FIELD OF THE INVENTION
[0001] The present invention relates to an engine and a straddle-type vehicle provided with
the same.
BACKGROUND OF THE INVENTION
[0002] JP-A-2007-106348 discloses a scooter-type motorcycle in which an engine is mounted between a section
where the legs of a driver straddle the motorcycle and an underside of the seat. It
is desired for such a scooter-type vehicle to lower the height of the section where
the legs of the driver straddle the motorcycle in order to facilitate riding for the
driver. For this purpose, in the engine of
JP-A-2007-106348 the height of the cylinder section is lowered by providing a crankcase dividable
in a longitudinal direction and by mounting a forwardly-inclined cylinder section
on a front-half of the crankcase.
[0003] However, because a crankshaft and a balancer shaft, disposed on a dividing surface
of the crankcase, are vertically stacked in the engine of
JP-A-2007-106348, the size of the whole engine grows in the vertical direction. Therefore, it is difficult
to lower the height of the section where the legs of the driver straddle the vehicle
when such an engine is mounted on a straddle-type vehicle such as a scooter-type vehicle.
[0004] An object of an embodiment of the invention is to provide an engine that can be made
compact, and a straddle-type vehicle equipped with the engine.
SUMMARY OF THE INVENTION
[0005] Various aspects of the present invention are defined in the independent claims. Some
preferred features are defined in the dependent claims.
[0006] According to an aspect of the present invention is an engine comprising: a crankshaft
including a crank web; a clutch shaft disposed behind the crankshaft and provided
with a clutch; a balancer shaft disposed in front of the crankshaft and provided with
a balancer weight; a crankcase for accommodating the crankshaft, the balancer shaft
and the clutch shaft; a cylinder section attached to the crankcase; and a starter
motor disposed above the cylinder section and capable of driving the crankshaft, wherein
the balancer shaft is disposed between a first horizontal surface intersecting an
axial center of the crankshaft when the engine is mounted on a vehicle and a second
horizontal surface intersecting a lower end of the crank web when the engine is mounted
on the vehicle, the balancer weight is disposed below the first horizontal surface,
and the starter motor is disposed forward of a vertical surface intersecting the axial
center of the crankshaft when the engine is mounted on the vehicle.
[0007] A vertical surface intersecting an axial center of the balancer shaft when the engine
is mounted on the vehicle may be located rearward of a lower end of the cylinder section.
[0008] The engine may further comprise an oil unit, which may be attached to a front wall
of the crankcase. The oil unit may be located to overlap a third horizontal surface
intersecting a lower end of the balancer weight when the engine is mounted on the
vehicle.
[0009] The engine may further comprise an oil unit attached to a front wall of the crankcase.
[0010] An uppermost point of the oil unit as measured in a direction perpendicular to a
plane intersecting the axial center of the crankshaft and an axial center of the balancer
shaft may be located higher, as measured in said direction, than a lowermost point
of the balancer weight, as measured in said direction.
[0011] The balancer weight may include at least two balancer weights separately disposed
in an axial direction of the balancer shaft to sandwich the crank web, and the oil
unit may be located in a position different from that of the balancer weights as measured
in an axial direction of the balancer shaft.
[0012] A front end of the balancer weight may be located forward of a lower end of the cylinder
section.
[0013] The first horizontal surface may overlap the cylinder section.
[0014] The crankcase may be dividable by a dividing surface intersecting an axial center
of the crankshaft and an axial center of the balancer shaft. The cylinder section
may be inclined forward with respect to a line perpendicular to the dividing surface
of the crankcase.
[0015] According to an aspect of the invention is an engine comprising: a crankshaft including
a crank web; a balancer shaft disposed in front of the crankshaft and provided with
a balancer weight; a crankcase for accommodating the crankshaft and the balancer shaft
and configured to be dividable by a dividing surface intersecting an axial center
of the crankshaft and an axial center of the balancer shaft; and a cylinder section
mounted on the crankcase in a manner that the section inclines forward with respect
to a line perpendicular to a dividing surface of the crankcase. When the engine is
mounted on the vehicle, the axial center of the balancer shaft is disposed between
a first horizontal surface intersecting the axial center of the crankshaft and a second
horizontal surface intersecting a lower end of the crank web.
[0016] According to an aspect of the invention is a straddle type vehicle comprising the
engine according to the first and/or second aspects.
[0017] Description will hereinafter be made of an engine and a straddle-type vehicle according
to an embodiment of the invention with reference to the drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0018]
FIG. 1 is a left side view of a motorcycle according to an embodiment of the present
invention.
FIG. 2 is a left side view of an engine case according to an embodiment of the present
invention.
FIG. 3 is a right side view of the engine case according to an embodiment of the present
invention.
FIG. 4 is another example of the right side view of the engine case according to an
embodiment of the present invention.
FIG. 5 is a sectional view of the engine taken along the line V-V of FIG. 2.
FIG. 6 is a sectional view of the engine taken along the line VI-VI of FIGs. 2 to
4.
FIG. 7 is a sectional view of the engine taken along the line VII-VII of FIG. 4.
FIG. 8 is an explanatory view for showing relative positions of shafts when viewed
from the left side of an engine.
FIG. 9 is an example of a plan view of the motorcycle according to an embodiment of
the present invention.
FIG. 10 is another example of the left side view of the engine case according to an
embodiment of the present invention.
FIG. 11 is further another example of the right side view of the engine case according
to an embodiment of the present invention.
FIG. 12 is a rear view of the engine case according to an embodiment of the present
invention.
FIG. 13 is a bottom view of the engine case according to an embodiment of the present
invention.
FIG. 14 is a sectional view taken along a crankcase dividing surface of the engine
according to an embodiment of the present invention.
FIG. 15 is a sectional view of the engine case taken along the line XV-XV of FIG.
14.
DETAILED DESCRIPTION OF THE DRAWINGS
[0019] In this embodiment, the engine according to the invention is realized as a water-cooled,
four-stroke, in-line three-cylinder engine, and the straddle-type vehicle according
to the invention is realized as a scooter-type motorcycle. In this embodiment, directions
of front, rear, left, right, up, and down are directions of front, rear, left, right,
up, and down seen from a rider operating the motorcycle. A right-and-left direction
may also be referred to as a vehicle width direction.
[0020] The motorcycle will be described first. FIG. 1 is a left side view of a motorcycle
1. As shown in FIG. 1, the motorcycle 1 includes a front wheel 3 and a rear wheel
4 rotatably supported by a body thereof, a seat 5 which a driver sits on, handlebars
6 for steering the front wheel 3, and an engine 2 for producing power to drive the
rear wheel 4.
[0021] The seat 5 behind the handlebars 6 extends from an intermediate position between
the front wheel 3 and the rear wheel 4 to a position above the rear wheel 4. This
seat 5 is a tandem seat having a front seating section 5a on which the driver sits
in front and a rear seating section 5b on which a passenger sits above the rear wheel.
The driver seated on the seat 5 manipulates the handlebars 6 to turn the front wheel
3 from side to side, which is rotatably supported at lower ends of a pair of a right
and a left front forks 7.
[0022] The engine 2 is fixed to a body frame (not shown) constituting a body framework of
the motorcycle 1. The engine 2 has a cylinder section 2b for accommodating pistons
(not shown). The cylinder section 2b extends upward while inclining forward from a
position below the front seating section 5a of the seat 5. The engine 2 will be described
in detail later.
[0023] The motorcycle 1 is also equipped with a shaft-driven driveline 8 for transmitting
driving force of the engine 2 to the rear wheel 4. More specifically, the motorcycle
1 has a drive shaft 9 extending from the engine 2 to the rear wheel 4 in the left
side of the body.
[0024] The drive shaft 9 is supported to be vertically swingable about a pivot shaft 11
extended in the vehicle width direction. A bevel gear formed on a rear end of the
drive shaft 9 meshes with a bevel gear formed on a left end of a rear wheel rotating
shaft 4a, which supports the rear wheel 4 for rotation. Thus, the rear wheel 4 is
supported to be vertically swingable about the pivot shaft 11.
[0025] The motorcycle 1 also includes a body cover 12 for covering the body thereof. The
body cover 12 includes: a front cowling 12a formed above the front wheel 3 to cover
a front section of the body; leg shields 12b formed to cover the front of the legs
of the driver seated on the front seating section 5a of the seat 5; a center cover
12c formed to cover an upper section of the body in a position between the handlebars
6 and the seat 5; a side cover 12d formed to cover the right side and the left side
of the body (that is, lateral sides in the vehicle width direction) below the center
cover 12c; and a pair of a right and a left footboards 12e formed below the side cover
12d with a pair of a right and a left flat surfaces 12f which the driver seated on
the front seating section 5a of the seat 5 puts his/her right and left feet on.
[0026] The center cover 12c extends forward while inclining upward from a position below
a front end of the seat 5. The inclination of the center cover 12c generally corresponds
with that of the cylinder section 2b of the engine 2 disposed below the center cover
12c.
[0027] The engine 2 can be started by a starter motor 2c to start driving of the motorcycle
1. Air and a fuel are supplied from an intake port (not shown) to the cylinder section
2b of the started engine 2 by a fuel injection method. The engine 2 produces power
by combusting the fuel in the cylinder section 2b. This power is transmitted to the
rear wheel 4 via the drive shaft 9. Consequently, the rear wheel 4 rotates, and the
motorcycle 1 travels forward. Exhaust gases of the engine 2 discharged from an exhaust
port (not shown) in the cylinder section 2b are released into the atmosphere through
a silencer (muffler) 10.
[0028] Next, the engine 2 will be described in detail. FIG. 2 is a left side view of an
engine case 2a constituting a framework of the engine 2. FIGs. 3 and 4 are right side
views of the engine case 2a. FIGs. 2 and 3 show the engine case 2a in a state where
a cover section for partially covering a lateral side in the vehicle width direction
is removed. FIG. 5 is a sectional view of the engine 2 taken along the line V-V of
FIG. 2. FIG. 6 is a sectional view of the engine 2 taken along the line VI-VI of FIGs.
2 to 4. FIG. 7 is a sectional view of the engine 2 taken along the line VII-VII of
FIG. 4.
[0029] The engine case 2a has a crankcase 20 for accommodating a crankshaft 40 and a transmission
case 30 for accommodating a transmission 60. As shown in FIG. 5, the transmission
60 is a wet-type continuously variable transmission having: a drive pulley 61; a drive
pulley shaft 62 for driving the drive pulley; a driven pulley 63; a driven pulley
shaft 64 for driving the driven pulley; an endless metal belt 65 wound between the
drive pulley 61 and the driven pulley 63.
[0030] As shown in FIGs. 2 to 4, the crankcase 20 can be divided into upper and lower sections
on a dividing surface S1 passing through an axial center P1 of the crankshaft 40.
In other words, as two case sections that are formed individually and dividable into
the upper and the lower sections, the crankcase 20 has an upper case section 20a constituting
a section above the dividing surface S1 (that is, in the cylinder section 2b side)
and a lower case section 20b constituting a section below the dividing surface S1.
The crankcase 20 is constructed by joining a mating surface at a bottom of the upper
case section 20a with a mating surface on top of the lower case section 20b on the
dividing surface S1.
[0031] As shown in FIGs. 5 to 7, the transmission case 30 is configured to be dividable
into a right and a left sections on a dividing surface S2 and a dividing surface S3,
both of which are perpendicular to the axial center P1 of the crankshaft 40. In other
words, the transmission case 30 has a right case section 30a, a left case section
30b, and a left end case section 30c as three case sections that are formed individually
and separable from each other into the right and the left sections. The right case
section 30a constitutes a section further on the right of the right dividing surface
S2 and covers the right side of the transmission 60 (outside in the vehicle width
direction). The left case section 30b constitutes a section between the dividing surface
S2 and the left dividing surface S3 and covers the left side of the transmission 60
(inside in the vehicle width direction). The left end case section 30c constitutes
a section further on the left of the dividing surface S3 and partially covers the
left side of the left case section 30b. The transmission case 30 is constructed by
joining a mating surface on a left end of the right case section 30a with a mating
surface on a right end of the left case section 30b on the dividing surface S2, and
by joining a mating surface on a left end of a portion of the left case section 30b
with a mating surface on a right end of the left end case section 30c on the dividing
surface S3.
[0032] Then, the upper case section 20a and the lower case section 20b of the crankcase
20 are respectively coupled to a portion and another portion of the transmission case
30, and thereby the crankcase 20 and the transmission case 30 are integrated to constitute
the engine case 2a.
[0033] In other words, as shown in FIG. 2, rear portions of the upper case section 20a and
the lower case section 20b and a front portion of the transmission case 30 are disposed
in positions where they overlap each other in the vehicle width direction. Then, the
upper case section 20a and a portion of the transmission case 30 overlapping the upper
case section 20a are fastened and secured in the vehicle width direction while the
lower case section 20b and another portion of the transmission case 30 overlapping
the lower case section 20b are fastened and secured in the vehicle width direction.
[0034] More specifically, as shown in FIGs. 2 and 5, on the right of a portion (clutch chamber
22) at the back of a portion where the crankshaft 40 is accommodated (crank chamber
21) in the upper case section 20a and the lower case section 20b, front portions of
the right case section 30a and the left case section 30b are disposed across both
of the case sections of the upper case section 20a and the lower case section 20b
(across the dividing surface S1).
[0035] Then, as shown in FIGs. 2 and 3, a plurality of fastening holes 90 are formed in
corresponding positions on the rear portions of the upper case section 20a and the
lower case section 20b, the front portion of the left case section 30b, and the front
portion of the right case section 30a (see FIG. 4) that are aligned in the vehicle
width direction. Furthermore, as shown in FIGs. 4 and 6, bolt members 91 extending
through the three case sections in the vehicle width direction are inserted in the
plural fastening holes 90.
[0036] More specifically, three case sections, which are the upper case section 20a, the
left case section 30b, and the right case section 30a, are fastened in the vehicle
width direction by the plural bolt members 91 while the other three case sections,
which are the lower case section 20b, the left case section 30b, and the right case
section 30a, are also fastened in the vehicle width direction by the same.
[0037] As described above, the upper case section 20a and the lower case section 20b are
each integrally connected with the left case section 30b and the right case section
30a. Therefore, rigidity of the engine case 2a, especially that of the crankcase 20,
is increased.
[0038] As shown in FIGs. 2 to 5, the crank chamber 21 extended in the vehicle width direction
is formed in the front portion of the crankcase 20 in such an engine case 2a. The
crankshaft 40 is accommodated in the crank chamber 21.
[0039] The above-mentioned cylinder section 2b extends upward while inclining forward above
the crank chamber 21. As shown in FIG. 5, this cylinder section 2b has: a cylinder
block 13 in which three cylinders 13a for accommodating three pistons 13b are formed
in line in the vehicle width direction; a cylinder head 14 in which three combustion
chambers 14a for compressing and combusting the fuel are formed in corresponding positions
to the three cylinders 13a as shown in FIG. 2; and a cover 15 for closing a top end
of the cylinder head 14.
[0040] As shown in FIG. 2, corresponding to each of the three combustion chambers 14a, an
intake port 14b and an exhaust port 14c are formed in the cylinder head 14. One end
of each port is open to a lateral side of the cylinder head 14 while the other end
is open to the combustion chamber 14a. The cylinder head 14 also accommodates an intake
valve 14d that opens and closes an opening of each of the intake ports 14b to the
combustion chamber 14a and an exhaust valve 14e that opens and closes an opening of
each of the exhaust ports 14c to the combustion chamber 14a. A double overhead camshaft
(DOHC) system is adopted for the engine 2 as a drive mechanism of the intake valves
14d and the exhaust valves 14e.
[0041] Meanwhile, as shown in FIG. 5, the crankshaft 40 accommodated in the crank chamber
21 of the crankcase 20 has: four journals 41 a to 41 d, each formed in a cylindrical
shape and extending in the vehicle width direction in a manner that an axial center
thereof corresponds to the axial center P1 of the crankshaft 40; three pairs of crank
webs 42, each formed in a plate shape and extending in a perpendicular direction to
the axial center P1; and three crankpins 43, each extending in the vehicle width direction
to connect a pair of the crank webs 42 in a position apart from the axial center P1.
The journals 41 a to 41 d, the cranks webs 42, and the crankpins 43 are integrally
formed.
[0042] The three pairs of the crank webs 42 are formed in positions corresponding to the
three cylinders 13a formed in the cylinder block 13. Then, the three crankpins 43
are each coupled to a lower end of a pillar-shaped connecting rod 13c supporting the
piston 13b from below.
[0043] The crankshaft 40 is supported in the crankcase 20 to rotate about the axial center
P1 in accordance with reciprocating motion of the three pistons 13b in the cylinders
13a that are coupled to the crankshaft 40 via the connecting rods 13c.
[0044] More specifically, as shown in FIG. 5, a journal bearing 21 a for supporting the
journal 41 a that constitutes a left end portion of the crankshaft 40 is formed on
a left wall for closing the left side of the crank chamber 21. A journal bearing 21d
for supporting the journal 41 d that constitutes a right end portion of the crankshaft
40 is formed on a right wall for closing the right side of the crank chamber 21. Furthermore,
in the crank chamber 21, a journal bearing 21 b is formed to support the journal 41
b that extends between a left end pair of the crank webs 42 and a middle pair of the
crank webs 42. A journal bearing 21 c is also formed to support the journal 41 c that
extends between the middle pair of the crank webs 42 and a right end pair of the crank
webs 42. The journals 41 a to 41d of the crankshaft 40 are respectively supported
by the journal bearings 21 a to 21 d with plain bearings (not shown) formed in a cylindrical
shape with a thin wall and disposed to cover peripheries of the journals 41 a to 41
d.
[0045] A left end portion of the crankshaft 40 projects to the left of the crank chamber
21, and a generator 44 for producing electric power in accordance with rotation of
the crankshaft 40 is mounted on the left end of the crankshaft 40. The generator 44
has a rotor having a magnet and integrally rotating with the crankshaft 40, and a
stator coil disposed facing the magnet. Then, the generator 44 is able to produce
electric power with the rotor rotating in conjunction with the crankshaft 40. The
electric power produced by the generator 44 is supplied to, for example, a battery
(not shown) provided in the motorcycle 1 (see FIG. 1). A cover member 20c for covering
the outside of the generator 44 in the vehicle width direction is removably attached
to the left side of the crank chamber 21.
[0046] As shown in FIGs. 2 to 4, a gear 45a that meshes with a gear (not shown) on a periphery
of a balancer 47 (see FIGs. 2 to 4) disposed below the crankshaft 40 is formed between
the right end crank web 42 of the crankshaft 40 and the journal bearing 21d for supporting
the right end journal 41d. The balancer 47 is rotatably supported in the crankcase
20 with a shaft (not shown) extending in the vehicle width direction. That is, a bearing
47a supporting the shaft for driving the balancer 47 is formed in the crankcase 20.
This balancer 47 is disposed in front of and slightly below the crankshaft 40 so that
an axial center of the balancer 47 is located on the dividing surface S1 of the crankcase
20.
[0047] Also, as shown in FIG. 5, a right end portion of the crankshaft 40 projects to the
right of the crank chamber 21, and a gear 45b is formed on the right end portion of
the crankshaft 40. A chain 46 for opening and closing the intake valves 14d and the
exhaust valves 14e (see FIG. 2) in the cylinder head 14 shown in FIG. 2 in the DOHC
system is wound around the gear 45b. A cover member 20d for covering the lateral side
of the right end of the crankshaft 40 in the vehicle width direction is removably
attached to the right side of the crank chamber 21.
[0048] As shown in FIG. 5, the engine 2 is also equipped with a clutch 50 that can connect
or disconnect the transmission of driving force from the crankshaft 40 to the drive
pulley shaft 62 of the transmission 60. This clutch 50 is accommodated in the crankcase
20.
[0049] More specifically, the clutch chamber 22 for accommodating the clutch 50 is formed
in parallel with the crank chamber 21 in the crankcase 20. A left portion of the crank
chamber 21 projects rearward to form this clutch chamber 22. A left wall for closing
a left side of the clutch chamber 22 is formed as a detachable cover member 20e.
[0050] In this embodiment, the clutch 50 is a multi-plate clutch. This clutch 50 has: a
clutch upstream section 51 constantly rotating in conjunction with the crankshaft
40; a clutch downstream section 52 that can be engaged with the clutch upstream section
51; a clutch shaft 53 integrally rotating with the clutch downstream section 52; and
a pressure plate 54 for controlling engagement and disengagement of the clutch upstream
section 51 with the clutch downstream section 52.
[0051] A gear 51 b is formed on a periphery of the clutch upstream section 51. This gear
51 b meshes with a gear 42g formed on a periphery of the right crank web 42 in the
left end pair of the crank webs 42 in the crankshaft 40. Therefore, while the crankshaft
40 rotates, the clutch upstream section 51 keeps rotating in conjunction with the
crankshaft 40.
[0052] The clutch upstream section 51 has: a plurality of upstream discs 51 a disposed with
predetermined spacing between one upstream disc 51a and another in the vehicle width
direction; and a gear 51 b disposed on the right of the plural upstream discs 51 a.
Meanwhile, the clutch downstream section 52 has a plurality of downstream discs 52a
disposed with predetermined spacing between one downstream disc 52a and another in
the vehicle width direction. The upstream discs 51a and the downstream discs 52a are
alternatively disposed to overlap each other in the vehicle width direction. The pressure
plate 54 disposed on the left of the upstream discs 51a and the downstream discs 52a
is urged to the right by a spring, which is not shown, and presses the upstream discs
51 a against the downstream discs 52a. Consequently, the clutch upstream section 51
and the clutch downstream section 52 are engaged. In a state where the clutch upstream
section 51 and the clutch downstream section 52 are engaged (hereinafter referred
to as an "engaged state"), the clutch upstream section 51, the clutch downstream section
52 and the clutch shaft 53 rotate integrally, and rotational driving force of the
crankshaft 40 is transmitted to the clutch shaft 53.
[0053] On the other hand, the engagement of the upstream discs 51a with the downstream discs
52a can be cancelled by moving the pressure plate 54 to the left with operation of
a rod (not shown) connected to the pressure plate 54. In such a state where the engagement
of the clutch upstream section 51 with the clutch downstream section 52 is cancelled
(hereinafter referred to as a "disengaged state"), only the clutch upstream section
51 rotates, and thus, rotational driving force of the crankshaft 40 is not transmitted
to the clutch shaft 53. The above-mentioned rod for switching the engaged state and
the disengaged state of the clutch 50 can be operated by, for example, the driver
of the motorcycle 1 with a clutch lever (not shown) provided on the handlebars 6 (see
FIG. 1) or by an actuator, which is not shown, provided in the motorcycle 1. This
actuator can be operated by hydraulic pressure or a motor, for example, on the basis
of an electric instruction input by the driver via an instruction input means (a button,
etc.), which is not shown but is provided in the motorcycle 1, or on the basis of
an electric instruction output from an Engine Control Unit (ECU), which is not shown
but is provided in the motorcycle 1, in accordance with speed of the engine 2 and
the like. The clutch 50 can also be a centrifugal clutch that switches the engaged
state and the disengaged state in accordance with centrifugal force associated with
rotation of the clutch upstream section 51.
[0054] As shown in FIGs. 2 and 5, the clutch shaft 53 is formed separately from the crankshaft
40 and is disposed parallel to the crankshaft 40 in a position adjacent to the crankshaft
40. In addition, the clutch shaft 53 is disposed behind the crankshaft 40 and above
the dividing surface S1 of the crankshaft 40 and the crankcase 20.
[0055] This clutch shaft 53 is rotatably supported in the crankcase 20. More specifically,
as shown in FIG. 5, a left clutch shaft bearing 22a for supporting a left end of the
clutch shaft 53 is formed on the left wall of the clutch chamber 22. A middle clutch
shaft bearing 22b for supporting a middle portion of the clutch shaft 53 is formed
on a right wall of the clutch chamber 22. Furthermore, in the right of the clutch
chamber 22, a right clutch shaft bearing 22c for supporting a right end portion of
the clutch shaft 53 is formed on a portion of the rear wall of the crank chamber 21
further projecting to the rear. The left clutch shaft bearing 22a, the middle clutch
shaft bearing 22b, and the right clutch shaft bearing 22c are all formed in the upper
case section 20a (see FIG. 2). The clutch shaft 53 is supported by each of the bearings
22a to 22c with a ball bearing.
[0056] As shown in FIG. 2, a crankcase-side oil pan 23 for storing lubricating oil is formed
in a portion of a bottom section of the crankcase 20 below the crank chamber 21. Lubricating
oil flows down by gravitation from the crank chamber 21 and the clutch chamber 22
in the crankcase 20 to the crankcase-side oil pan 23. An oil tank 24 for storing lubricating
oil transferred from the crankcase-side oil pan 23 is formed in another portion of
the bottom section of the crankcase 20, which is adjacent to the crankcase-side oil
pan 23, below the clutch chamber 22.
[0057] As shown in FIGs. 2 and 6, the engine 2 includes a crankcase-side oil pump 82 for
supplying lubricating oil to a motor section including such as the crankshaft 40,
the cylinder section 2b, the clutch 50 (see FIG. 5) and upstream of the clutch 50
in a driving force transmission passage in the engine 2. This crankcase-side oil pump
82 is accommodated in the crankcase 20, is positioned between the clutch 50 and the
drive pulley 61 in the vehicle width direction (see FIG. 6), and is disposed below
the clutch 50 and the drive pulley 61 in a side view (see FIG. 2).
[0058] The crankcase-side oil pump 82 has: a scavenge pump 83 for transferring lubricating
oil in the crankcase-side oil pan 23 to the oil tank 24; and a feed pump 84 for sending
lubricating oil in the oil tank 24 to each component of the engine 2 with pressure.
The scavenge pump 83 and the feed pump 84 are integrally configured and are supported
between a right pump support section 29a and a left pump support section 29b as portions
of the crankcase 20. In this embodiment, the scavenge pump 83 and the feed pump 84
are both trochoid pumps and respectively have a pair of inner rotors 83a, 84a and
outer rotors 83b, 84b.
[0059] As shown in FIG. 2, an upper end of a strainer 25 for sucking lubricating oil from
the crankcase-side oil pan 23 into the scavenge pump 83 is connected to the scavenge
pump 83. An intake section 25a for sucking lubricating oil in the crankcase-side oil
pan 23 is formed at a lower end of the strainer 25. In addition, an oil flow passage
(not shown) for guiding lubricating oil discharged from the scavenge pump 83 to the
oil tank 24 is formed between the scavenge pump 83 and an upper end of the oil tank
24.
[0060] As shown in FIG. 2, an upper end of a strainer 26 for sucking lubricating oil from
the oil tank 24 into the feed pump 84 is connected to the feed pump 84. An intake
section 26a for sucking lubricating oil in the oil tank 24 is formed at a lower end
of this strainer 26. In addition, an oil flow passage 28a for guiding lubricating
oil discharged from the feed pump 84 to an oil filter 27 is formed between the feed
pump 84 and the oil filter 27 formed in the front portion of the crankcase 20.
[0061] Furthermore, as shown in FIG. 2, a main oil flow passage (main gallery) 28c extending
in the vehicle width direction is formed below the crank chamber 21 in the crankcase
20, and an oil flow passage 28b is also formed between the main oil flow passage 28c
and the oil filter 27. Lubricating oil pumped from the oil tank 24 to the oil filter
27 by the feed pump 84 is filtered by an element (not shown) included in the oil filter
27, and then flows into the main oil flow passage 28c through the oil flow passage
28b extending rearward from the oil filter 27. Following this, as shown in FIG. 5,
lubricating oil pumped through in the main oil flow passage 28c is supplied to the
crank chamber 21 and the cylinder section 2b through an oil injection passage 28d
formed in each of the journal bearings 21 a to 21 d for supporting the journals 41
a to 41 d of the crankshaft 40 and through an oil flow passage 28e formed inside each
of the journals 41 a to 41 d.
[0062] As shown in FIG. 6, in the crankcase 20, the engine 2 is also equipped with a crankcase-side
oil pump shaft 85a driving the crankcase-side oil pump 82 and a cooling water pump
shaft 85b driving a cooling water pump 87 for circulating cooling water in the engine
2. The respective inner rotors 83a, 84a of the scavenge pump 83 and the feed pump
84 are connected to a periphery of the crankcase-side oil pump shaft 85a and integrally
rotate with the crankcase-side oil pump shaft 85a. The cooling water pump 87 is attached
to a left end of the cooling water pump shaft 85b. The crankcase-side oil pump shaft
85a and the cooling water pump shaft 85b are separately formed from each other and
are coaxially coupled. More specifically, a left end of the crankcase-side oil pump
shaft 85a and a right end of the cooling water pump shaft 85b are respectively formed
with a projection and a recess whose shapes correspond to each other. The left end
of the crankcase-side oil pump shaft 85a is coupled to the right end of the cooling
water pump shaft 85b by fitting the projection to the recess. As a result, an axial
center of the crankcase-side oil pump shaft 85a is oriented to that of the cooling
water pump shaft 85b to constitute a single crankcase-side pump shaft 85. Therefore,
the crankcase-side oil pump shaft 85a and the cooling water pump shaft 85b rotate
integrally.
[0063] This crankcase-side pump shaft 85 is formed separately from the crankshaft 40 (see
FIG. 5) and the clutch shaft 53 and is disposed parallel to the clutch shaft 53 in
a position adjacent to the clutch shaft 53. The crankcase-side pump shaft 85 is also
disposed behind the crankshaft 40 and below the drive pulley shaft 62 and the driven
pulley shaft 64.
[0064] This crankcase-side pump shaft 85 is rotatably supported by the crankcase 20. More
specifically, as shown in FIG. 6, a left crankcase-side pump shaft bearing 29c for
supporting a left end portion of the crankcase-side pump shaft 85 is formed on the
left wall of the crankcase 20 for closing the left side of the crankcase-side oil
pump 82. A middle portion of the crankcase-side pump shaft 85 is supported by the
right pump support section 29a and the left pump support section 29b via the crankcase-side
oil pump 82. Furthermore, a right crankcase-side pump insertion section 29d through
which a right end portion of the crankcase-side pump shaft 85 is inserted is formed
on the right wall of the crankcase 20 for closing the right side of the crankcase-side
oil pump 82.
[0065] An intermediate gear 86 rotatably supported by the crankcase 20 is disposed between
the crankcase-side pump shaft 85 and the clutch shaft 53. A gear 51 c that meshes
with the intermediate gear 86 is formed on the periphery of the clutch upstream section
51 of the clutch 50, and a gear 85c that also meshes with the intermediate gear 86
is attached to a periphery of the crankcase-side pump shaft 85. That is, the clutch
upstream section 51 and the crankcase-side pump shaft 85 are coupled to each other
via the intermediate gear 86.
[0066] This makes it possible for the crankcase-side pump shaft 85 to rotate in conjunction
with the crankshaft 40 regardless of connection or disconnection of driving force
transmission by the clutch 50. Consequently, the crankcase-side oil pump 82 attached
to the crankcase-side pump shaft 85 can continuously be driven in the disengaged state
of the clutch 50 as well as in the engaged state of the clutch 50. Therefore, the
crankcase-side oil pump 82 is able to supply lubricating oil to the crank chamber
21 and the cylinder section 2b via the above-mentioned oil flow passages 28a to 28e
while the crankshaft 40 is rotating.
[0067] Furthermore, the cooling water pump 87 driven by rotation of the crankcase-side pump
shaft 85 can also be driven continuously to circulate cooling water to each component
of the engine 2 even in the disengaged state of the clutch 50.
[0068] Meanwhile, as shown in FIG. 5, the transmission 60 is accommodated in the transmission
case 30. More specifically, a transmission chamber 31 extended in a longitudinal direction
is formed between the right case section 30a and the left case section 30b in the
transmission case 30, and the transmission 60 is accommodated in the transmission
chamber 31. A front side portion of this transmission chamber 31 is disposed to the
right of the clutch chamber 22 of the crankcase 20, and a rear side portion thereof
extends more rearward than the crankcase 20.
[0069] The drive pulley 61 and the drive pulley shaft 62 are accommodated in the front side
portion of the transmission chamber 31. The drive pulley shaft 62 is formed separately
from the crankshaft 40 and the clutch shaft 53 and is disposed parallel to the crankshaft
40 in a position adjacent to the crankshaft 40.
[0070] This drive pulley shaft 62 is rotatably supported by the transmission case 30. More
specifically, a right drive pulley shaft bearing 33a for supporting a right end of
the drive pulley shaft 62 is formed in the right case section 30a for closing the
right side of the transmission chamber 31, and a left drive pulley shaft bearing 33b
for supporting a left end portion of the drive pulley shaft 62 is formed in the left
case section 30b for closing the left side of the transmission chamber 31. Also, as
shown in FIGs. 3 and 4, the right drive pulley shaft bearing 33a and the left drive
pulley shaft bearing 33b in the transmission case 30 are both formed above the dividing
surface S1 of the crankcase 20.
[0071] This drive pulley shaft 62 is coaxially coupled to the clutch shaft 53. More specifically,
as shown in FIGs. 5 and 6, the right end of the clutch shaft 53 is coupled to the
left end of the drive pulley 62 by means of spline connection. Consequently, the axial
center of the clutch shaft 53 is oriented to that of the drive pulley shaft 62 to
constitute a single shaft (hereinafter referred to as a "complex main shaft 100")
extended in the vehicle width direction from the crankcase 20 to the transmission
case 30. Thus, the clutch shaft 53 and the drive pulley shaft 62 rotate integrally.
[0072] As shown in FIGs. 5 and 6, the complex main shaft 100 is formed separately from the
crankshaft 40 and is disposed parallel to the crankshaft 40 in a position adjacent
to the crankshaft 40. A left end of the complex main shaft 100 is supported by the
left clutch shaft bearing 22a on the crankcase 20. Also, a right end of the complex
main shaft 100 is supported by the right drive pulley shaft bearing 33a in the transmission
case 30. Furthermore, a middle portion of the complex main shaft 100 is supported
by the right clutch shaft bearing 22c in the crankcase 20 and by the left drive pulley
shaft bearing 33b in the transmission case 30. Moreover, as shown in FIGs. 2 to 4,
the complex main shaft 100 is disposed behind the crankshaft 40 and above the crankshaft
40 and the dividing surface S1 of the crankcase 20.
[0073] As shown in FIGs. 5 and 6, the right clutch shaft bearing 22c for supporting the
right end of the clutch shaft 53 and the left drive pulley shaft bearing 33b for supporting
the left end of the drive pulley shaft 62 are formed in shapes which correspond with
each other and are fitted to each other. More specifically, a cylindrical projection
projecting to the right from the crankcase 20 is formed in the right clutch shaft
bearing 22c around the right end portion of the clutch shaft 53. Meanwhile, a cylindrical
projection projecting to the left from the left case section 30b is formed in the
left drive pulley shaft bearing 33b around the left end portion of the drive pulley
shaft 62. Here, an inner diameter of the cylinder of the right clutch shaft bearing
22c is generally equal to an outer diameter of the left drive pulley shaft bearing
33b, and the cylinder of the left drive pulley shaft bearing 33b is fitted into that
of the right clutch shaft bearing 22c. An O-ring 30j for sealing is held between an
inner periphery of the cylinder of the right clutch shaft bearing 22c and an outer
periphery of the cylinder of the left drive pulley shaft bearing 33b.
[0074] Then, the drive pulley shaft 62 and the clutch shaft 53 are coupled to each other
in a portion where the right clutch shaft bearing 22c is fitted to the left drive
pulley shaft bearing 33b. That is, a coupling portion between the drive pulley shaft
62 and the clutch shaft 53 in the complex main shaft 100 is inserted in a fitting
portion between the right clutch shaft bearing 22c and the left drive pulley shaft
bearing 33b.
[0075] The transmission case 30 is coupled to both the upper case section 20a and the lower
case section 20b, which are described above, mainly around the complex main shaft
100 across both upper and lower sides of the dividing section S1 of the crankcase
20. More specifically, as shown in FIGs. 2 and 3, the above-mentioned plural fastening
holes 90 are formed in a surrounding portion of the clutch shaft 53 in the upper case
section 20a, in a surrounding portion of the clutch shaft 53 in the lower case section
20b, and in surrounding portions of the drive pulley shaft 62 in both the right case
section 30a and the left case section 30b. Then, as shown in FIGs. 4 and 6, a combination
of three case sections, which are the upper case section 20a, the left case section
30b, and the right case section 30a, and another combination of three case members,
which are the lower case section 20b, the left case section 30b, and the right case
section 30a, are fastened by the plural bolt members 91 around the complex main shaft
100 in the vehicle width direction.
[0076] As shown in FIGs. 5 and 6, the drive pulley 61 is formed on a periphery of the drive
pulley shaft 62. The drive pulley 61 has a drive-side fixed sheave 61 a disposed on
the inside in the vehicle width direction and a drive-side movable sheave 61 b formed
on the outside in the vehicle width direction. The drive-side fixed sheave 61 a is
integrally formed with the drive pulley shaft 62. The drive-side movable sheave 61
b is formed separately from the drive pulley shaft 62, and the drive pulley shaft
62 is inserted through a central portion thereof. The drive-side movable sheave 61
b is adopted to be slidable on the periphery of the drive pulley shaft 62 in a direction
along an axial center P2 of the drive pulley shaft 62. A distance between the drive-side
movable sheave 61 b and the drive-side fixed sheave 61 a changes in accordance with
axial movement of the drive-side movable sheave 61 b, and consequently, a diameter
of a portion in the drive pulley 61 where a metal belt is wound around (hereinafter
referred to as an "effective diameter") changes.
[0077] The sliding of this drive-side movable sheave 61 b is hydraulically controlled. More
specifically, a drive-side lid 61d is attached to the right side of the drive-side
movable sheave 61 b so as to form an enclosed space therebetween to accommodate oil
for hydraulic control (hereinafter referred to as a "drive-side oil accommodating
section 61 c"). When the amount of oil stored in this drive-side oil accommodating
section 61 c increases, the drive-side movable sheave 61 b moves to the left. Then,
the distance between the drive-side fixed sheave 61 a and the drive-side movable sheave
61 b decreases and the effective diameter of the drive pulley 61 increases. On the
other hand, when the amount of oil stored in the drive-side oil accommodating section
61 c decreases, the drive-side movable sheave 61b moves to the right. Then, the distance
between the drive-side fixed sheave 61 a and the drive-side movable sheave 61 b increases
and the effective diameter of the drive pulley 61 decreases.
[0078] As shown in FIG. 5, the driven pulley 63 and the driven pulley shaft 64 are accommodated
behind the drive pulley 61 and the drive pulley shaft 62 in the transmission chamber
31. The driven pulley shaft 64 is formed separately from the crankshaft 40 and the
clutch shaft 53 and is disposed parallel to the drive pulley shaft 62 in a position
adjacent to the drive pulley shaft 62.
[0079] This driven pulley shaft 64 is rotatably supported by the transmission case 30. More
specifically, a right driven pulley shaft bearing 34a for supporting a right end of
the driven pulley shaft 64 is formed in the right case section 30a, and a left driven
pulley shaft bearing 34b for supporting a left end portion of the driven pulley shaft
64 is formed in the left case section 30b.
[0080] As described above, the right case section 30a includes and is integrally formed
with the right drive pulley shaft bearing 33a for supporting the right end of the
drive pulley shaft 62 and the right driven pulley shaft bearing 34a for supporting
the right end of the driven pulley shaft 64 (see FIGs. 4 and 5). Also, the left case
section 30b includes and is integrally formed with the left drive pulley shaft bearing
33b for supporting the left end of the drive pulley shaft 62 and the left driven pulley
shaft bearing 34b for supporting the left end of the driven pulley shaft 64 (see FIGs.
3 and 5). That is, the right drive pulley shaft bearing 33a and the right driven pulley
shaft bearing 34a are integrally formed with the right case section 30a, and the left
drive pulley shaft bearing 33b and the left driven pulley shaft bearing 34b are integrally
formed with the left case section 30b.
[0081] As shown in FIG. 5, the driven pulley 63 is formed on the periphery of the driven
pulley shaft 64. The driven pulley 63 has a driven-side fixed sheave 63a disposed
on the outside in the vehicle width direction and a driven-side movable sheave 63b
formed on the inside in the vehicle width direction. The driven-side fixed sheave
63a is integrally formed with the driven pulley shaft 64. Meanwhile, the driven-side
movable sheave 63b is formed separately from the driven pulley shaft 64, and the driven
pulley shaft 64 is inserted through a central portion thereof. Then, the driven-side
movable sheave 63b is adopted to be slidable on the periphery of the driven pulley
shaft 64 in a direction along an axial center P3 of the driven pulley shaft 64. A
distance between the driven-side movable sheave 63b and the driven-side fixed sheave
63a changes in accordance with axial movement of the driven-side movable sheave 63b.
Consequently, an effective diameter of the driven pulley 63 changes.
[0082] A driven-side lid 63d is attached to the left side of the driven-side movable sheave
63b so as to form an enclosed space therebetween to accommodate oil for hydraulic
control (hereinafter referred to as a "driven-side oil accommodating section 63c").
A coil spring for urging the driven-side movable sheave 63b to the driven-side fixed
sheave 63a side is accommodated in the driven-side oil accommodating section 63c.
The length of the metal belt 65 wound between the drive pulley 61 and the driven pulley
63 is constant. Therefore, when the effective diameter of the drive pulley 61 increases,
the driven-side movable pulley 63b slides to the driven-side fixed sheave 63a side
against urging force of the coil spring to decrease the effective diameter of the
driven pulley 63. On the contrary, when the effective diameter of the drive pulley
61 decreases, the effective diameter of the driven pulley 63 increases.
[0083] Furthermore, as shown in FIG. 5, the engine 2 includes an output shaft 70 for outputting
the driving force to a further downstream side transmitted from the crankshaft 40
to the driven pulley shaft 64. This output shaft 70 is formed separately from the
driven pulley shaft 64 and is disposed parallel to the driven pulley shaft 64 in a
position adjacent to the driven pulley shaft 64.
[0084] As shown in FIGs. 2 to 5, the entire output shaft 70 is disposed outside the crankcase
20. In other words, the output shaft 70 is entirely accommodated in the transmission
case 30 behind the crankcase 20. More specifically, an output chamber 32 is formed
between the left case section 30b and the left end case section 30c in the transmission
case 30. A left side portion of the output shaft 70 is accommodated in the output
chamber 32, and a right side portion of the output shaft 70 is accommodated in the
transmission chamber 31.
[0085] The output shaft 70 is constituted by coaxially coupling an output shaft right section
70a as the right side portion accommodated in the transmission chamber 31 to an output
shaft left section 70b as the left side portion accommodated in the output chamber
32. More specifically, as shown in FIG. 5, a left end of the output shaft right section
70a and a right end of the output shaft left section 70b are formed in cylindrical
shapes corresponding to each other and are fitted to each other.
[0086] In addition, the output shaft right section 70a and the output shaft left section
70b are coupled to each other in a manner that they can be divided into right and
left. More specifically, an engagement groove in a predetermined length that extends
over the output shaft right section 70a and the output shaft left section 70b in the
vehicle width direction is formed in a coupling portion between the output shaft right
section 70a and the output shaft left section 70b. Meanwhile, an engaging member 70c
in a cylindrical shape that extends over the output shaft right section 70a and the
output shaft left section 70b in the vehicle width direction and that engages with
the engagement groove is attached to a periphery of the coupling portion. A rod, which
is not shown, is attached to projections formed on a periphery of this engaging member
70c. The engaging member 70c can slide on the periphery of the output shaft 70 along
an axial center P4 thereof with operation of this rod. The engaging member 70c is
disposed across both the output shaft right section 70a and the output shaft left
section 70b in a coupling condition shown in FIG. 5. However, the engaging member
70c can also be disposed only on the periphery of the output shaft left section 70b
by sliding the engaging member 70c further to the left from the left end of the output
shaft right section 70a, for example with the operation of the rod by the driver of
the motorcycle 1. As a result, the output shaft right section 70a and the output shaft
left section 70b can be separated from each other by releasing the coupling therebetween.
In this separated condition, the output shaft left section 70b can rotate independently
from the output shaft right section 70a .
[0087] The output shaft 70 is rotatably supported by the transmission case 30. More specifically,
a right output shaft bearing 35a for supporting a right end of the output shaft 70
(that is, a right end of the output shaft right section 70a) is formed in the right
case section 30a, and a left output shaft bearing 35c for supporting a left end of
the output shaft 70 (that is, a left end portion of the output shaft left section
70b) is formed in the output chamber 32 of the left end case section 30c. In addition,
a middle output shaft bearing 35b for supporting a middle portion of the output shaft
70 (that is, the coupling portion between the output shaft right section 70a and the
output shaft left section 70b) is formed in the left case section 30b. That is, the
output shaft right section 70a and the output shaft left section 70b are coupled to
each other in a through hole formed in the middle output shaft bearing 35b as a boundary
between the transmission chamber 31 and the output chamber 32.
[0088] A gear 70d is integrally attached to the right end portion of the output shaft 70.
This gear 70d meshes with a gear 64a attached to the right end portion of the driven
pulley shaft 64. Therefore, the output shaft 70 rotates in conjunction with the driven
pulley shaft 64.
[0089] In addition, as shown in FIG. 5, a coupling shaft 71 that couples the output shaft
70 to the drive shaft 9 (see FIG. 1) is accommodated in the output chamber 32. This
coupling shaft 71 is formed so as to extend rearward from the left side of the output
shaft 70.
[0090] A bevel gear 71 a that meshes with a bevel gear 70e formed on the left end of the
output shaft 70 is attached to a front end of the coupling shaft 71. Therefore, the
coupling shaft 71 rotates in conjunction with the output shaft 70. A universal joint
71b for coupling a front end of the drive shaft 9 for rotation is attached to a rear
end of the coupling shaft 71.
[0091] The coupling shaft 71 is rotatably supported by the transmission case 30. More specifically,
a front coupling shaft bearing 36a for supporting the front end portion of the coupling
shaft 71 is formed in the front portion of the output chamber 32 in the left end case
section 30c, and a rear coupling shaft bearing 36b for supporting the rear end portion
of the coupling shaft 71 is formed in the rear portion of the output chamber 32.
[0092] As shown in FIG. 6, the engine 2 includes a transmission-side oil pump 80 for supplying
oil to the transmission 60. This transmission-side oil pump 80 is accommodated in
the transmission chamber 31 of the transmission case 30. More specifically, as shown
in FIGs. 3 and 4, the transmission-side oil pump 80 is located adjacent to the drive
pulley 61 and the driven pulley 63 and is disposed below the drive pulley 61 and the
driven pulley 63 in the transmission chamber 31.
[0093] As shown in FIG. 6, in this embodiment, the transmission-side oil pump 80 is a trochoid
pump and has a pair of inner rotors 80a and outer rotors 80d. This transmission-side
oil pump 80 is supported by a transmission-side pump support section 37, which is
a part of the left case section 30b of the transmission case 30.
[0094] The engine 2 also includes a transmission-side pump shaft 81 for driving the transmission-side
oil pump 80. The inner rotor 80a of the transmission-side oil pump 80 is connected
to a periphery at the right end of the transmission-side pump shaft 81 to integrally
rotate with the transmission-side pump shaft 81.
[0095] The transmission-side pump shaft 81 is formed separately from the crankshaft 40,
the clutch shaft 53, the drive pulley shaft 62, and the driven pulley shaft 64, and
is disposed parallel to the drive pulley shaft 62 and the driven pulley shaft 64 in
a position adjacent to the drive pulley shaft 62 and the driven pulley shaft 64. Also,
as shown in FIGs. 3 and 4, this transmission-side pump shaft 81 is disposed behind
the crankshaft 40, in front of the output shaft 70, and below the drive pulley shaft
62 and the driven pulley shaft 64. That is, the transmission-side pump shaft 81 is
disposed in a position surrounded by the crankshaft 40, the drive pulley shaft 62,
the driven pulley shaft 63, and the output shaft 70, and in a position below the dividing
surface S1 of the crankcase 20.
[0096] The transmission-side pump shaft 81 is rotatably supported in the transmission case
30. More specifically, as shown in FIG. 6, the transmission-side pump shaft 81 is
supported by the transmission-side pump support section 37 in the left case section
30b via the transmission-side oil pump 80. In addition, a transmission-side pump insertion
section 37c in which a left end of the transmission-side pump shaft 81 is inserted
is formed in a portion closing the left side of the transmission-side oil pump 80
in the left case section 30b.
[0097] Then, the transmission-side pump shaft 81 is coaxially coupled to the crankcase-side
pump shaft 85. That is, as shown in FIG. 6, the left end of the transmission-side
pump shaft 81 is coupled to the right end of the crankcase-side pump shaft 85. More
specifically, an engagement groove of a predetermined length that extends over the
transmission-side pump shaft 81 and the crankcase-side pump shaft 85 in the vehicle
width direction is formed in a coupling portion between the transmission-side pump
shaft 81 and the crankcase-side pump shaft 85. Then, an engaging member 88 in a cylindrical
shape that extends over the transmission-side pump shaft 81 and the crankcase-side
pump shaft 85 in the vehicle width direction and that engages with the engagement
groove is attached to a periphery of this coupling portion. Consequently, the axial
center of the crankcase-side pump shaft 85 is oriented to that of the transmission-side
pump shaft 81 to constitute a single shaft (hereinafter referred to as a "complex
pump shaft 101") extending in the vehicle width direction from the crankcase 20 to
the transmission case 30. Thus, the crankcase-side shaft pump 85 and transmission-side
pump shaft 81 rotate integrally.
[0098] This complex pump shaft 101 is formed separately from the crankshaft 40 and the complex
main shaft 100, and is disposed parallel to the complex main shaft 100 in a position
adjacent to the complex main shaft 100. A left end of the complex pump shaft 101 is
supported by the left crankcase-side pump shaft bearing 29c in the crankcase 20. A
middle portion of the complex pump shaft 101 is supported by the right pump support
section 29a and the left pump support section 29b via the crankcase-side oil pump
82. Furthermore, a right end of the complex pump shaft 101 is supported by the transmission-side
pump support section 37 in the transmission case 30 via the transmission-side oil
pump 80.
[0099] The complex pump shaft 101 rotates in conjunction with the crankshaft 40 regardless
of connection or disconnection of driving force transmission by the clutch 50. Consequently,
the transmission-side pump shaft 81 attached to the right end of the complex pump
shaft 101 can continuously be driven in the disengaged state of the clutch 50 as well
as in the engaged state of the clutch 50. Therefore, the transmission-side oil pump
80 is able to supply both an oil for hydraulic control and a lubricating oil to the
transmission 60 while the crankshaft 40 is rotating.
[0100] The right crankcase-side pump insertion section 29d through which the right end of
the crankcase-side pump shaft 85 is inserted and the transmission-side pump insertion
section 37c through which the left end of the transmission-side pump shaft 81 is inserted
are each formed in shapes which correspond with each other and are fitted to each
other. More specifically, in the right crankcase-side pump insertion section 29d,
a cylindrical projection projecting to the right from the crankcase 20 is formed around
the crankcase-side pump shaft 85. Meanwhile, in the transmission-side pump insertion
section 37c, a cylindrical projection, which projects to the left from the left case
section 30b, is formed around the transmission-side pump shaft 81. Here, an outer
diameter of the cylinder of the right crankcase-side pump insertion section 29d is
generally equal to an inner diameter of the cylinder of the transmission-side pump
insertion section 37c. Thus, the cylinder of the right crankcase-side pump insertion
section 29d is fitted into that of the transmission-side pump insertion section 37c.
[0101] Then, the crankcase-side pump shaft 85 and the transmission-side pump shaft 81 are
coupled to each other in a portion where the right crankcase-side pump insertion section
29d is fitted into the transmission-side pump insertion section 37c. That is, the
coupling portion between the crankcase-side pump shaft 85 and the transmission-side
pump shaft 81 in the complex pump shaft 101 is inserted in the fitting portion between
the right crankcase-side pump insertion section 29d and the transmission-side pump
insertion section 37c.
[0102] The above-mentioned coupling between the lower case section 20b and the transmission
case 30 is also conducted around the complex pump shaft 101. More specifically, as
shown in FIGs. 2 and 3, the above-mentioned plural fastening holes 90 are formed in
a surrounding area around the crankcase-side pump shaft 85 in the lower case section
20b and in a surrounding areas around the transmission-side pump shaft 81 in the right
case section 30a and the left case section 30b. Then, as shown in FIGs. 4 and 6, the
three case sections, which are the lower case section 20b, the left case section 30b,
and the right case section 30a, are fastened and secured in the vehicle width direction
around the complex pump shaft 101 with the plural bolt members 91.
[0103] As shown in FIGs. 2 to 4, 6 and 7, a transmission-side oil pan 38 for storing oil
supplied to the transmission 60 by the transmission-side oil pump 80 is formed in
the transmission case 30. As shown in FIG. 7, this transmission-side oil pan 38 is
provided so as to close an opening 30d from below. The opening 30d is formed at the
bottom of the left case section 30b among the three case sections 30a to 30c that
constitute the transmission case 30. In other words, the opening 30d of the left case
section 30b integrally formed as a case section is closed by the integrally formed
transmission-side oil pan 38.
[0104] Therefore, sealing between a mating surface 30e around the opening 30d at the lower
end of the left case section 30b and a mating surface 38a at the upper end of the
transmission-side oil pan 38 can securely and easily be achieved. In the left case
section 30b, a through hole 30f is formed in a portion of a wall that divides the
transmission chamber 31 from the opening 30d, and a through hole 30g is formed in
a portion of a wall that divides the output chamber 32 from the opening 30d. As a
result, lubricating oil supplied to the transmission chamber 31 flows down to the
transmission-side oil pan 38 from the through hole 30f and lubricating oil supplied
to the output chamber 32 flows down to the transmission-side oil pan 38 from the through
hole 30g.
[0105] As shown in FIGs. 3, 4, and 6, the transmission-side oil pan 38 in the left case
section 30b extends rearward from a position below the transmission-side oil pump
80 to the rear end of the left case section 30b on the right of the crankcase-side
oil pan 23 and the oil tank 24 in the crankcase 20. Furthermore, as shown in FIGs.
2 and 7, the rear end portion of the transmission-side oil pan 38 below the output
shaft 70 extends to the left at the back of the oil tank 24. As described above, the
transmission-side oil pan 38 is formed to extend on the right and to the back of the
crankcase-side oil pan 23 and the oil tank 24 to secure a sufficient oil storage capacity.
[0106] As shown in FIGs. 4, 6, and 7, a control unit 200 for controlling oil supply to the
transmission 60 and the output shaft 70 is disposed in the transmission-side oil pan
38. Meanwhile, as shown in FIG. 4, an intake flow passage 37a for sucking oil into
the transmission-side oil pump 80 and a discharge flow passage 37b for discharging
oil from the transmission-side oil pump 80 are formed in the transmission-side pump
support section 37. One end of this intake flow passage 37a is connected to an intake
port 80c of the transmission-side oil pump 80, and the other end thereof is connected
to the control unit 200. One end of the discharge flow passage 37b is connected to
a discharge port 80d of the transmission-side oil pump 80, and the other end thereof
is connected to the control unit. In addition, as shown in FIGs. 4 and 7, a strainer
201 for sucking oil into the control unit 200 from the transmission-side oil pan 38
extends downward from the control unit 200. An intake section 201 a disposed near
the bottom of the transmission-side oil pan 38 for sucking oil therein is formed at
a bottom end portion of this strainer 201.
[0107] As shown in FIG. 4, 5, and 7, an oil flow passage 39a, an oil flow passage 39b, and
an oil flow passage 39c are independently formed in the right case section 30a. One
end of the oil flow passage 39a opens to the right end of the right drive pulley shaft
bearing 33a while the other end thereof opens to a portion of the left end surface
in the lower side portion of the right case section 30a (that is, a mating surface
disposed on the dividing surface S2). One end of the oil flow passage 39b opens to
the right end of the right driven pulley shaft bearing 34a while the other end thereof
opens to another portion of the left end surface in the lower side portion of the
right case section 30a. One end of the oil flow passage 39c opens to the right output
shaft bearing 35a while the other end thereof opens to further another portion of
the left end surface in the lower side portion of the right case section 30a.
[0108] Meanwhile, as shown in FIGs. 4 and 7, three oil flow passages 39d to 39f are independently
formed from each other in the left case section 30b. One ends of the three oil flow
passages 39d to 39f respectively open to positions on the right end surface of the
left case section 30b that correspond to the three oil flow passages 39a to 39c formed
on the left end surface of the right case section 30a, and the other ends thereof
are connected to the control unit 200. As described above, the oil flow passages 39a
to 39f are formed across the left case section 30b and the right case section 30a
to be connected with the right drive pulley shaft bearing 33a, the right driven pulley
shaft bearing 34a, the right output shaft bearing 35a, and the control unit 200 in
the transmission case 30.
[0109] As shown in FIGs. 5 to 7, hollow sections 62a, 64b, and 70f are respectively formed
inside the drive pulley shaft 62, the driven pulley shaft 64, and the output shaft
70 to respectively extend along the axial centers P2, P3, and P4 thereof to open to
their right ends. In addition, oil flow passages 62b, 64c, and 70g that respectively
extend outward in a radial direction from the hollow sections 62a, 64b, and 70f to
open to the peripheries of the drive pulley shaft 62, the driven pulley shaft 64,
and the output shaft 70 are formed inside the drive pulley shaft 62, the driven pulley
shaft 64, and the output shaft 70. Moreover, oil flow passages 61 e, 63e are respectively
formed in the drive-side movable sheave 61 b and the driven-side movable sheave 63b.
The oil flow passage 61e connects the hollow section 62a of the drive pulley shaft
62 with the drive-side oil accommodating section 61c, and the oil flow passage 63e
connects the hollow section 64b of the driven pulley shaft 64 with the driven-side
oil accommodating section 63c.
[0110] Therefore, it is possible to supply oil for hydraulic control to the drive-side oil
accommodating section 61 c and the driven-side oil accommodating section 63c by driving
the transmission-side oil pump 80. More specifically, once the transmission-side oil
pump shaft 81 rotates in conjunction with the crankshaft 40, and thus the transmission-side
oil pump 80 is driven, oil stored in the transmission-side oil pan 38 flows into the
control unit 200 via the strainer 201 and is further drawn into the transmission-side
oil pump 80 via the intake flow passage 37a (see FIG. 4). The oil drawn into the transmission-side
oil pump 80 is discharged therefrom, flows into the control unit 200 via the discharge
flow passage 37b (see FIG. 4), and then further flows into the oil flow passages 39d
to 39f formed in the left case section 30b.
[0111] At this time, the control unit 200 can independently adjust opening and closing of
control valves (not shown) that are respectively provided in connecting portions between
the control unit 200 and the oil flow passages 39d to 39f formed in the left case
sections 30b. More specifically, for example, the control unit 200 opens the control
valve of the oil flow passage 39d that communicates with the drive pulley shaft 62
and closes the control valve of the oil flow passage 39e that communicates with the
driven pulley shaft 64 in order to increase the effective diameter of the drive pulley
61. As a result, oil is selectively delivered by pressure from the control unit 200
to the drive-side oil accommodating section 61 c of the drive pulley 61 through the
oil flow passage 39d in the left case section 30b and the oil flow passage 39a in
the right case section 30a. Then, the drive-side movable sheave 61 b (see FIGs. 5
and 6) slides to the left to increase the effective diameter of the drive pulley 61.
[0112] In addition, oil stored in the transmission-side oil pan 38 is utilized for the purpose
of both hydraulic control of the transmission 60 and lubrication of the transmission
60, the output shaft 70, and the coupling shaft 71. That is, in the engine 2, the
single transmission-side oil pump 80 supplies oil in the transmission-side oil pan
38 to the transmission 60 for hydraulic control as described above, and also supplies
oil in the transmission-side oil pan 38 to the transmission 60, the output shaft 70,
and the coupling shaft 71 for lubrication. An oil flow passage (not shown) is formed
in the transmission case 30 with its one end opening to both the transmission chamber
31 and the output chamber 32. Thus, lubrication oil delivered by pressure from the
transmission-side oil pump 80 can be supplied to the transmission chamber 31 and the
output chamber 32 through the oil flow passage.
[0113] FIG. 8 is an explanatory view for showing relative positions of shafts disposed parallel
in the engine case 2a when viewed from the left side of the engine 2. More specifically,
FIG. 8 shows a shaft 47b of the balancer 47, the crankshaft 40, the drive pulley shaft
62, the driven pulley shaft 64, the output shaft 70, and the transmission-side pump
shaft 81. A direction indicated by an arrow F in FIG. 8 is a front direction of the
engine 2.
[0114] As described above, because the drive pulley shaft 62 and the clutch shaft 53 are
coaxially coupled to constitute the complex main shaft 100 (see FIG. 5), the clutch
shaft 53 and the complex main shaft 100 are placed in the same position as the drive
pulley shaft 62 in FIG. 8. Also, because the transmission-side pump shaft 81 and the
crankcase-side pump shaft 85 are coaxially coupled to constitute the complex pump
shaft 101 (see FIG. 6), the crankcase-side pump shaft 85 and the complex pump shaft
101 are placed in the same position as the transmission-side pump shaft 81 in FIG.
8.
[0115] Furthermore, FIG. 8 shows: the dividing surface S1 of the crankcase passing through
an axial center P6 of the balancer shaft 47b and the axial center P1 of the crankshaft
40; a flat surface (horizontal surface) S4 showing a horizontal direction of the engine
2 when it is mounted on the motorcycle 1; a flat surface S5 passing through the axial
center P1 of the crankshaft 40 and the axial center P4 of the output shaft 70; a flat
surface S6 that passes through the axial center P1 of the crankshaft 40 and is perpendicular
to the flat surface S5; a flat surface S7 that passes through the axial center P4
of the output shaft 70 and is perpendicular to the flat surface S5; a flat surface
S8 that passes through the axial center P2 of the drive pulley shaft 62 and is parallel
to the dividing surface S1 of the crankcase 20; and a flat surface S9 that passes
through the axial center P2 of the drive pulley shaft 62 and is perpendicular to the
flat surface S5.
[0116] For example, in the engine case 2a shown in FIG. 2, the horizontal surface S4 extends
on an extended line of the flat bottomed surfaces of the crankcase-side oil pan 23,
the oil tank 24, and the transmission-side oil pan 38. The horizontal surface S4 is
also an end surface positioned at the bottom of the engine case 2a.
[0117] As described above, the engine 2 includes: the crankshaft 40 driven by reciprocating
motion of the pistons (not shown) accommodated in the cylinder section 2b (see FIG.
2); the drive pulley shaft 62 driven by rotation of the crankshaft 40; the driven
pulley shaft 64 driven by rotation of the drive pulley shaft 62; the output shaft
70 driven by rotation of the driven pulley shaft 64; and the transmission-side pump
shaft 81 driven by rotation of the crankshaft 40. Then, the crankshaft 40, the drive
pulley shaft 62, the driven pulley shaft 64, the output shaft 70, and the transmission-side
pump shaft 81 are separately formed from each other and are disposed parallel to each
other.
[0118] As described above, the complex pump shaft 101 composed of the transmission-side
pump shaft 81 and the crankcase-side pump shaft 85 is coupled to the clutch upstream
section 51 via the intermediate gear 86 as an idler gear. This complex pump shaft
101 may be coupled to a shaft provided upstream of the clutch 50 in terms of driving
force transmission via the idler gear.
[0119] The crankcase-side oil pump 82 for supplying oil to the crankcase 20 is attached
to the complex pump shaft 101 composed of the transmission-side pump shaft 81 and
the crankcase-side pump shaft 85.
[0120] In addition to the above configuration, in the engine case 2a, the drive pulley shaft
62 and the driven pulley shaft 64 are disposed between the crankshaft 40 and the output
shaft 70 and are disposed above the flat surface S5. More specifically, both the axial
center P2 of the drive pulley shaft 62 and the axial center P3 of the driven pulley
shaft 64 are positioned between the flat surface S6 and the flat surface S7 and are
positioned above the flat surface S5.
[0121] The transmission-side pump shaft 81 is disposed between the crankshaft 40 and the
output shaft 70. More specifically, the axial center P5 of the transmission-side pump
shaft 81 is positioned between the flat surface S6 and the flat surface S7.
[0122] Furthermore, the transmission-side pump shaft 81 is disposed closer to the flat surface
S5 side than the drive pulley shaft 62 and the driven pulley shaft 64. More specifically,
the axial center P5 of the transmission-side pump shaft 81 is positioned below the
flat surface S5.
[0123] However, for instance, the axial center P5 of the transmission-side pump shaft 81
may be positioned above the flat surface S5 and be positioned closer to the flat surface
S5 than a flat surface (not shown) that is parallel to the flat surface S5 and passes
through one of the axial center P2 of the drive pulley shaft 62 and the axial center
P3 of the driven pulley shaft 64.
[0124] As described above, the transmission-side pump shaft 81 is disposed in a position
surrounded by the crankshaft 40, the drive pulley shaft 62, the driven pulley shaft
64, and the output shaft 70 in a side view of the engine 2 as shown in FIG. 8. Therefore,
downsizing of the engine 2 is attained not only in a width direction thereof but also
in the longitudinal direction and a vertical direction.
[0125] The driven pulley shaft 64 is disposed below the drive pulley shaft 62. More specifically,
the axial center P3 of the driven pulley shaft 64 is located below the flat surface
S8.
[0126] The complex pump shaft 101 including the transmission-side pump shaft 81 is disposed
behind the drive pulley shaft 62. More specifically, the axial center P5 of the complex
pump shaft 101 is located behind the flat surface S9.
[0127] The complex main shaft 100 including the drive pulley shaft 62 is rotatably supported
by the upper case section 20a above the dividing surface S1 of the crankcase 20. That
is, the axial center P2 of the complex main shaft 100 is positioned above the dividing
surface S1.
[0128] Furthermore, the complex pump shaft 101 including the transmission-side pump shaft
81 is rotatably supported by the lower case section 20b below the dividing surface
S1 of the crankcase 20. That is, the axial center P5 of the complex pump shaft 101
is positioned below the dividing surface S1.
[0129] As described above, the engine 2 has two shafts for coupling the crankcase 20 to
the transmission case 30, that is, the complex main shaft 100 and the complex pump
shaft 101. The complex main shaft 100 is supported so that the axial center P2 thereof
is positioned above the dividing surface S1, and the complex pump shaft 101 is supported
so that the axial center P5 thereof is positioned below the dividing surface S1. Therefore,
in addition to the increased rigidity of the engine case 2a, the length of the engine
2 especially in the width direction and in the longitudinal direction can effectively
be decreased.
[0130] Next, a second aspect of the engine 2 according to this embodiment will be described
with reference to FIGs. 9 to 15. In the following description as well as in FIGs.
9 to 15, the same components as ones used in the aforementioned example shown in the
FIGs. 1 to 8 are denoted by the same reference numerals, and detailed description
thereof will be omitted. In addition, for parts of the components that are the same
as ones in the aforementioned example shown in FIGs. 1 to 8, graphical representation
and description thereof will be omitted.
[0131] FIG. 9 is a plan view of the motorcycle 1. This motorcycle 1 is equipped with the
same engine 2 as the one shown in FIG. 1, and, as shown in FIG. 9, is further equipped
with the seat 5 having the front seating section 5a and the rear seating section 5b,
the center cover 12c extending forward while inclining upward from the position below
the front end of the seat 5, a pair of the left and the right footboards 12e having
a pair of the left and the right flat surfaces 12f on which the rider seated on the
front seating section 5a places his/her left and right feet, for example.
[0132] Also, FIG. 9 shows a line (body centerline) C1 indicating the center of the motorcycle
1 in the vehicle width direction. This body centerline C1 is a straight line that
passes the center of the front wheel 3 in the vehicle width direction and that of
the rear wheel in the vehicle width direction in a state where the front wheel 3 and
the rear wheel 4 are linearly disposed so that the motorcycle 1 travels straight.
[0133] FIG. 10 is a left side view of the engine case 2a. FIG. 11 is a right side view of
the engine case 2a. FIGs. 10 and 11 show the engine case 2a in a state that the cover
members 20c, 20d of the crankcase 20 for covering the lateral sides of the crankshaft
40 in the vehicle width direction are attached.
[0134] As shown in FIG. 10, this engine case 2a includes a bracket 103 that is disposed
across the three case sections, which are the upper case section 20a and the lower
case section 20b of the crankcase 20 and the left case section 30b of the transmission
case 30, and is fastened and secured by bolt members with each of the three case members.
The above three case sections are further integrally coupled to each other with this
bracket 103; therefore, the rigidity of the engine case 2a as a whole is increased
more effectively.
[0135] FIG. 12 is a rear view of the engine case 2a. FIG. 13 is a bottom view of the engine
case 2a. FIG. 13 shows the axial center P1 of the crankshaft 40, the axial center
P2 of the drive pulley shaft 62, the axial center P3 of the driven pulley shaft 64,
the axial center P4 of the output shaft 70, and the axial center P5 of the transmission-side
pump shaft 81 in a case that the engine case 2a is viewed from below.
[0136] FIG. 14 is a sectional view of the engine 2 that is cut off along the dividing surface
S1 of the crankcase 20 and is seen from above the dividing surface S1. FIG. 15 is
a sectional view of the engine case 2a taken along the line XV-XV (that is, an engine
centerline C2) shown in FIG. 14. FIG. 14 shows a line (engine centerline) C2 indicating
the center of the engine in the vehicle width direction. The engine centerline C2
is a line that passes through a central point of a middle pair of the webs 42b and
is perpendicular to the axial center P1 of the crankshaft 40 in a direction along
the axial center P1 (that is, a longitudinal direction of the crankshaft 40). In addition,
this engine centerline C2 is parallel to the body centerline C1 shown in FIG. 9 and
is positioned slightly away from the body centerline C1 in the vehicle width direction.
FIG. 14 exposes a mating surface 20g on which the lower case section 20b of the crankcase
20 is joined with the upper case section 20a.
[0137] As with the above-mentioned example, the engine 2 according to the second aspect
includes the transmission 60 having the drive pulley 61 and the driven pulley 63 with
the metal V belt 65 being wound therebetween (see FIG. 5), and also includes the crankshaft
40, the drive pulley shaft 62, the driven pulley shaft 64, the output shaft 70, and
the transmission-side pump shaft 81 that are aligned parallel with each other as shown
in FIGs. 10 and 11.
[0138] The drive pulley shaft 62 and the clutch shaft 53 are coaxially coupled to constitute
the complex main shaft 100, and the transmission-side pump shaft 81 and the crankcase-side
pump shaft 85 are coaxially coupled to constitute the complex pump shaft 101. Also,
FIG. 10 shows a shaft 86a of the intermediate gear 86 (see FIG. 6) that couples the
crankshaft 40 to the complex pump shaft 101.
[0139] As shown in FIGs. 10 to 13 and 15, the engine 2 is equipped with a crankcase oil
pan 110, which receives oil supplied to the crankshaft 40, and a transmission oil
pan 140, which receives oil supplied to the transmission 60.
[0140] The crankcase oil pan 110 and the transmission oil pan 140 are separately formed
from each other. More specifically, the crankcase oil pan 110 is provided so as to
seal an opening (not shown) formed at the bottom of the lower case section 20b of
the crankcase 20 from below. Meanwhile, the transmission oil pan 140 is provided so
as to seal the opening 30d (see FIG. 11) formed at the bottom of the left case section
30b of the transmission case 30 from below.
[0141] The crankcase oil pan 110 has a crankcase-side oil pan 120 and an oil tank 130. The
crankcase-side oil pan 120 is formed in a portion of the bottom section of the crankcase
20 below the crank chamber 21 and stores lubricating oil in a same manner as the crankcase-side
oil pan 23 in the above-mentioned example. Lubricating oil flows down by gravitation
from the crank chamber 21 and the clutch chamber 22 in the crankcase 20 into the crankcase-side
oil pan 120.
[0142] The crankcase-side oil pan 120 has a bottom surface 121 including a middle bottom
surface 121 a, a left bottom surface 121 b, and a right bottom surface 121c. The middle
bottom surface 121a is disposed undermost in the crankcase-side oil pan 120 and extends
flatly along the horizontal surface S4. The intake section 25a (see FIG. 15) of the
strainer 25 disposed in the crankcase-side oil pan 120 is disposed above the middle
bottom surface 121a.
[0143] Both the left bottom surface 121 b and the right bottom surface 121c are formed to
be located upward as they move away from the center C1 in the vehicle width direction
to the lateral sides (that is, the lateral sides in the vehicle width direction).
In other words, the left bottom surface 121 b is formed to incline upward to the left
from a left end of the middle bottom surface 121a, and the right bottom surface 121
c is formed to incline upward to the right from a right end of the middle bottom surface
121 a. In addition, in the bottom surface 121, a portion in front of and a portion
in the rear of the middle bottom surface 121a are respectively formed to incline upward
to the front and to the rear from a front end of and a rear end of the middle bottom
surface 121 a.
[0144] The oil tank 130 is formed in another portion of the bottom section of the crankcase
20 (a portion at the back of the crankcase-side oil pan 120) that is adjacent to the
crankcase-side oil pan 120 below the clutch chamber 22 and stores lubricating oil
transferred from the crankcase-side oil pan 120 in a same manner as the oil tank 24
in the above-mentioned example.
[0145] The oil tank 130 has a bottom surface 131 including a middle bottom surface 131 a,
a left bottom surface 131b, and a right bottom surface 131c. The middle bottom surface
131 a is disposed undermost in the oil tank 130 and extends flatly along the horizontal
surface S4. The intake section 26a (see FIG. 15) of the strainer 26 disposed in the
oil tank 130 is placed above the middle bottom surface 131 a.
[0146] Both the left bottom surface 131 b and the right bottom surface 131c are formed to
be located upward as they move away from the center C1 in the vehicle width direction
to the lateral sides (that is, the lateral sides in the vehicle width direction).
More specifically, the left bottom surface 131 b is formed to incline upward to the
left from a left end of the middle bottom surface 131 a, and the right bottom surface
131 c is formed to incline upward to the right from a right end of the middle bottom
surface 131 a. In addition, in the bottom surface 131, a portion in front of and a
portion in the rear of the middle bottom surface 131a are respectively formed to incline
upward to the front and to the rear from a front end of and a rear end of the middle
bottom surface 131 a.
[0147] The transmission oil pan 140 stores oil supplied to the transmission 60 by the transmission-side
oil pump 80 in the same manner as the transmission-side oil pan 38 in the above-mentioned
example. The transmission oil pan 140 has a bottom surface 141 including a middle
bottom surface 141 a, a left bottom surface 141b, and a right bottom surface 141c.
The middle bottom surface 141 a is disposed undermost in the transmission oil pan
140 and extends flatly above the undermost surface among the bottom surfaces of the
crankcase oil pan 110 (that is, the middle bottom surface 121a of the crankcase-side
oil pan 120 and the middle bottom surface 131a of the oil tank 130). The intake section
201a of the strainer 201 disposed in the transmission oil pan 140 is disposed above
the middle bottom surface 141a (see FIGs. 11 to 13).
[0148] As shown in FIGs. 10, 11, and 15, the horizontal surface S4 extends along the middle
bottom surface 121a of the crankcase-side oil pan 120 and the middle bottom surface
131a of the oil tank 130 as the undermost surfaces of the engine case 2a on an extended
line of these bottom surfaces.
[0149] Both the left bottom surface 141 b and the right bottom surface 141c are formed to
be located upward as they move away from the center C1 in the vehicle width direction
to the lateral sides (that is, the lateral sides in the vehicle width direction).
More specifically, the left bottom surface 141 b is formed to incline upward to the
left from a left end of the middle bottom surface 141 a, and the right bottom surface
141 c is formed to incline upward to the right from a right end of the middle bottom
surface 141 a. In addition, in the bottom surface 141, a portion in front of and a
portion in the rear of the middle bottom surface 141 a are respectively formed to
incline upward to the front and to the rear from a front end of and a rear end of
the middle bottom surface 141 a.
[0150] The transmission oil pan 140 is formed in an L-shape having a first section 142,
which is disposed on the right side with respect to the body centerline C1 along the
metal belt 65, and a second section 143 extending from a portion of the first section
142 in the driven pulley 63 side to the left side with respect to the body centerline
C1.
[0151] In other words, as shown in FIG. 13, the drive pulley 61, the driven pulley 63, and
the metal belt 65 wound between the drive pulley 61 and the driven pulley 63 are all
disposed on the right side with respect to the body centerline C1. Then, in the transmission
oil pan 140, the first section 142 extending in the longitudinal direction is disposed
along the metal belt 65 on the right side with respect to the body centerline C1.
[0152] The second section 143 is disposed across the body centerline C1. In other words,
the second section 143 extends in the vehicle width direction from a rear portion
of the first section 142 and is disposed from the right side to the left side with
respect to the body centerline C1. More specifically, the second section 143 is disposed
along the output shaft 70 below the output shaft 70.
[0153] As in the above-described example, the control unit 200 for controlling the oil supply
to the transmission 60 and to the output shaft 70 is disposed inside the transmission
oil pan 140. The control unit 200 includes a valve mechanism for controlling pressure
that is necessary to supply oil stored in the transmission oil pan 140 to the transmission
60.
[0154] As shown in FIG. 13, this control unit 200 is formed in an L-shape that corresponds
to the L-shape of the transmission oil pan 140. More specifically, a portion of the
control unit 200 is formed to extend in the longitudinal direction within the first
section 142 of the transmission oil pan 140, and the other portion of the control
unit 200 is formed to extend in the vehicle width direction within the second section
143.
[0155] Meanwhile, the crankcase oil pan 110 is formed in an L-shape having: a third section
111 (a front portion of the crankcase-side oil pan 120) that is disposed along the
longitudinal direction of the crankshaft 40; and a fourth section 112 (a rear portion
of the crankcase-side oil pan 120 and the oil tank 130) that is disposed in a position
next to the first section 142 of the transmission oil pan 140 in the vehicle width
direction.
[0156] That is, the third section 111 is composed of a portion located in front of the rear
end of the middle bottom surface 121 a of the crank-side oil pan 120. This third section
111 extends in the vehicle width direction from the left side to the right side with
respect to the body centerline C1 in front of the first section 142 and the second
section 143 of the transmission oil pan 140.
[0157] The fourth section 112 is composed of a portion positioned in the rear of the rear
end of the middle bottom surface 121a in the crank-side oil pan 120 and the oil tank
130. This fourth section 112 extends in the vehicle width direction from the left
side to the right side with respect to the body centerline C1 in the left side of
the first section 142 and in front of the second section 143 of the transmission oil
pan 140.
[0158] That is, the crank-side oil pan 120 itself is formed in the L-shape, and the crankcase
oil pan 110 composed of the crank-side oil pan 120 and the oil tank 130 that are adjacent
to each other is also formed in the L-shape as a whole.
[0159] As described above, a portion of the crankcase oil pan 110 and a portion of the transmission
oil pan 140 are disposed parallel to each other respectively in the crankshaft 40
side and in the drive pulley shaft 62 side. More specifically, the entire crankcase
oil pan 110 and the second section 143 of the transmission oil pan 140 are disposed
parallel to each other in the longitudinal direction, respectively on the crankshaft
40 side and on the drive pulley shaft 62 side .
[0160] Then, the crankcase oil pan 110 and the transmission oil pan 140 are each formed
in the L-shape that corresponds to the other. In other words, as shown in FIG. 13,
the crankcase oil pan 110 and the transmission oil pan 140 are each formed in the
L-shape that engage with each other below the engine case 2a. More specifically, the
fourth section 112 of the crankcase oil pan 110 and the first section 112 of the transmission
oil pan 140 are disposed to overlap each other in the vehicle width direction. Therefore,
capacities of both the crankcase oil pan 110 and the transmission oil pan 140 can
effectively be secured in a limited space.
[0161] As described above, the left end of the crankshaft 40 is covered with the cover member
20c that is disposed on the left side surface of the crankcase 20, and the right end
of the crankshaft 40 is covered with the cover member 20d that is disposed on the
right side surface of the crankcase 20 (see FIG. 5). The length of the crankcase oil
pan 110 in the vehicle width direction and the length of the transmission oil pan
140 in the vehicle width direction are both within a range of length between a surface
S10 that passes by the left end of the left cover member 20c of the crankcase 20 in
the vehicle width direction and is perpendicular to the axial center P1 of the crankshaft
40 and a surface S11 that passes by the right end of the right cover member 20d of
the crankcase 20 in the vehicle width direction and is perpendicular to the axial
center P1 of the crankshaft 40. In other words, both the width of the crankcase oil
pan 110 (the length between the left end of the crankcase oil pan 110 to the right
end thereof) and the width of the transmission oil pan 140 (the length between the
left end of the transmission oil pan 140 and the right end thereof) are within a range
of the width of the engine case 2a.
[0162] The transmission oil pan 140 is disposed under the transmission case 30. A rear end
144 of the transmission oil pan 140 is located more rearward than a rear end 30h of
a portion in the transmission case 30 that covers the rear of the driven pulley 63.
Also, as described above, the transmission case 30 is composed of the three case sections
30a, 30b, 30c that can be divided into each section by the dividing surfaces S2, S3
(see FIG. 5) that are perpendicular to the axial center P2 of the drive pulley shaft
62. Then, as shown in FIG. 11, the transmission oil pan 140 is provided to close the
opening 30d from below, and the opening 30d is formed below the bottom of the left
case section 30b among the three case sections 30a, 30b, 30c that constitute the transmission
case 30.
[0163] Here, as shown in FIGs. 10 and 11, a lower end portion 30i of the left case section
30b is formed to project to the rear so that a rear end thereof is positioned more
rearward than the rear end 30h of a portion that covers the rear of the driven pulley
63. Then, the transmission oil pan 140 is provided so as to seal the lower end portion
30i of the left case section 30b, which projects to the rear, from below. As a result,
the rear end 144 of the transmission oil pan 140 is disposed more rearward than the
rear end 30h of a portion in the transmission case 30 that covers the rear of the
driven pulley 63.
[0164] The width of the transmission oil pan 140 in the longitudinal direction of the crankshaft
40 is longer than the width of the crankcase oil pan 110 in the longitudinal direction
of the crankshaft 40. In addition, the bottom surface 141 of the transmission oil
pan 140 is located higher than the bottom surface of the crankcase oil pan 110 (that
is, the bottom surface 121 of the crankcase-side oil pan 120 and the bottom surface
131 of the oil tank 130). Meanwhile, the engine 2 is a multi-cylinder engine having
three cylinders, and three exhaust pipes 2d, 2e, 2f come out of the cylinder section
2b. More specifically, as shown in FIGs. 10 and 11, each of the three exhaust pipes
2d, 2e, 2f extends downward and rearward from a front lateral surface of the cylinder
unit 2b.
[0165] Then, as shown in FIG. 10, the two left exhaust pipes 2d, 2e extend rearward on the
left side of the crankcase 20, and as shown in FIG. 11, the right exhaust pipe 2f
extends rearward on the right side of the crankcase 20.
[0166] In the engine 2, the two left exhaust pipes 2d, 2e can be disposed on the left side
of the crankcase oil pan 110 whose width is reduced, and the right exhaust pipe 2f
can be disposed on the right side of the crankcase oil pan. Furthermore, in the engine
2, these three exhaust pipes 2d, 2e, 2f may be disposed all together under the transmission
oil pan 140 whose height is reduced.
[0167] As shown in FIGs. 14 and 15, the engine 2 includes an oil unit 300 having an oil
filter 300a for filtering oil and an oil cooler 300b for cooling oil in the front
end portion of the crankcase 20. It is preferable that the oil unit 300 be disposed
in the front side of the vehicle body while being exposed to the outside as described
above from a standpoint of maintainability of the oil unit 300 and cooling capability
of the oil cooler 300b.
[0168] The oil filter 300a and the oil cooler 300b are each formed as a cylindrical member.
A circular end surface in a rear side of the oil filter 300a is joined with a circular
end surface in a front side of the oil cooler 300b. Then, they are coupled to each
other to constitute the integrated oil unit 300.
[0169] An oil flow passage member 301 is inserted in this oil unit 300. A hollow portion
formed inside this oil flow passage member 301 forms the same oil flow passage 28b
as the one shown in FIG. 2.
[0170] The oil unit 300 is disposed to be positioned as upward and rearward as possible.
More specifically, as shown in FIG. 14, a central portion 20f in the front end portion
of the crankcase 20 in a direction along the axial center P1 of the crankshaft 40
is formed to be dented rearward.
[0171] Then, the oil unit 300 is provided to project forward from the central portion 20f,
which is dented rearward, in the crankcase 20. That is, the oil unit 300 is disposed
in front of the central cylinder in the vehicle width direction among the three cylinders
included in the engine 2. More specifically, as shown in FIG. 14, the oil unit 300
is disposed in front of the pair of the crank webs 42b, which is provided in the center
in a direction along the axial center P1 of the crankshaft 40, among the three pairs
of the crank webs 42a, 42b, 42c provided in the crankshaft 40.
[0172] If the engine 2 is a multi-cylinder engine with three or more cylinders, the position
of the oil unit 300 in the longitudinal direction of this crankshaft 40 is not limited
in a range of a cylinder placed in the center in the longitudinal direction thereof.
For example, it can also be placed within a range of one or more cylinders except
one placed on both ends.
[0173] As shown in FIG. 14, the engine 2 includes the balancer 47 in front of the crankshaft
40. More specifically, as shown in FIG. 8, this balancer 47 is disposed parallel to
the crankshaft in front of the crankshaft 40 in a manner that the axial center P6
of the shaft 47b thereof is positioned on the dividing surface S1 of the crankcase
20.
[0174] The balancer shaft 47b is rotatably supported by the crankcase 20. More specifically,
as shown in FIG. 14, a left end portion of the balancer shaft 47b is supported by
a shaft support section 47a in the left side of the crankcase 20 via a needle bearing.
A right end portion thereof is supported by the shaft support section 47a in the right
side of the crankcase 20 via a ball bearing.
[0175] The balancer 47 has a pair of left and right balancer weights 47c, 47d provided on
both ends of the balancer shaft 47b. More specifically, as shown in FIG. 14, the left
balancer weight 47c is provided on the right side of the left shaft support section
47a, and the right balancer weight 47d is provided on the right side of the right
shaft support section 47a.
[0176] On the balancer shaft 47b, a gear 47e for driving the balancer shaft 47b in conjunction
with the crankshaft 40 is provided in a position adjacent to the left side of the
right balancer weight 47d via the right shaft support section 47a. This gear e meshes
with a gear formed on the periphery of the right crank web in the right pair 42c of
the crank webs of the crankshaft 40. The balancer shaft 47b is coupled to the crankshaft
40 via the gear 47e and is driven by the rotation of the crankshaft 40.
[0177] The left balancer weight 47c and the right balancer weight 47d are respectively disposed
on the left side and the right side of the oil unit 300. In other words, as shown
in FIG. 14, the left balancer weight 47c and the right balancer weight 47d are respectively
disposed on the left side and the right side of the central portion 20f of the crankcase
20.
[0178] The oil cooler 300b as the rear portion of the oil unit 300, the left balancer weight
47c, and the right balancer weight 47d are linearly disposed to overlap each other
in the longitudinal direction of the crankshaft 40. With such a configuration, in
the engine 2, the oil unit 300 can be disposed below and at leat partially behind
the crankshaft 40 while the balancer 47 is provided in front of the crankshaft 40.
[0179] As shown in FIG. 15, this oil unit 300 extends forward while inclining downward.
Meanwhile, the dividing surface S1 of the crankcase 20 also extends forward while
inclining downward. An angle A1 formed by this dividing surface S1 and the horizontal
surface S4 is kept in a predetermined range of 25 degrees to 45 degrees, for example.
[0180] On the contrary, a line that passes through the center of an attachment surface S14,
on which the oil filter 300a is attached to the oil cooler 300b, and is perpendicular
to the attaching surface S14 (that is, a centerline C3 of the oil unit 300) extends
forward while inclining so as to approach the dividing surface S1 of the crankcase
20. More specifically, an angle A2 formed by this oil unit centerline C3 and a flat
surface S15 that passes through the center of the attachment surface S14 and is parallel
to the dividing surface S1 can be set to approximately 10 degrees.
[0181] As a result, as shown in FIG. 15, the oil unit 300 is disposed in a manner that the
lower end thereof is located higher than the lower end of the crankcase oil pan 110
(that is, the horizontal surface S4 shown in FIG. 15). As described above, the oil
unit 300 can be disposed in a position in the proximity of the crankshaft 40 in the
engine 2.
[0182] In the engine 2, the cylinder section 2b is provided so as to incline forward with
respect to the dividing surface S1 of the crankcase 20. In other words, as shown in
FIG. 15, a line (cylinder centerline) D1 along a longitudinal direction of the cylinder
section 2b (a direction in which the pistons reciprocate) inclines more forward than
a line D2 that is perpendicular to the dividing surface S1 of the crankcase 20. More
specifically, an angle A3 formed by this cylinder centerline D1 and the perpendicular
line D2 can be equal to or larger than 25 degrees. As a result, an angle A4 formed
by the cylinder centerline D1 and a line D3 that is perpendicular to the horizontal
surface S4 can be equal to or larger than 60 degrees.
[0183] As shown in FIG. 15, the balancer shaft 47b is disposed above a horizontal surface
S12 that passes a lower end of a range Q1 of the crankshaft 40 including the crank
webs 42. Furthermore, a range Q2 of the pair of the left and the right balancer weights
47c, 47d is disposed below a horizontal surface S13 passing the axial center P1 of
the crankshaft 40.
[0184] It is possible in the engine 2 to effectively reduce its overall vertical length
with such a configuration by: providing the crankcase 20 whose dividing surface S1
inclines; controlling the height of the cylinder section 2b while disposing the balancer
shaft 47b in front of the crankcase 40 on the dividing surface S1; and disposing the
oil unit 300 above the lower end of the crankcase oil pan 110.
[0185] As shown in FIG. 15, clearance between a level surface L1 of oil stored in the crankcase-side
oil pan 120 and the balancer 47 is sufficiently secured in the engine 2. Therefore,
it is possible to effectively reduce loss of driving force by preventing the balancer
weights 47c, 47d from being soaked in the oil in the crankcase-side oil pan 120. FIG.
15 also shows an oil level surface L2 in the oil tank 130.
[0186] In the engine 2, the crankshaft 40, the complex main shaft 100, the driven pulley
shaft 64, the output shaft 70, and the complex pump shaft 101 are separately formed
from each other and are disposed parallel to each other. Therefore, it is possible
to shorten the length of the engine 2 in the vehicle width direction and thus to downsize
the engine 2.
[0187] The engine according to the present invention may be an engine equipped with one
or more cylinders. However, it is preferable that the engine according to the invention
be one with plural in-line cylinders and is further preferable that the engine be
one with three or more in-line cylinders. Also, the transmission-side oil pump 80
and the crankcase-side oil pump 80 (scavenge pump 83, feed pump 84) are not limited
to trochoid pumps, and at least partially, they can be another type of oil pumps.
[0188] As described above, a compact engine can be realized with the invention. Therefore,
the engine according to the invention is suitable for a straddle-type vehicle with
a limited space for mounting an engine, such as a motorcycle.
[0189] As shown in FIG. 15, the dividing surface S1 of the crankcase 20 is inclined forward
in the above-described engine 2 of this embodiment so as to dispose the axial center
of the balancer shaft 47b (further the overall balancer shaft 47b) between the horizontal
surface (first horizontal surface) S13 including the axial center of the crankshaft
40 and the horizontal surface (second horizontal surface) S12 intersecting the lower
end of the crank webs 42 when the engine 2 is mounted on the motorcycle 1. With this
configuration, it is possible to suppress the height of the crankcase 20 and that
of the cylinder section 2b and thus to make the entire engine 2 compact in the vertical
direction.
[0190] Also, in the engine 2 of this embodiment, as shown in FIG. 15, the line C3 perpendicular
to the attachment surface S14 of the oil unit 300 (a centerline along an extended
direction of the oil unit 300) inclines forward so as to approach the extended line
of the dividing surface S1 of the crankcase 20. It is possible with this configuration
to raise the lower end of the oil unit 300 to be positioned higher than the bottom
end of the crankcase oil pan 110 (that is, the horizontal surface S4).
[0191] In addition, in the engine 2 of this embodiment, as shown in FIG. 15, the crankcase
20 is formed in a manner that an attachment surface of the crankcase oil pan 110 is
generally parallel to the dividing surface S1. With this configuration, for example,
when the crankcase 20 is cast with dies, a draw direction of a core (insert) in the
dividing surface S1 side can be set opposite from a draw direction of a core in the
attachment surface side. Therefore, it is easy to form the internal shape of the crankcase
20.
[0192] Furthermore, in the engine 2 of this embodiment, as shown in FIG. 14, the balancer
weights 47c, 47d provided on the balancer shaft 47 are located on the outer sides
of the outermost crank webs (that is, the left crank web in the left crank web pair
42a and the right crank web of the right crank web pair 42c) among the three crank
web pairs 42a, 42b, 42c provided on the crankshaft 40. With this configuration, because
the balancer weights 47c, 47d do not interfere with the crank web pairs 42a, 42b,
42c, a distance between the balancer shaft 47b and the crankshaft 40 can be shortened
as shown in FIG. 15. Therefore, the engine 2 can be made compact. Furthermore, the
balancer weights 47c, 47d are in reversed phase to constitute couple balancers. Therefore,
it is possible to gain enough couple by disposing each of the balancer weights 47c,
47d on the outer sides of the outmost crank webs even if the balancer weights 47c,
47d are made short and small. However, the balancer weights 47c, 47d may be disposed
respectively between the left crank web pair 42a and between the right crank web pair
42c.
[0193] In the engine 2 of this embodiment, as shown in FIG. 15, the oil unit 300 is disposed
to overlap portions of the balancer weights 47c, 47d (see FIG. 14) in a side view.
More specifically, an upper portion of the oil unit 300 that is disposed below the
middle cylinder in the cylinder section 2b (that is, obliquely downward and forward
of the middle crank web pair 42b (see FIG. 14)) overlaps lower portions (a lower portion
of the range Q2) of the balancer weights 47c, 47d provided on both sides of the oil
unit 300. With this configuration, it is possible to reduce both forward and downward
protrusions of the oil unit 300 by disposing the oil unit 300 as rearward and upward
as possible.
[0194] In the engine 2 of this embodiment, as shown in FIG. 14, the central portion 20f
in the front portion of the crankcase 20, to which the oil unit 300 is attached, is
concaved rearward in comparison with the portions on both sides that correspond with
the balancer weights 47c, 47d. Also, as shown in FIG. 15, the attachment portion of
the oil unit 300 is concaved rearward to the crankshaft 40 side with respect to the
balancer shaft 47b. With this configuration, it is possible to reduce both forward
and downward protrusions of the oil unit 300 by disposing the oil unit 300 as rearward
and upward as possible.
[0195] The compactification of the engine 2 according to this embodiment, which has been
described so far, can be realized in the vertical direction. Therefore, the engine
2 is suitable for a straddle-type vehicle such as a scooter-type vehicle as shown
in FIG. 1, in which the engine 2 is disposed below a section that the driver straddles
(that is, an area between the handlebars 6 and the seat 5).
Description of Reference Numerals and Symbol
[0196]
- 1:
- motorcycle
- 2:
- engine
- 2a:
- engine case
- 2b:
- cylinder section
- 3:
- front wheel
- 4:
- rear wheel
- 5:
- seat
- 6:
- handlebar
- 7:
- front fork
- 8:
- driveline
- 9:
- drive shaft
- 10:
- silencer
- 11:
- pivot shaft
- 12:
- body cover
- 13:
- cylinder block
- 14:
- cylinder head
- 15:
- cover
- 20:
- crankcase
- 20a:
- upper case section
- 20b:
- lower case section
- 21:
- crank chamber
- 22:
- clutch chamber
- 22a:
- left clutch shaft bearing
- 22b:
- middle clutch shaft bearing
- 22c:
- right clutch shaft bearing
- 23:
- crankcase-side oil pan
- 24:
- oil tank
- 29a:
- right pump support section
- 29b:
- left pump support section
- 29c:
- left crankcase-side pump shaft bearing
- 29d:
- right crankcase-side pump insertion section
- 30:
- transmission case
- 30a:
- right case section
- 30b:
- left case section
- 30c:
- left end case section
- 30d:
- opening
- 31:
- transmission chamber
- 32:
- output chamber
- 33a:
- right drive-side pulley shaft bearing
- 33b:
- left drive-side pulley shaft bearing
- 34a:
- right driven-side pulley shaft bearing
- 34b:
- left driven-side pulley shaft bearing
- 37:
- transmission-side pump support section
- 37c:
- transmission-side pump insertion section
- 38:
- transmission-side oil pan
- 40:
- crankshaft
- 50:
- clutch
- 53:
- clutch shaft
- 60:
- transmission
- 61:
- drive pulley
- 62:
- drive pulley shaft
- 63:
- driven pulley
- 64:
- driven pulley shaft
- 65 :
- metal belt
- 70:
- output shaft
- 71:
- coupling shaft
- 80:
- transmission-side oil pump
- 81:
- transmission-side pump shaft
- 82:
- crankcase-side oil pump
- 85:
- crankcase-side pump shaft
- 85a:
- crankcase-side oil pump shaft
- 85b:
- cooling water pump shaft
- 86:
- intermediate gear
- 88:
- engaging member
- 90:
- fastening hole
- 91:
- bolt member
- 100:
- complex main shaft
- 101:
- complex pump shaft
- 110:
- crankcase oil pan
- 120:
- crankcase-side oil pan
- 130:
- oil tank
- 140:
- transmission oil pan
- 141:
- bottom surface
- 200:
- control unit
Additional Clauses to the Summary
[0197] The following numbered clauses form part of the description that is a continuation
of the Summary of Invention provided on pages 1 to 3.
- 1. According to an aspect of the invention is an engine for mounting on a vehicle,
the engine comprising: a crankshaft including a crank web; a balancer shaft disposed
in front of the crankshaft and provided with a balancer weight; a crankcase for accommodating
the crankshaft and the balancer shaft and being dividable by a dividing surface intersecting
an axial center of the crankshaft and an axial center of the balancer shaft; and a
cylinder section attached to the crankcase and inclined forward with respect to a
line perpendicular to the dividing surface of the crankcase, wherein when the engine
is mounted on a vehicle the axial center of the balancer shaft is disposed between
a first horizontal surface intersecting the axial center of the crankshaft and a second
horizontal surface intersecting a lower end of the crank web.
- 2. The engine according to Clause 1, wherein the balancer shaft is disposed between
the first horizontal surface and the second horizontal surface.
- 3. The engine according to Clause 1 or Clause 2, further comprising an oil unit attached
to a front side of a lower crankcase section below the dividing surface of the crankcase,
wherein a line perpendicular to an attachment surface of the oil unit inclines forward
so as to approach an extended line of the dividing surface of the crankcase.
- 4. The engine according to Clause 1, 2 or 3, further comprising an oil pan for closing
an opening formed at a bottom end of the crankcase, wherein the crankcase is formed
such that the dividing surface of the crankcase is generally parallel to an attachment
surface of the oil pan.
- 5. The engine according to any preceding Clause, wherein the balancer weight is positioned
on the outer side of the outermost crank web among the crank webs disposed along the
crankshaft.
- 6. The engine according to Clause 5, further comprising a cylinder section having
three cylinders, wherein the balancer shaft is provided with the balancer weights
in reversed phase and positioned on the outer sides of the outermost crank webs among
the crank webs aligned to correspond with each cylinder.
- 7. The engine according to any preceding Clause, further comprising
an oil unit attached to a front side of the crankcase, wherein the oil unit is disposed
in a position overlapping at least a portion of the balancer weight in a side view.
- 8. The engine according to Clause 7, further comprising a cylinder section having
three cylinders, wherein the oil unit is disposed in a position below the middle cylinder
among the three cylinders and where the oil unit overlaps at least portions of the
balancer weights disposed on both sides of the middle cylinder.
- 9. The engine according to any preceding Clause, further comprising an oil unit attached
to a front side of the crankcase, wherein a front portion of the crankcase where the
oil unit is attached has a concave shape.
- 10. The engine according to Clause 9, further comprising a cylinder section having
three cylinders, wherein the front portion of the crankcase in which an attachment
portion of the oil unit is formed below the middle cylinder among the three cylinders
is concave rearward with respect to portions on both sides thereof corresponding with
the balancer weights.
- 11. The engine according to Clause 9 or 10, wherein the crankcase portion for attaching
the oil unit is concave rearward to the crankshaft side with respect to the balancer
shaft.
- 12. A straddle-type vehicle comprising the engine according to any preceding Clause.