrical dog clutch 24 that selectively engages
with one of either of the front gear 22 and the rear gear 23. The
outboard motor 2 includes a shift mechanism that moves the dog
clutch 24 in an axial direction (front/rear direction) of the
propeller shaft 7 to switch a shift state of the gear mechanism
6.
[0053] The pinion 21 is coupled to a lower end portion of the
driveshaft 5. The driveshaft 5 is inserted in a shaft insertion
hole 25 provided in the lower case 17. The driveshaft 5 is
rotatably supported by the lower case 17 via an upper bearing B1
and a lower bearing B2 that surround the driveshaft 5. The pinion
21 is disposed below the lower bearing B2, and the upper bearing B1
is disposed above the lower bearing B2.
[0054] Each of the upper bearing B1 and the lower bearing B2 may be
any of a ball bearing, a roller bearing, and a needle bearing, for
example. FIG. 2 shows an example where the upper bearing B1 is a
double-row tapered roller bearing and the lower bearing B2 is a
needle bearing. The upper bearing B1 includes an inner ring
surrounding the driveshaft 5, an outer ring surrounding the inner
ring, and a plurality of rollers interposed between the inner ring
and the outer ring. The lower bearing B2 includes an outer ring
surrounding the driveshaft 5 and a plurality of needles interposed
between the outer ring and the driveshaft 5.
[0055] The inner ring of the upper bearing B1 is sandwiched in an
axial direction of the driveshaft 5 by an annular nut 26 mounted to
the driveshaft 5 and an annular step portion provided at the
driveshaft 5. The outer ring of the upper bearing B1 is sandwiched
in the axial direction of the driveshaft 5 by an annular fixing
ring 27 mounted to an inner peripheral surface of the shaft
insertion hole 25 and an annular step portion provided at the shaft
insertion hole 25. The fixing ring 27 surrounds a nut 26 across an
interval in a radial direction of the driveshaft 5. The nut 26 and
the fixing ring 27 are positioned between the upper bearing B1 and
a shaft cap 28. An upper end of the shaft insertion hole 25 is
closed by the cylindrical shaft cap 28 that surrounds the
driveshaft 5.
[0056] The front gear 22 is disposed farther to the front than the
drive axis Ad. The rear gear 23 is disposed farther to the rear
than the drive axis Ad. The dog clutch 24 is disposed between the
front gear 22 and the rear gear 23. A front end portion of the
propeller shaft 7 is inserted inside the cylindrical front gear 22,
rear gear 23, and dog clutch 24. The front gear 22 and the rear
gear 23 are supported by the lower case 17 so as to be rotatable
around the propeller axis Ap. When the prime mover 3 rotates the
driveshaft 5, the rotation of the pinion 21 defining a drive gear
is transmitted to the front gear 22 and the rear gear 23 defining
driven gears and the front gear 22 and the rear gear 23 rotate in
mutually opposite directions.
[0057] The front gear 22 is rotatably supported by the lower case
17 via a front bearing B3 that surrounds the front gear 22. The
rear gear 23 is rotatably supported by the lower case 17 via a rear
bearing B4 that surrounds the rear gear 23. The front bearing B3 is
inserted inside the torpedo portion 17a, and the rear bearing B4 is
inserted inside a cylindrical or substantially cylindrical bearing
housing 29 surrounding the propeller shaft 7. The rear bearing B4
is supported by the lower case 17 via the bearing housing 29.
[0058] The dog clutch 24 is splined to the propeller shaft 7. The
dog clutch 24 is movable in an axial direction of the propeller
shaft 7 with respect to the propeller shaft 7 and rotates
integrally with the propeller shaft 7 around the propeller axis Ap.
The dog clutch 24 includes a front engaging portion 24a facing an
engaging portion of the front gear 22 and a rear engaging portion
24b facing an engaging portion of the rear gear 23. The dog clutch
24 is movable along the propeller shaft 7 in the front/rear
direction between a forward rotation position at which the front
engaging portion 24a engages with the engaging portion of the front
gear 22 and a reverse rotation position at which the rear engaging
portion 24b engages with the engaging portion of the rear gear 23.
A position between the forward rotation position and the reverse
rotation position is a neutral position (position shown in FIG. 2)
at which the dog clutch 24 is not engaged with either of the front
gear 22 and the rear gear 23.
[0059] The pinion 21, the front gear 22, the rear gear 23, and the
dog clutch 24 are disposed inside a gear chamber 30 provided in the
torpedo portion 17a. The gear chamber 30 is defined by an inner
surface of the torpedo portion 17a. The gear chamber 30 is filled
with a lubricating oil (gear oil) that lubricates the gear
mechanism 6. The shaft insertion hole 25 is disposed above the gear
chamber 30. The shaft insertion hole 25 is connected to the gear
chamber 30 via a lower bearing bypass groove 57 provided around the
lower bearing B2. The lubricating oil is movable between the gear
chamber 30 and the shaft insertion hole 25 via the lower bearing
bypass groove 57.
[0060] The shift mechanism positions the dog clutch 24 at one shift
position among the forward rotation position, the reverse rotation
position, and the neutral position. The shift mechanism includes a
shift actuator 31 (see FIG. 1) driven in accordance with a shift
operation by a user and a shift rod 32 that is driven to rotate by
the shift actuator 31. The shift mechanism further includes a slide
shaft 33 driven in the front/rear direction by the shift rod 32 and
a coupling pin 34 coupling the slide shaft 33 and the dog clutch
24.
[0061] The shift rod 32 includes a rod portion 32a extending in the
up/down direction, a disk portion 32b disposed below the rod
portion 32a, and a crank portion 32c disposed below the disk
portion 32b. The rod portion 32a and the disk portion 32b are
coaxial and a portion (eccentric portion) of the crank portion 32c
is eccentric with respect to the rod portion 32a and the disk
portion 32b. An outer diameter of the disk portion 32b is greater
than an outer diameter of the rod portion 32a.
[0062] The rod portion 32a is positioned in front of the driveshaft
5 and is parallel or substantially parallel to the driveshaft 5.
The rod portion 32a is inserted in a rod insertion hole 36 provided
at the lower case 17. The rod insertion hole 36 extends in the
up/down direction along the rod portion 32a. An inner peripheral
surface of the rod insertion hole 36 surrounds the rod portion 32a
across an interval in a radial direction of the shift rod 32. The
rod portion 32a projects upward from an upper end of the rod
insertion hole 36. The upper end of the rod insertion hole 36 is
closed by an annular rod cap 35 that surrounds the rod portion 32a.
A lower end of the rod insertion hole 36 is closed by the disk
portion 32b. The rod portion 32a is supported by the lower case 17
via the rod cap 35 so as to be rotatable around a center line of
the rod portion 32a.
[0063] The inner peripheral surface of the rod insertion hole 36,
the rod cap 35, and the disk portion 32b define a shift chamber 37
that houses the rod portion 32a. The shift chamber 37 is positioned
above the gear chamber 30. The shift chamber 37 is connected to the
gear chamber 30 via a plurality of rod bypass grooves 38 disposed
around the disk portion 32b. The shift chamber 37 is also connected
to the gear chamber 30 via a penetrating hole 39 penetrating
through a portion of the lower case 17, positioned between the
shift rod 32 and the pinion 21, in the front/rear direction. The
penetrating hole 39 is positioned between the shift rod 32 and the
pinion 21. The lubricating oil is movable between the gear chamber
30 and the shift chamber 37 via the rod bypass grooves 38 or the
penetrating hole 39.
[0064] The lubricating oil that lubricates the gears, bearings,
etc., is stored not only in the gear chamber 30 but also in the
shaft insertion hole 25 and the shift chamber 37. The gear chamber
30, the shaft insertion hole 25, and the shift chamber 37 define an
oil storage chamber storing the lubricating oil. When the prime
mover 3 is stopped and idle, an oil surface (oil level L1) of the
lubricating oil is positioned between an upper end of the upper
bearing B1 and a lower end of the upper bearing B1. That is, the
entire gear chamber 30 is filled with the lubricating oil and
portions of the shaft insertion hole 25 and the shift chamber 37
are filled with the lubricating oil. A position (height) of the oil
surface of the lubricating oil changes in accordance with a
temperature of the lubricating oil.
[0065] The slide shaft 33 includes a front shaft 33a mounted to the
crank portion 32c and a rear shaft 33b mounted to the coupling pin
34. The rear shaft 33b is inserted inside the propeller shaft 7
from the front of the propeller shaft 7, and the front shaft 33a
extends forward from the rear shaft 33b. The front shaft 33a
projects forward from a front end of the propeller shaft 7. The
crank portion 32c is mounted to the front shaft 33a at the front of
the propeller shaft 7.
[0066] When the user operates a shift lever provided at a vessel
operator compartment, the shift actuator 31 (see FIG. 1) causes the
shift rod 32 to pivot around the center line of the rod portion
32a. A portion of the crank portion 32c is eccentric with respect
to the rod portion 32a and therefore when the shift rod 32 pivots,
a portion of the crank portion 32c moves in the front/rear
direction. The front shaft 33a is thus pushed forward or rearward
by the crank portion 32c and moves in the front/rear direction.
Accordingly, the rear shaft 33b, the coupling pin 34, and the dog
clutch 24 move integrally in the front/rear direction. The dog
clutch 24 is thus disposed at one of the forward rotation position,
the reverse rotation position, and the neutral position.
[0067] The outboard motor 2 includes a water cooling apparatus that
cools respective portions of the outboard motor 2 including the
prime mover 3. The water cooling apparatus includes a first water
inlet 41 and a second water inlet 42 opening at an outer surface of
the outboard motor 2, a cooling water passage guiding the water
outside the outboard motor 2 that flowed into the first water inlet
41 and the second water inlet 42 to the respective portions of the
outboard motor 2, and a water pump 45 generating a suction force
that suctions the water outside the outboard motor 2 into the first
water inlet 41 and the second water inlet 42.
[0068] The water pump 45 that is driven by the prime mover 3 is
disposed on the cooling water passage provided in an interior of
the outboard motor 2. The cooling water passage includes a first
water supply passage 43 and a second water supply passage 44, which
guide the water outside the outboard motor 2 to the respective
portions of the outboard motor 2, and a drain passage by which the
water that has cooled the respective portions of the outboard motor
2 is discharged to outside the outboard motor 2. The first water
supply passage 43 extends to the water pump 45 from the first water
inlet 41, disposed farther to the front than the driveshaft 5, and
the second water supply passage 44 extends to the water pump 45
from the second water inlet 42, disposed farther to the rear than
the driveshaft 5.
[0069] The water pump 45 includes an impeller 45a rotating together
with the driveshaft 5 and a pump case 45b that accommodates the
impeller 45a. When the prime mover 3 rotates the driveshaft 5, the
impeller 45a rotates with respect to the pump case 45b. The pump
case 45b is connected to the first water inlet 41 and the second
water inlet 42 via the first water supply passage 43 and the second
water supply passage 44 provided at the lower case 17. When the
prime mover 3 rotates the driveshaft 5, the water outside the
outboard motor 2 is suctioned as cooling water from the first water
inlet 41 and the second water inlet 42 and via the first water
supply passage 43 and the second water supply passage 44 into an
interior of the pump case 45b and fed to the prime mover 3, etc.,
from the pump case 45. The respective portions of the outboard
motor 2 are thus cooled.
[0070] The oil storage chamber that includes gear chamber 30, the
shaft insertion hole 25, and the shift chamber 37 is provided at
the lower case 17 that is disposed underwater. The lower case 17 is
preferably made of a metal that is higher in thermal conductivity
than a resin. The lubricating oil inside the oil storage chamber is
thus cooled by the water outside the outboard motor 2. Further,
just a first partition wall 17x of the lower case 17 is interposed
between the first water supply passage 43 and the shift chamber 37
and just a second partition wall 17y of the lower case 17 is
interposed between the second water supply passage 44 and the shaft
insertion hole 25. The lubricating oil inside the shift chamber 37
and the shaft insertion hole 25 are thus cooled effectively by the
cooling water flowing through the first water supply passage 43 and
the second water supply passage 44.
[0071] An oil circulation system circulating the lubricating oil
inside the outboard motor 2 shall now be described.
[0072] FIG. 3 is partially enlarged view of FIG. 2. FIG. 4A is a
view of a vertical section, including the drive axis Ad and
orthogonal or substantially orthogonal to the propeller axis Ap, as
viewed from the rear. FIG. 4B is a horizontal section taken along
line B-B in FIG. 4A, and FIG. 4C is a horizontal section taken
along line C-C in FIG. 4A.
[0073] As shown in FIG. 3, the oil circulation system includes a
feed passage 51, 52 feeding the lubricating oil upward from the
gear chamber 30, a return passage 55 returning the lubricating oil,
fed by the feed passage, to the gear chamber 30, and a connection
passage 53, 54 guiding the lubricating oil from the feed passage to
the return passage 55.
[0074] The feed passage includes a first feed passage 51 and a
second feed passage 52 that are separated from each other between
the upper bearing B1 and the lower bearing B2. The return passage
55 is defined by the shift chamber 37 and the plurality of rod
bypass grooves 38. The connection passage includes one or more
passages extending from the feed passage to the return passage 55.
FIG. 3 shows an example where the connection passage is provided
with a first connection passage 53 and a second connection passage
54.
[0075] The gear chamber 30, the feed passage, the connection
passage, and the return passage 55 define a circulation path
through which the lubricating oil inside the lower case 17 is
circulated. When the prime mover 3 rotates the driveshaft 5, the
lubricating oil inside the gear chamber 30 is fed upward by
rotation of the gear mechanism 6 and the lubricating oil is fed
upward by a screw pump defined by a spiral groove 59 and a pump
defining surface 60. The lubricating oil inside the gear chamber 30
is thus made to pass through the feed passage, the connection
passage, and the return passage 55 in that order and return to the
gear chamber 30. In this process, the lubricating oil is cooled by
the lower case 17, etc.
[0076] The first feed passage 51 includes a first upstream passage
56 extending upward from the gear chamber 30, a spiral first
intermediate passage 58 provided around the driveshaft 5, an
internal gap of the upper bearing B1, and a first downstream
passage 61 provided between the upper bearing B1 and the shaft cap
28. The internal gap of the upper bearing B1 is, for example, a gap
between the inner ring and the outer ring of the upper bearing B1.
The first intermediate passage 58 is an example of a spiral
passage.
[0077] The second feed passage 52 includes a second upstream
passage extending upward from the gear chamber 30, a second
intermediate passage 62 separated from the first intermediate
passage 58 by a portion of the lower case 17, and one or more
second downstream passages 63 extending upward from the second
intermediate passage 62 while bypassing an interior of the upper
bearing B1. FIG. 3 shows an example where two downstream passages
63 are provided and the second upstream passage is the same passage
as the first upstream passage 56. The second intermediate passage
62 is an example of a bypass passage, and each second downstream
passage 63 is an example of an outer peripheral passage.
[0078] The first upstream passage 56 is, for example, positioned in
front of the lower bearing B2. An upstream end of the first
upstream passage 56 that corresponds to a lower end is positioned
lower than the lower bearing B2 and faces an engaging portion of
the pinion 21 and the front gear 22 in the up/down direction. A
downstream end of the first upstream passage 56 that corresponds to
an upper end is positioned above the lower bearing B2 and faces an
outer peripheral surface of the driveshaft 5 in a radial direction.
As long as it extends upward from the gear chamber 30, the first
upstream passage 56 may be vertical or may be inclined.
[0079] The first upstream passage 56 is defined by an inner surface
of the lower bearing bypass groove 57 provided at the lower case 17
and an outer peripheral surface of the lower bearing B2. The lower
bearing bypass groove 57 extends in the up/down direction along the
outer peripheral surface of the lower bearing B2. The lower bearing
bypass groove 57 is recessed outward from a circular or
substantially circular cylindrical surface in contact with an outer
peripheral surface of the outer ring of the lower bearing B2. A
flow passage area of the first upstream passage 56 is greater than
a flow passage area of the first intermediate passage 58.
[0080] The first intermediate passage 58 extends in the up/down
direction along the driveshaft 5 while spirally surrounding the
driveshaft 5. The first intermediate passage 58 is defined by the
spiral groove 59 provided on an outer peripheral surface of a
groove defining portion 5a of the driveshaft 5 and the circular
cylindrical pump defining surface 60, which is a portion of the
inner peripheral surface of the shaft insertion hole 25. The spiral
groove 59 and the pump defining surface 60 define the screw pump
that feeds the lubricating oil upward in accompaniment with the
rotation of the driveshaft 5. A rotation direction of the spiral
groove 59 is set so that the lubricating oil is fed upward in
accompaniment with the rotation of the driveshaft 5. If the
rotation direction of the driveshaft 5 is, for example, clockwise
as viewed from above, the spiral groove 59 extends clockwise as
viewed from above.
[0081] The spiral groove 59 extends in the up/down direction while
spirally surrounding the center line of the driveshaft 5. An upper
end of the spiral groove 59 corresponds to a downstream end of the
first intermediate passage 58 and a lower end of the spiral groove
59 corresponds to an upstream end of the first intermediate passage
58. The upper end and the lower end of the spiral groove 59 are
positioned at heights between the lower end of the upper bearing B1
and the upper end of the lower bearing B2. The lower end of the
spiral groove 59 is positioned at the same height as the downstream
end of the first upstream passage 56.
[0082] The first downstream passage 61 extends upward from the
upper bearing B1. The first downstream passage 61 is in
communication with the internal gap of the upper bearing B1. The
first downstream passage 61 guides the lubricating oil, which has
passed upward through the internal gap of the upper bearing B1,
toward the first connection passage 53. The first downstream
passage 61 is positioned between the upper bearing B1 and the shaft
cap 28. The first downstream passage 61 passes between an outer
peripheral surface of the nut 26 and an inner peripheral surface of
the fixing ring 27 and extends from the upper bearing B1 to the
shaft cap 28.
[0083] The second intermediate passage 62 extends upward from the
first upstream passage 56. The second intermediate passage 62 is
positioned below the upper bearing B1. The second intermediate
passage 62 is positioned in front of the driveshaft 5. The second
intermediate passage 62 is positioned between the shaft insertion
hole 25 and the shaft chamber 37. The second intermediate passage
62 is a passage that is defined by the lower case 17 and is
integral and unitary with the lower case 17.
[0084] The second intermediate passage 62 is a separate passage
from the first intermediate passage 58 and does not intersect the
first intermediate passage 58. A flow passage area of the second
intermediate passage 62 is greater than the flow passage area of
the first intermediate passage 58. In a radial direction of the
driveshaft 5, the second intermediate passage 62 is positioned
farther outward than the first intermediate passage 58. The second
intermediate passage 62 is separated from the first intermediate
passage 58 by a partition wall 17z of the lower case 17. The
partition wall 17z is positioned between the first intermediate
passage 58 and the second intermediate passage 62 in the radial
direction of the driveshaft 5.
[0085] An upper end of the second intermediate passage 62
corresponds to a downstream end of the second intermediate passage
62, and a lower end of the second intermediate passage 62
corresponds to an upstream end of the second intermediate passage
62. Both the upper end and the lower end of the second intermediate
passage 62 are positioned at heights between the upper end and the
lower end of the spiral groove 59. The second intermediate passage
62 may be vertical from its upper end to its lower end or may be
inclined obliquely with respect to a vertical direction. Also, the
second intermediate passage 62 may have a broken line shape or a
curved shape. A length of the second intermediate passage 62 in the
up/down direction is shorter than a distance in the up/down
direction from the lower end of the upper bearing B1 to the upper
end of the lower bearing B2 and is longer than an outer diameter of
the upper bearing B1.
[0086] As shown in FIG. 4A, the second intermediate passage 62 is
longer than the first upstream passage 56 and the second downstream
passages 63 in the up/down direction. As shown in FIG. 4B and FIG.
4C, the second intermediate passage 62 preferably is provided only
in an annular region surrounding the pump defining surface 60. The
second intermediate passage 62 preferably has, for example, a
horizontal cross section of circular shape. As shown in FIG. 4C, an
inner diameter of the second intermediate passage 62, that is, a
diameter D2 of a cross section of the second intermediate passage
62 orthogonal or substantially orthogonal to the center line of the
driveshaft 5 is less than an outer diameter D1 of the groove
defining portion 5a, which is a maximum value of outer diameter of
the driveshaft 5.
[0087] As shown in FIG. 3, each second downstream passage 63
extends in the up/down direction along an outer peripheral surface
of the upper bearing B1. Each second downstream passage 63 is
longer than the upper bearing B1 in the up/down direction. The
plurality of second downstream passages 63 include a front
downstream passage 63f positioned in front of the upper bearing B1
and a lateral downstream passage 63L positioned on the lateral of
the upper bearing B1. The plurality of second downstream passages
63 are disposed across an interval in a circumferential direction
of the driveshaft 5. The second downstream passages 63 are defined
by an inner surface of an upper bearing bypass groove 64 provided
at the lower case 17 and the outer peripheral surface of the upper
bearing B1.
[0088] Upper ends of the second downstream passages 63 that
correspond to downstream ends are positioned at heights between the
upper end of the upper bearing B1 and a lower end of the rod cap
35. The upper ends of the second downstream passages 63 are
positioned around the fixing ring 27. Lower ends of the second
downstream passages 63 that correspond to upstream ends are
positioned at heights between the upper end of the second
intermediate passage 62 and the lower end of the upper bearing B1.
The second downstream passages 63 are connected to the first feed
passage 51 via a merging portion 65 positioned at a height between
the upper end of the second intermediate passage 62 and the lower
end of the upper bearing B1. The merging portion 65 faces the outer
peripheral surface of the driveshaft 5 across an interval in a
radial direction.
[0089] The first connection passage 53 and the second connection
passage 54 are separate passages that do not intersect each other.
The first connection passage 53 and the second connection passage
54 are parallel or substantially parallel to each other and extend
obliquely downward from the shaft insertion hole 25 to the shift
chamber 37. The first connection passage 53 and the second
connection passage 54 are positioned at heights between an upper
end 25a of the shaft insertion hole 25 and the lower end of the
upper bearing B1. The first connection passage 53 is positioned
above the second connection passage 54. The second connection
passage 54 is positioned lower than the nut 26 and the fixing ring
27. The first connection passage 53 and the second connection
passage 54 are mutually overlapped in plan view.
[0090] An upstream end of the first connection passage 53 opens at
the inner peripheral surface of the shaft insertion hole 25. An
upstream end of the second connection passage 54 opens at an inner
peripheral surface of the upper bearing bypass groove 64.
Downstream ends of both the first connection passage 53 and the
second connection passage 54 open at an inner surface of the shift
chamber 37. When the prime mover 3 is stopped, both the upstream
end and the downstream end of the first connection passage 53 are
disposed higher than the oil surface (oil level L1) of the
lubricating oil. A length of the first connection passage 53, that
is, a length of a center line of the first connection passage 53 is
shorter than the outer diameter of the upper bearing B1 and longer
than an inner diameter of the first connection passage 53. The same
applies to the second connection passage 54.
[0091] An upper portion of the upstream end of the first connection
passage 53 is positioned higher than the fixing ring 27 and is
disposed at the same height as the first downstream passage 61. A
lower portion of the upstream end of the first connection passage
53 is positioned around the fixing ring 27 and is disposed at the
same height as the upper ends of the second downstream passages 63.
The upstream end of the second connection passage 54 is positioned
around the upper bearing B1 and faces the outer peripheral surface
of the upper bearing B1 across an interval in a radial direction.
The second connection passage 54 is directly connected to the
second downstream passage 63. The first connection passage 53 is
directly connected to each of the first downstream passage 61 and
the second downstream passage 63. The second connection passage 54
is indirectly connected to the first downstream passage 61 and the
first connection passage 53 via the second downstream passage
63.
[0092] A flow of the lubricating oil inside the lower case 17 shall
now be described with reference to FIG. 3.
[0093] When the prime mover 3 (see FIG. 1) rotates the driveshaft
5, the pinion 21, the front gear 22, and rear gear 23 rotate around
their respective center lines and the spiral groove 59 provided at
the groove defining portion 5a of the driveshaft 5a rotates around
the drive axis Ad. At the same time, the water pump 45 rotates and
the water outside the outboard motor 2 is supplied as cooling water
to the water pump 45 via the first water supply passage 43 and the
second water supply passage 44.
[0094] The gear chamber 30, in which the pinion 21, the front gear
22, and the rear gear 23 are housed, is filled with the lubricating
oil. When the front gear 22 rotates, the lubricating oil inside the
gear chamber 30 flows upward from the front gear 22 and is supplied
to the first upstream passage 56 shared by the first feed passage
51 and the second feed passage 52. A portion of the lubricating oil
supplied to the first upstream passage 56 is fed upward along the
first intermediate passage 58 by the screw pump defined by the
spiral groove 59 and the pump defining surface 60. The remaining
lubricating oil supplied to the first upstream passage 56 is guided
upward by the second intermediate passage 62.
[0095] The lubricating oil guided upward by the first intermediate
passage 58 is supplied to the internal gap of the upper bearing B1.
A portion of the lubricating oil guided upward by the second
intermediate passage 62 is supplied to the first feed passage 51
via the merging portion 65 and the remaining lubricating oil is
supplied to the front downstream passage 63f positioned in front of
the upper bearing B1. A portion of the lubricating oil supplied to
the first feed passage 51 via the merging portion 65 is supplied to
the internal gap of the upper bearing B1 and the remaining
lubricating oil is supplied to the lateral downstream passage 63L
positioned on the lateral side of the upper bearing B1.
[0096] The lubricating oil guided by the front downstream passage
63f is supplied to the second connection passage 54 disposed below
the first connection passage 53. Also, the lubricating oil guided
by the lateral downstream passage 63L is supplied to the first
downstream passage 61 positioned above the upper bearing B1. The
lubricating oil discharged upward from the internal gap of the
upper bearing B1 is also supplied to the first downstream passage
61. The lubricating oil supplied to the first downstream passage 61
is supplied to the first connection passage 53.
[0097] The first downstream passage 61 is connected not just to the
first connection passage 53 but also to the second connection
passage 54 via the front downstream passage 63f. When a pressure of
the lubricating oil at the first downstream passage 61 is higher
than a pressure of the lubricating oil at the front downstream
passage 63f, a portion of the lubricating oil inside the first
downstream passage 61 flows into the first connection passage 53
and the remaining lubricating oil is supplied to the second
connection passage 54 after flowing in reverse through the front
downstream passage 63f. Oppositely, when the pressure of the
lubricating oil at the first downstream passage 61 is lower than
the pressure of the lubricating oil at the front downstream passage
63f, a portion of the lubricating oil inside the front downstream
passage 63f flows into the second connection passage 54 and the
remaining lubricating oil is supplied to the first connection
passage 53.
[0098] The lubricating oil supplied to the first connection passage
53 and the second connection passage 54 is guided from the shaft
insertion hole 25 of the feed passage to the rod insertion hole 36
of the return passage 55. The lubricating oil supplied inside the
rod insertion hole 36 flows downward inside the rod insertion hole
36 due to gravity while being cooled by the lower case 17. The
lubricating oil that has reached a vicinity of the disk portion 32b
of the shift rod 32 flows into the gear chamber 30 via the rod
bypass groove 38. The lubricating oil is thus returned to the gear
chamber 30 by the return passage 55. The lubricating oil that has
returned to the gear chamber 30 is fed upward again by the rotation
of the gear mechanism 6.
[0099] As described above, with the present preferred embodiment,
when the prime mover 3 rotates the driveshaft 5, the gear mechanism
6 housed in the gear chamber 30 of the lower case 17 rotates and
the lubricating oil inside the gear chamber 30 is fed upward. The
lubricating oil is thus made to flow through the first upstream
passage 56, the first intermediate passage 58, and the upper
bearing B1 interior of the first feed passage 51, in that order.
The second feed passage 52 extends from the first upstream passage
56 to the connection passage while bypassing the first intermediate
passage 58 by the second intermediate passage 62. A portion of the
lubricating oil flowing upward from the gear mechanism 6 flows
through the second intermediate passage 62 toward the connection
passage without passing through the first intermediate passage
58.
[0100] The second intermediate passage 62 bypassing the spiral
first intermediate passage 58 is thus provided in the second feed
passage 52 and therefore a flow rate of the lubricating oil flowing
through the circulation path including the gear chamber 30, the
feed passage, the connection passage, and the return passage 55 is
not restricted by the first intermediate passage 58. The
lubricating oil is thus circulated at a flow rate exceeding a
supply capacity of the first intermediate passage 58. Circulation
efficiency of the lubricating oil flowing through the circulation
path is thus improved and the lubricating oil inside the lower case
17 is cooled effectively.
[0101] Further, the lubricating oil is released to the second
intermediate passage 62, so that the lubricating oil is prevented
from increasing in pressure at the first upstream passage 56, even
if a flow rate of the lubricating oil flowing upward from the gear
mechanism 6 increases. Further, the second intermediate passage 62
is provided not farther inward than the spiral first intermediate
passage 58 but is provided outward of the spiral first intermediate
passage 58, so that complicating of the structure of the passage is
prevented. Moreover, the diameter D2 of the cross section of the
second intermediate passage 62 is smaller than the maximum diameter
D1 of the driveshaft 5, so that an increase in size of the lower
case 17 is prevented.
[0102] With the present preferred embodiment, the flow passage area
of the second intermediate passage 62 bypassing the spiral first
intermediate passage 58 is greater than the flow passage area of
the first intermediate passage 58. The lubricating oil is thus
guided through the second intermediate passage 62 at a flow rate
greater than a flow rate of the lubricating oil flowing through the
first intermediate passage 58. The circulation efficiency of the
lubricating oil is thus improved.
[0103] With the present preferred embodiment, the first feed
passage 51 and the second feed passage 52 are connected to each
other by the merging portion 65 at a position upstream of the
connection passage and therefore excess lubricating oil is released
from one of either of the first feed passage 51 and the second feed
passage 52 to the other of either of the first feed passage 51 and
the second feed passage 52. Pressure increase of the lubricating
oil at the first feed passage 51 and the second feed passage 52 is
thus significantly reduced or prevented.
[0104] With the present preferred embodiment, the lubricating oil
that has bypassed the spiral first intermediate passage 58 is
supplied from the second feed passage 52 to the first feed passage
51 at a position that is upstream the upper bearing B1 and
downstream the first intermediate passage 58. The lubricating oil
supplied to the first feed passage 51 at the merging portion 65 is
supplied to the internal gap of the upper bearing B1 that is
positioned downstream the merging portion 65. The flow rate of the
lubricating oil supplied to the upper bearing B1 is thus increased.
Further, the excess lubricating oil is released from the first feed
passage 51 to the second feed passage 52 via the merging portion
65, so that the pressure of the lubricating oil is prevented from
increasing at a portion between the upper bearing B1 and the first
intermediate passage 58.
[0105] With the present preferred embodiment, the second feed
passage 52 extends toward the connection passage while bypassing
the internal gap of the upper bearing B1 by the plurality of second
downstream passages 63. By bypassing the internal gap of the upper
bearing B1 that is small in flow passage area, the flow rate of the
lubricating oil flowing through the second feed passage 52 is
prevented from being restricted by the internal gap of the upper
bearing B1. Further, the second feed passage 52 is provided with
the plurality of second downstream passages 63, so that a
sufficient flow passage area is secured for the passage bypassing
the upper bearing B1.
[0106] With the present preferred embodiment, an inner wall surface
of each second downstream passage 63 that defines each second
downstream passage 63 includes the outer peripheral surface of the
upper bearing B1, and the outer peripheral surface of the upper
bearing B1 defines portions of the outer peripheral passage. The
lubricating oil inside each second downstream passage 63 flows
while in contact with the outer peripheral surface of the upper
bearing B1. The upper bearing B1 is thus cooled by the lubricating
oil flowing through each second downstream passage 63. The upper
bearing B1 is thus cooled while improving the circulation
efficiency of the lubricating oil.
[0107] With the present preferred embodiment, the lubricating oil
inside the first feed passage 51 is guided to the return passage 55
by the first connection passage 53 and the lubricating oil inside
the second feed passage 52 is guided to the return passage 55 by
the second connection passage 54. The first connection passage 53
and the second connection passage 54 are separate passages that do
not intersect each other. A flow passage area of the connection
passage is thus increased and the flow rate of the lubricating oil
flowing through the circulation path is prevented from being
restricted by the connection passage.
[0108] With the present preferred embodiment, the second feed
passage 52 is connected not just to the second connection passage
54 but also to the first connection passage 53. The second feed
passage 52 includes a portion intersecting the first connection
passage 53 and a portion intersecting the second connection passage
54. When the amount of lubricating oil flowing through the second
feed passage 52 is high, a portion of the lubricating oil flows
from the second feed passage 52 to the second connection passage 54
and the remaining lubricating oil flows from the second feed
passage 52 to the first connection passage 53. A portion of the
lubricating oil flowing through the second feed passage 52 is thus
released to the first connection passage 53 and the circulation
flow rate of the lubricating oil is thus prevented from being
restricted by the second connection passage 54.
Other Preferred Embodiments
[0109] The present invention is not restricted to the contents of
the preferred embodiments and various modifications are possible
within the scope of the present invention.
[0110] For example, with the preferred embodiment described above,
a non-limiting example where the first upstream passage 56 is
preferably shared by the first feed passage 51 and the second feed
passage 52 was described. However, the second feed passage 52 may
include a second upstream passage separate from the first upstream
passage 56.
[0111] With the preferred embodiment described above, a
non-limiting example where the first upstream passage 56 is
adjacent to the lower bearing B2 and the second downstream passages
63 preferably are adjacent to the upper bearing B1 was described.
However, the first upstream passage 56 may be separated from the
lower bearing B2. Similarly, the second downstream passages 63 may
be separated from the upper bearing B1.
[0112] With the preferred embodiment described above, a
non-limiting example where the second intermediate passage 62
preferably is integral with the lower case 17 was described.
However, the second intermediate passage 62 may be defined by a
member separate from the lower case 17.
[0113] With the preferred embodiment described above, a
non-limiting example where the second intermediate passage 62
preferably is positioned in front of the driveshaft 5 was
described. However, the second intermediate passage 62 may be
positioned to a side or behind the driveshaft 5. The same applies
to the first upstream passage 56.
[0114] With the preferred embodiment described above, a
non-limiting example where both the upper end and the lower end of
the second intermediate passage 62 preferably are positioned at
heights between the upper end and the lower end of the spiral
groove 59 was described. However, a portion of the second
intermediate passage 62 may be disposed higher than or lower than
the spiral groove 59.
[0115] A non-limiting example case where the cross section of the
second intermediate passage 62 is circular or substantially
circular was described. However, the cross section of the second
intermediate passage 62 does not have to be circular. For example,
the cross section of the second intermediate passage 62 may be
elliptical or polygonal or may be a C shape extending along the
shaft insertion hole 25.
[0116] With the preferred embodiment described above, a
non-limiting example where the lower ends of the second downstream
passages 63 that correspond to the upstream ends preferably are
connected by the merging portion 65 to the first feed passage 51
was described. However, a partition wall separating the lower ends
of the second downstream passages 63 from the first feed passage 51
may be provided in place of the merging portion 65.
[0117] With the preferred embodiment described above, a
non-limiting example where the second connection passage 54
preferably is positioned higher than the lower end of the upper
bearing B1 was described. However, at least a portion of the second
connection passage 54 may be positioned lower than the lower end of
the upper bearing B1. In this case, the second downstream passages
63 may be omitted. That is, the second connection passage 54 may
extend from the second intermediate passage 62 to the return
passage 55.
[0118] Also, features of two or more of the various preferred
embodiments described above may be combined.
[0119] The present application corresponds to Japanese Patent
Application No. 2015-222386 filed on Nov. 12, 2015 in the Japan
Patent Office, and the entire disclosure of this application is
incorporated herein by reference.
[0120] While preferred embodiments of the present invention have
been described above, it is to be understood that variations and
modifications will be apparent to those skilled in the art without
departing from the scope and spirit of the present invention. The
scope of the present invention, therefore, is to be determined
solely by the following claims.
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