EP0987413B1 - Motorradbrennkraftmaschine in V-Bauart - Google Patents

Motorradbrennkraftmaschine in V-Bauart Download PDF

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Publication number
EP0987413B1
EP0987413B1 EP99116636A EP99116636A EP0987413B1 EP 0987413 B1 EP0987413 B1 EP 0987413B1 EP 99116636 A EP99116636 A EP 99116636A EP 99116636 A EP99116636 A EP 99116636A EP 0987413 B1 EP0987413 B1 EP 0987413B1
Authority
EP
European Patent Office
Prior art keywords
bank
disposed
crank
motorcycle
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99116636A
Other languages
English (en)
French (fr)
Other versions
EP0987413A3 (de
EP0987413A2 (de
Inventor
Takashi Kanbe
Akifumi Nomura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP0987413A2 publication Critical patent/EP0987413A2/de
Publication of EP0987413A3 publication Critical patent/EP0987413A3/de
Application granted granted Critical
Publication of EP0987413B1 publication Critical patent/EP0987413B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
    • F02B61/02—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1808—Number of cylinders two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/20—SOHC [Single overhead camshaft]

Definitions

  • the present invention relates to a motorcycle having a V-type internal combustion engine, and particularly to a motorcycle having an improved V-type internal combustion engine, in which a front bank and a rear bank are disposed fore and aft in an upper portion of a crank case in such a manner as to cross each other in a V-shape centered at a crank shaft disposed laterally in a state that the crank shaft is mounted on a body frame; a mission case portion for containing a transmission is integrally provided on a rear portion of the crank case for containing the crank shaft; and a front exhaust pipe is connected to a front portion of the front bank and a rear exhaust pipe is connected to a rear portion of the rear bank.
  • V-type internal combustion engine for a motorcycle of this type has been disclosed, for example, in Japanese Patent Laid-open No. Sho 58-96130 and US-A-4,497,293.
  • the prior art V-type internal combustion engine for a motorcycle has a problem. Since a lubricating oil pump and a cooling water pump are disposed vertically in a rear portion of a crank case, the rear portion of the crank case must be made deep on the rear side.
  • an object of the present invention is to provide a V-type internal combustion engine for a motorcycle, which is intended to realize a reasonable arrangement of a lubricating oil pump and a cooling water pump for making the rear portion of a crank case compact while suppressing enlargement of the entire engine, and sufficiently ensuring a gap between the rear portion of the crank case and a rear exhaust pipe thereby reducing the adverse effect of radiation heat produced by the exhaust pipe exerted on the crank case.
  • a motorcycle having an improved V-type internal combustion engine, in which a front bank and a rear bank are disposed fore and aft in an upper portion of a crank case in such a manner as to cross each other in a V-shape centered at a crank shaft disposed laterally in a state that the crank shaft is mounted on a body frame; a mission case portion for containing a transmission is integrally provided on a rear portion of the crank case for containing said crank shaft; and a front exhaust pipe is connected to a front portion of the front bank and a rear exhaust pipe is connected to a rear portion of the rear bank, characterized in that a lubricating oil pump for supplying oil to portions to be lubricated of the front and rear banks and a cooling water pump for supplying cooling water to water jackets of the front and rear banks are provided in the crank case in such a manner as to be laterally disposed in front of and over the crank shaft.
  • the rear portion of the crank case can be made compact without any interference with both the pumps. Accordingly, it is possible to sufficiently ensure a gap between the rear portion of the crank case and the rear exhaust pipe and hence to reduce the adverse effect of radiation heat produced by the exhaust pipe exerted on the crank case.
  • crank case Although the front portion of the crank case is slightly swelled by the effect of the above arrangement of both the pumps, the swelled portion of the crank case is contained in a lower dead space of the front bank, and thereby it never promotes enlargement of the entire size of the internal combustion engine.
  • the rear bank is offset on one side in the lateral direction from the front bank by an amount corresponding to a slit between center lines of adjacently disposed connecting rods of the both banks; an exhaust muffler is disposed on the side, opposed to the offset direction of the rear bank from the front bank, in such a manner as to extend on one side of a rear wheel; and an exhaust port of the rear bank is opened in a side surface, on the exhaust muffler side, of the rear portion of the rear bank, and the rear exhaust pipe connected to the exhaust muffler is connected to the exhaust port.
  • the second feature it is possible to reduce the degree of bending of the rear exhaust pipe, and hence to reduce the flow resistance of the exhaust pipe resulting in the enhanced output performance of the engine.
  • front and rear timing transmission units disposed adjacent to each other for driving valve system cam shafts of the front and rear banks respectively are connected to one end portion, on the side opposed to the exhaust muffler side, of the crank shaft.
  • the rear exhaust pipe can be made compact without any interference with the front and rear timing transmission units.
  • a side wall, on the rear timing transmission unit side, of the mission case portion is offset to the exhaust muffler side from the rear timing transmission unit.
  • a lifter for a chain tensioner can be mounted to a rear wall of the rear bank without interference with the mission case portion even in a state that the rearward tilt angle of the rear bank is not set at a particularly small value.
  • an input shaft and an output shaft of the transmission are disposed fore and aft at the back of the crank shaft, and an upper wall of the mission case portion for containing the input shaft and the output shaft is flattened.
  • the fifth feature it is possible to sufficiently ensure a gap between the mission case portion and the rear exhaust pipe, and hence to reduce the adverse effect of radiation heat produced by the exhaust pipe exerted on the mission case portion.
  • the lubricating oil pump for supplying oil to the front and rear banks and the cooling water pump for supplying cooling water to the front and rear banks are provided in the crank case in such a manner as to be laterally disposed in front of and over the crank shaft, the rear portion of the crank case can be made compact without any interference with both the pumps. This makes it possible to sufficiently ensure a gap between the rear portion of the crank case and the rear exhaust pipe and hence to reduce the adverse effect of radiation heat produced by the exhaust pipe exerted on the crank case.
  • crank case Although the front portion of the crank case is slightly swelled because of the above arrangement of both the pumps, the swelled portion of the crank case is contained in a lower dead space of the front bank, and thereby it never promotes enlargement of the entire size of the internal combustion engine.
  • the rear bank is offset on one side in the lateral direction from the front bank by an amount corresponding to a slit between center lines of adjacently disposed connecting rods of the both banks; an exhaust muffler is disposed on the side, opposed to the offset direction of the rear bank from the front bank, in such a manner as to extend on one side of a rear wheel; and an exhaust port of the rear bank is opened in a side surface, on the exhaust muffler side, of the rear portion of the rear bank, and the rear exhaust pipe connected to the exhaust muffler is connected to the exhaust port. Accordingly, it is possible to reduce the degree of bending of the rear exhaust pipe, and hence to reduce the flow resistance of the exhaust pipe resulting in the enhanced output performance of the engine.
  • front and rear timing transmission units disposed adjacent to each other for driving valve system cam shafts of the front and rear banks respectively are connected to one end portion, on the side opposed to the exhaust muffler side, of the crank shaft. Accordingly, the rear exhaust pipe can be made compact without any interference with the front and rear timing transmission units.
  • a side wall, on the rear timing transmission unit side, of the mission case portion is offset to the exhaust muffler side from the rear timing transmission unit. Accordingly, since there is a slight lateral offset between the main body of the crank case and the mission case portion, a lifter for a chain tensioner can be mounted to a rear wall of the rear bank without interference with the mission case portion even in a state that the rearward tilt angle of the rear bank is not set at a particularly small value.
  • an input shaft and an output shaft of the transmission are disposed fore and aft at the back of the crank shaft, and an upper wall of the mission case portion for containing the input shaft and the output shaft is flattened. Accordingly, it is possible to sufficiently ensure a gap between the mission case portion and the rear exhaust pipe, and hence to reduce the adverse effect of radiation heat produced by the exhaust pipe exerted on the mission case portion.
  • the front, rear, right, and left sides are based on a body of the motorcycle.
  • a front fork (not shown in Figs. 1 and 2) for supporting a front wheel is steerably connected to the front end of a body frame 1 of a motorcycle M.
  • a rear fork 3 for supporting a rear wheel 2 is vertically swingably connected to a rear portion of the body frame 1, and a rear cushion 7 is interposed between the rear ends of the rear fork 3 and the body frame 1.
  • a V-type internal combustion engine E having a front bank 4 1 and a rear band 4 2 is mounted on an intermediate portion of the body frame 1, and a fuel tank 5 is mounted on the intermediate portion of the body frame 1 at a position over the engine E.
  • a main seat 6a and a pillion seat 6b are mounted on the rear portion of the body frame 1 in such a manner as to be continuous to the rear end of the fuel tank 5.
  • a chain transmission unit 10 for connecting an output shaft 97 of a transmission 8 connected to the internal combustion engine E and a hub of the rear wheel 2 is disposed on the left side of the rear wheel 2.
  • a starting motor 11 is disposed in front of and under the crank shaft 15.
  • a front carburetor 12 1 connected to the front bank 4 1 and a rear carburetor 12 2 connected to the rear bank 4 2 are disposed in a valley portion 28 between the front bank 4 1 and the rear band 4 2 of the internal combustion engine E.
  • a front exhaust pipe 13 1 connected to a front surface portion of the front bank 4, and a rear exhaust pipe 13 2 connected to a rear portion of the rear bank 4 2 are collectively connected to the front end of a common exhaust muffler 14.
  • the exhaust muffler 14 is disposed opposite to the chain transmission unit 10 with respect to the rear wheel 2, that is, on the right side of the rear wheel 2.
  • the front bank 4 1 and the rear bank 4 2 of the internal combustion engine E are disposed fore and aft in such a manner as to cross each other at 90° centered at a crank shaft 15 extending from right to left.
  • the crank shaft 15 has a single crank portion 16 having a crank pin 16a, and a pair of right and left journals 18 and 17 adjacent to both the ends of the crank shaft 15.
  • the journals 18 and 17 are supported by a crank case 21 via ball bearings 20 and 19, respectively.
  • the front bank 4 1 and the rear bank 4 2 include cylinder blocks 22 1 and 22 2 connected to the front and rear sloping surfaces of a cone-shaped upper portion of the crank case 21 supporting the crank shaft 15, and cylinder heads 23 1 and 23 2 connected to upper ends of the cylinder blocks 22 1 and 22 2 , respectively.
  • Water jackets 24 1 and 24 2 which are continuous to each other, are formed in the cylinder blocks 22 1 and 22 2 and cylinder heads 23 1 and 23 2 , respectively.
  • Pistons 26 1 and 26 2 inserted in cylinder bores 25 1 and 25 2 of the cylinder blocks 22 1 and 22 2 are connected to the crank pin 16a via connecting rods 27 1 and 27 2 , respectively.
  • the connecting rod 27 2 of the rear bank 4 2 is connected to the crank pin 16a in such a manner as to be offset leftwardly from the connecting rod 27 1 of the front bank 4 1 .
  • the axial line of the rear bank 4 2 is offset leftwardly from that of the front bank 4 1 in accordance with a lateral offset S, as shown in Fig. 8, between the connecting rods 27 1 and 27 2 .
  • an over-running clutch 53 of a starting transmission unit 94, and a drive gear 54a of a first transmission unit 54 connected to a clutch 100 are mounted to a right end portion, projecting outwardly from the right journal 18, of the crank shaft 15 in such a manner as to be adjacently positioned in this order from the inside of the right end portion of the crank shaft 15.
  • an outer member of the over-running clutch 53 is spline-connected to the crank shaft 15, and a starting gear 52 is fixed to an inner member of the over-running clutch 53.
  • the drive gear 54a is key-connected to the crank shaft 15.
  • a drive timing sprocket 42 1 of a front timing transmission unit 46 1 for driving a valve system cam shaft 41 1 of the front bank 4 1 , a drive timing sprocket 42 2 of a rear timing transmission unit 46 2 for driving a valve system cam shaft 41 2 of the rear bank 4 2 , and a rotor 31 of a generator 30 are mounted on a left end portion, projecting outwardly from the left journal 17, of the crank shaft 15 in such a manner as to be adjacently positioned in this order from the inside of the left end portion of the crank shaft 15.
  • the rotor 31 is key-connected to the crank shaft 15.
  • the mounting structure of the two drive timing sprockets 42 1 and 42 2 will be described later.
  • a projection 35 is formed at a portion on the outer peripheral surface of the rotor 31.
  • a crank position sensor 36 for detecting a rotational position of the crank shaft 15 in cooperation with the projection 35 is fixed to the left end surface of the crank case 21.
  • An output signal sent from the crank position sensor 36 is used as a control signal for an ignitor or an input signal for a tachometer.
  • the starting gear 52 is supported thereon via the over-running clutch 53 in such a manner as to be adjacent to the right journal 18, and the first drive gear 54a is key-connected thereto in such a manner as to be adjacent to the starting gear 52.
  • the front and rear timing transmission units 46 1 and 46 2 can be collectively assembled on the same side, that is, on the left end portion side of the crank shaft 15, to thereby improve the assembling performance thereof, and also the maintenance of both the timing transmission units 46 1 and 46 2 can be easily performed without any interference with other parts only by removing the generator 30 positioned outside both the timing transmission units 46 1 and 46 2 from the crank shaft 15. Further, since the generator 30 is disposed adjacent to both the timing transmission units 46 1 and 46 2 , oil scattered from both the timing transmission units 46 1 and 46 2 are splashed to the generator 30 during operation of the engine, it is possible to effectively cool the generator 30.
  • the front and rear timing transmission units 46 1 and 46 2 and the generator 30 are disposed on the left side portion of the crank case 21 while a starting transmission unit 94, the first transmission unit 54, and the clutch 100 are disposed on the other side of the crank case 21, so that good balance in weight is maintained between both sides of the crank case 21 and accordingly, when the internal combustion engine is mounted on the body frame 1, it is possible to easily offer good balance in weight between the right and left sides of the motorcycle M.
  • Valve System see Figs. 2, 3, 4, 8, and 9
  • Intake valves 37 1 and 37 2 and exhaust valves 38 1 and 38 2 are respectively provided in the cylinder heads 23 1 and 23 2 of the front and rear banks 4 1 and 4 2 in such a manner that the intake valves 37 1 and 37 2 are offset to the valley 28 side between the front and rear banks 4 1 and 4 2 .
  • Both ends of cam shafts 41 1 and 41 2 extending in parallel to the crank shaft 15 are supported by the cylinder heads 23 1 and 23 2 via ball bearings 50 and 50', respectively.
  • the cam shaft 41 1 is adapted to open/close the intake valve 37 1 and the exhaust valve 38 1 via rocker arms 39 1 and 40 1 , respectively, and the cam shaft 41 2 is adapted to open/close the intake valve 37 2 and the exhaust valve 38 2 via rocker arms 39 2 and 40 2 , respectively.
  • Timing chains 44 1 and 44 2 are wound around the drive timing sprockets 42 1 and 42 2 fixed to the left end portion of the crank shaft 15 and driven timing sprockets 43 1 and 43 2 fixed to the left ends of the cam shafts 41 1 and 41 2 of the front and rear banks 4 1 and 4 2 , respectively.
  • Both the drive timing sprockets 42 1 and 42 2 has a common boss 45 press-fitted around a portion, adjacent to the outer end of the left journal 17, of the crank shaft 15.
  • the drive timing sprockets 42 1 , the timing chain 44 1 and the driven timing sprocket 43 1 of the front bank 4 1 constitute the front timing transmission unit 46 1 for reducing the rotational speed of the crank shaft 15 to half and transmitting the reduced rotational speed to the corresponding cam shaft 41 1 .
  • the front timing transmission unit 46 1 is disposed in a front timing transmission chamber 47 1 formed in a side wall, on the generator 30 side, of the front bank 4 1 .
  • the drive timing sprockets 42 2 , the timing chain 44 2 and the driven timing sprocket 43 2 of the rear bank 4 2 constitute the rear timing transmission unit 46 2 for reducing the rotational speed of the crank shaft 15 to half and transmitting the reduced rotational speed to the corresponding cam shaft 41 2 .
  • the rear timing transmission unit 46 2 is disposed in a rear timing transmission chamber 47 2 formed in a side wall, on the generator 30 side, of the rear bank 4 2 .
  • the rear timing transmission unit 46 2 is disposed outside the front timing transmission unit 46 1 in the axial direction, that is, it is located closer to the generator 30 than the front timing transmission unit 46 1 is.
  • the crank shaft 15 is rotated counterclockwise as shown by an arrow R in Fig. 4, and accordingly, the rear sides of the timing chains 44 1 and 44 2 are loosened.
  • arched chain tensioners 48 1 and 48 2 swingably supported by the crank case 21 are brought into slide-contact with the loosened rear sides of the timing chains 44 1 and 44 2 .
  • known tensioner lifters 49 1 and 49 2 for pressing central portions of the chain tensioners 48 1 and 48 2 in the longitudinal direction toward the timing chains 44 1 and 44 2 at specific loads are mounted on mounting planes formed on rear surfaces of the cylinder blocks 22 1 and 22 2 of the front and rear banks 4 1 and 4 2 with bolts 109, respectively.
  • the crank case 21 is divided at the central portion in the lateral direction into a right case half 21b and a left case half 21a.
  • Outer races of the ball bearings 20 and 19 are previously lightly press-fitted in the right and left case halves 21b and 21a, respectively, and upon assembly of both the case.halves 21b and 21a, the right and left journals 18 and 17 of the crank shaft 15 are lightly press-fitted in inner races of the ball bearings 20 and 19, respectively.
  • an outside diameter d 1 of each of the drive timing sprockets 42 1 and 42 2 is set to be slightly smaller than an inside diameter d 2 of the inner race of the ball bearing 19.
  • the ball bearings 20 and 19 are lightly press-fitted in the right and left case halves 21b and 21a and the right and left crank journals 18 and 17, it is possible to suppress occurrence of vibration of the ball bearings 20 and 19 and hence reduce occurrence of noise during operation of the engine.
  • the exit of an exhaust port 51 1 of the front bank 4 1 is opened to the front of the cylinder head 23 1 of the front bank 4 1 , and the upstream end of the front exhaust pipe 13 1 is connected to the exit of the exhaust port 51 1 .
  • the exit of an exhaust port 51 2 of the rear bank 4 2 is opened to a right side surface, opposed to the rear timing transmission unit 46 2 , of the rear portion of the cylinder head 23 2 of the rear bank 4 2 , and the upstream end of the rear exhaust pipe 13 2 is connected to the exit of the exhaust port 51 2 .
  • the front and rear exhaust pipe 13 1 and 13 2 arranged on the upper and lower sides extend on the right side, opposed to the front and rear chain transmission units 46 1 and 46 2 , of the internal combustion engine E, and the downstream ends of the front and rear exhaust pipe 13 1 and 13 2 are collected and connected to the exhaust muffler 14 disposed on the right side of the rear wheel 2.
  • the rear exhaust pipe 13 2 disposed on the right side of the motorcycle M is connected to the exhaust port 51 2 opened to the right side surface of the rear portion of the cylinder head 23 2 of the rear bank 4 2 , the degree of bending of the rear exhaust pipe 13 2 is reduced, so that it may make small the flow resistance of the pipe and hence to improve the output performance.
  • a mission case portion 95 protruded from a lower portion of the rear bank 4 2 is formed integrally with the crank case 21.
  • An input shaft 96 and an output shaft 97 of the transmission 8, which are provided directly behind the crank shaft 15 in such a manner as to be located on the front and rear sides in parallel to the crank shaft 15, are contained in the mission case portion 95.
  • Both ends of the input shaft 96 are supported by right and left walls of themission case portion 95 via a pair of ball bearings 98' and 98, and both ends of the output shaft 97 are supported by the right and left walls of the mission case portion 95 via a pair of ball bearings 99' and 99.
  • An inner member 101 of the clutch 100 covered with the right cover 34 connected to the right side surface of the crank case 21 is spline-connected to the right end portion of the input portion 96.
  • a first driven gear 54b which is meshed with the first drive gear 54a to constitute the first transmission unit 54, is mounted to the inner end of the outer member 102.
  • a plurality (five in the example shown in the figures) of speed change gear trains G 1 to G 5 are selectively arranged between the input shaft 96 and the output shaft 97.
  • a left wall 95a, which supports the left end portions of the input shaft 96 and the output shaft 97, of the mission case portion 95 is offset rightwardly from the timing transmission unit 46 2 of the rear bank 4 2 . Accordingly, when the tensioner lifter 49 2 of the timing transmission unit 46 2 of the rear bank 4 2 is mounted on the rear surface of the cylinder block 22 2 of the rear bank 4 2 , it is possible to prevent the tensioner lifter 49 2 from interfering with the mission case portion 95.
  • timing transmission unit 46 2 of the rear bank 4 2 is disposed outwardly, that is, leftwardly from the timing transmission unit 46 1 of the front bank 4 1 , it is possible to minimize the rightward offset of the mission case portion 95 from the crank case 21, and hence to realize the compactness of the internal combustion engine E.
  • the rear wall of the mission case portion 95 has a mounting hole 103, and a vehicular speed sensor 105 having a detecting portion 105a inserted in the mission case portion 95 through the mounting hole 103 is fixed on the rear wall of the mission case portion 95 with a bolt 110.
  • the vehicular speed sensor 105 is disposed with the detecting portion 105a facing to the tips of a top driven gear, that is, a driven gear 104 of the top gear train G 5 .
  • the top driven gear 104 which is spline-connected to the output shaft 97, serves as a shift gear for working the second-speed gear train G 2 by leftward shift thereof.
  • the vehicular speed sensor 105 creates a signal corresponding to the number of teeth of the top driven gear 104 just crossing the detecting portion of the vehicular speed sensor 105 and outputs the signal to a computer (not shown).
  • the computer calculates a vehicular speed on the basis of the signal thus inputted from the vehicular speed sensor 105 and displays the vehicular speed on a speed meter (not shown) on an instrument panel (not shown) of the motorcycle M.
  • the vehicular speed sensor 105 for detecting the rotational speed of the top driven gear 104 usually rotated together with the output shaft 97 can be mounted on the rear wall of the mission case portion 95 without any interference with not only the rear bank 4 2 tilted rearwardly toward the mission case portion 95 side but also the rear exhaust pipe 13 2 mounted on the rear portion of the rear bank 4 2 .
  • a rib 106 for covering the lower surface of the vehicular speed sensor 105 is integrally formed on the rear surface of the mission case portion 95.
  • the central portion of the rib 106 has a through-hole 107 allowing a lead wire 108 of the vehicular speed sensor 105 to pass therethrough.
  • a pair of right and left hangers 112 1 and a pair of right and left hangers 112 2 are integrally formed on the upper and lower sides of the rear surface of the mission case portion 95 in such a manner as to project therefrom, and a pair of right and left hangers 112 3 are integrally formed on the front surface of the crank case 21 in such a manner as to project therefrom.
  • these hangers 112 1 , 112 2 , and 112 3 are connected to the body frame 1.
  • the vehicular speed sensor 105 is disposed in a rear dead space of the interior of the mission case portion 95 surrounded by the rear side two pairs of the hangers 112 1 and 112 2 . With this configuration, it is possible to enhance the space efficiency.
  • the above rib 106 functions to protect the vehicular speed sensor 105 from being affected by small stones and sands flying from a road during running of the motorcycle M.
  • the through-hole 107 for allowing the lead wire 108 to pass therethrough functions as a port for discharging rainwater and cleaning water permeated in the rib 106.
  • the first drive gear 54a key-connected to the right end portion of the crank shaft 15 is meshed at its two different portions in the peripheral direction with a pump drive gear 56 and the first driven gear 54b.
  • the pump drive gear 56 is key-connected to a pump shaft 61 which is supported via a bearing 86 by the right cover 34 connected to the right end surface of the crank case 21.
  • the pump shaft 61 which is in parallel to the crank shaft 15, is disposed in front of and over the crank shaft 15.
  • An inner rotor 58 of a trochoid type oil pump 57 for lubrication is fixed on the inner end of the pump shaft 61, and an impeller 63 of a water pump 62 for cooling is fixed on the outer end of the pump shaft 61.
  • a pump housing 60 for containing an outer rotor 59 of the oil pump 57 is screwed in a partition wall 65 for supporting the ball bearing 20 of the crank case 21.
  • a pump casing 64 for containing the impeller 63 is fixed on the outer surface of the right cover with a bolt 87.
  • the oil pump 57 and the water pump 62 are coaxially disposed in front of and over the crank shaft 15.
  • the oil pump 57 is provided on the crank case 21 in such a manner as to be adjacent to the outer side of the over-running clutch 53 in the radial direction.
  • a suction port of the oil pump 57 is connected via a suction pipe 68 to a strainer 67 (see Fig. 2) disposed in an oil sump 66 on the inner bottom of the crank case 21, and a discharge port of the oil pump 57 is communicated via an oil passage 69 to the crank shaft 15, the cam shafts 41 1 and 41 2 of the front and rear banks 4 1 and 4 2 , and other portions to be lubricated.
  • An oil filter 70 positioned substantially directly over the crank shaft 15 is interposed in the course of the oil passage 69.
  • the oil filter 70 is mounted to a filter chamber 71 formed in the right cover 34, and a cap 72 for closing an opening of the chamber 71 is fixed to the right cover 34.
  • An inlet chamber 71a on the outer peripheral side of the oil filter 70 in the filter chamber 71 is communicated to the discharge port of the oil pump 57 via an upstream portion 69a of the oil passage 69 formed in the crank case 21, and an outlet chamber 71b on the inner peripheral side of the oil filter 70 in the filter chamber 71 is communicated to two branch oil passages 69b and 69c, formed in the cap 72, of the oil passage 69.
  • One branch oil passage 69b is communicated to a portion 73 to be lubricated of the crank shaft 15 system.
  • the other branch oil passage 69c is further branched at a connection surface between the crank case 21 and the right cover 34 into front and rear branch oil passages 69d and 69e which are in turn communicated to portions 74 1 and 74 2 to be lubricated of the valve systems including the cam shafts 41 1 and 41 2 of the front and rear banks 4 1 and 4 2 .
  • the oil filter 70 is provided with a relief valve 70b for short-circuiting the inlet chamber 71a to the outlet chamber 71b when a filter element 70a of the oil filter 70 becomes blocked.
  • a suction pipe 75 is connected to an outlet of the radiator 29 (disposed in front of the internal combustion engine E as shown in Fig. 1) via a water pipe 77 1 , and a discharge pipe 76 is connected to a lower portion of the water jacket 24 1 of the front bank 4 1 via a water pipe 77 2 .
  • the front and rear banks 41 and 4 2 include the cylinder blocks 22 1 and 22 2 , the cylinder heads 23 1 and 23 2 , and the water jacket 24 1 and 24 2 continuous to each other, respectively, and a combined chamber 80 opened to the front surface of the cylinder head 23 2 of the rear bank 4 2 is formed in the cylinder head 23 2 and an upper portion of the water jacket 24 2 is communicated to the combined chamber 80.
  • Lower joints 78 1 and 78 2 communicated to lower portions of the corresponding water jackets 24 1 and 24 2 are integrally formed on the opposed surfaces of the front and rear banks 41 and 4 2 in such a manner as to project therefrom. Both ends of a lower communication water pipe 77 3 disposed in the valley portion 28 are connected to these joints 78 1 and 78 2 .
  • An upper joint 79 1 communicated to an upper portion of the jacket 23 1 is integrally formed on the rear surface of the front bank 4 1 , and a flange of an upper joint 79 2 communicated to the combined chamber 80 is screwed in a lower surface portion of the cylinder head 23 2 of the rear bank 4 2 . Both ends of a rear communication water pipe 77 4 disposed in the valley portion 28 are connected to these upper joints 79 1 and 79 2 .
  • a thermostat 82 is disposed in the combined chamber 80, and a thermostat cover 81 for holding the thermostat 82 and covering the opening of the combined chamber 80 is connected to the front surface of the cylinder head 23 2 .
  • An outlet joint 83 connected to the outlet of the thermostat 82 is integrally formed on the thermostat cover 81.
  • the outlet joint 83 is connected to the inlet of the radiator 29 via a water pipe 77 5 .
  • a bypass outlet joint 84 communicated to the combined chamber 80 via a communication passage 84' is integrally formed on the upper joint 79 2 .
  • the bypass outlet joint 84 is communicated to a heating chamber of the carburetor 12 2 of the rear bank 4 2 , a heating chamber of the carburetor 12 1 of the front bank 4 1 , and the suction pipe 75 in sequence by way of a bypass water pipe 85.
  • the bypass outlet joint 84 has an inside diameter sufficiently smaller than that of the outlet joint 83 of the thermostat cover 81.
  • the thermostat 82 blocks the combined chamber 80 from the thermostat cover 81 and opens the communication passage 84' between the combined chamber 80 and the bypass outlet joint 84.
  • the thermostat 82 communicates the combined chamber 80 to the thermostat cover 81 and closes the communication passage 84'.
  • the thermostat 82 blocks the combined chamber 80 from the thermostat cover 81 and opens the communication passage 84'. Consequently, cooling water is fed first from the discharge pipe 76 to the water jacket 24 1 of the front bank 4 1 by the water pump 62.
  • about a half of the cooling water is immediately fed to the water jacket 24 2 of the rear bank 4 2 by way of the lower communication water pipe 77 3 , and the remaining cooling water passes through the water jacket 24 1 of the front bank 4 1 and is then fed to the combined chamber 80 of the rear bank 4 2 by way of the upper communication water pipe 77 4 .
  • the cooling water is combined with the above cooling water having passed through the water jacket 24 2 of the rear bank 4 2 .
  • the cooling water thus combined is fed from the combined chamber 80 to the bypass outlet joint 84 by way of the communication passage 84', being further fed from the bypass outlet joint 84 to the heating chambers of the carburetors 12 2 and 12 1 of the rear and front banks 4 2 and 41 in sequence, and is returned to the suction pipe 75 of the water pump 62. Thereafter, the same circulation is repeated.
  • Such circulation of cooling water not by way of the radiator 29 makes it possible to promote the warming of the internal combustion engine E, and to heat the carburetors 12 1 and 12 2 thereby preventing icing of a fuel nozzle and its neighborhood.
  • the temperature of the cooling water whose components having passed through the water jackets 24 1 and 24 2 of the front and rear banks 4 1 and 4 2 and combined in the combined chamber 80 becomes the above specific temperature.
  • the thermostat 82 since the thermostat 82 communicates the combined chamber 80 to the thermostat cover 81 and closes the communication passage 84', the above cooling water flows on the outlet joint 83 side, and is returned to the suction pipe 75 of the water pump 62 by way of the radiator 29. Thereafter, the same circulation is repeated. Accordingly, the front and rear banks 4 1 and 4 2 can be effectively cooled with the cooling water cooled by the radiation action of the radiator 29.
  • the lower and upper communication water pipes 77 3 and 77 4 are sufficient to be relatively short in length and are disposed in the valley portion 28 between both the banks 4 1 and 4 2 , they are hidden by both the banks 4 1 and 4 2 .
  • the water pipes 77 3 and 77 4 therefore, are inconspicuous as seen from the outside, that is, do not degrade the appearance of the internal combustion engine E.
  • the thermostat 82 Since the thermostat 82 is disposed in the combined chamber 80 in which components of cooling water having cooled the front and rear banks 4 1 and 4 2 are combined, it can suitably control the water temperature in both the banks 4 1 and 4 2 by certainly detecting an average water temperature in both the banks 4 1 and 4 2 . Further, it is not required to make a layout of piping for the thermostat 82, thereby simplifying the entire piping layout.
  • thermostat cover 81 including the outlet joint 83 projecting forwardly is connected to the front surface of the upper portion of the rear bank 4 2 , it is possible to reduce the degree of bending of the water pipe 77 5 for communicating the outlet joint 83 to the inlet of the radiator 29, and hence to make small the flow resistance of the water pipe 77 5 and also improve the entire appearance of the internal combustion engine E.
  • bypass outlet joint 84 having the inside diameter smaller than that of the upper joint 79 2 of the rear bank 4 2 and being communicated to the combined chamber 80 is integrally formed on the upper joint 79 2 , it is possible to collectively mount the upper joint 79 2 and the bypass outlet joint 84 to the rear bank 4 2 , and hence to simplify the piping works.
  • the oil pump 57 is disposed adjacent to the over-running clutch 53 in the radial direction, it is possible to suppress the increase in lateral width of the internal combustion engine E, although the oil pump 57 and the water pump 62 are coaxially disposed.
  • crank case 21 Since the oil pump 57 and the water pump 62 are disposed in front of and over the crank shaft 15, it is possible to compactly form the rear portion of the crank case 21 and the mission case portion 95 continuous thereto without any interference with the oil pump 57 and the water pump 62, and hence to ensure a desirable ground clearance of the internal combustion engine E and easily reduce the heights of the driver's seat 6a and the pillion seat 6b.
  • the front portion of the crank case 21 is slightly swelled by the effect of the above arrangement of the oil pump 57 and the water pump 62, the swelled portion of the crank case 21 is contained in the lower dead space of the front bank 4 1 , and therefore, it does not obstruct the compactness of the internal combustion engine E.
  • the input shaft 96 and the output shaft 97 of the transmission 8 are horizontally disposed directly after the crank shaft 15 without any interference with the oil pump 57 and the water pump 62, it is possible to achieve the compactness of the mission case portion 95 and also flatten the upper wall of the mission case portion 95. This makes it possible to sufficiently ensure the distance between the mission case portion 95 and the rear exhaust pipe 13 2 and hence to easily prevent the mission case portion 95 and the transmission 8 contained therein from being thermally affected by the rear exhaust pipe 13 2 .
  • a containing recessed portion 88 is formed in the bottom surface of the front portion of the crank case 21, and the starting motor 11 is disposed in the containing recessed portion 88 with its axial line directed in parallel to the crank shaft 15.
  • a casing 89 of the starting motor 11 is mounted on the crank case 21 in such a manner that a cylindrical supporting portion 89a at one end of the casing 89 is liquid-tightly fitted in a through-hole 90 formed in the end wall of the containing recessed portion 88 and a mounting arm portion 89b at the other end of the casing 89 is fastened to the crank case 21 with a bolt 111.
  • the leading end of a rotor shaft 91 of the starting motor 11 is inserted in the crank case 21, and a pinion 92 formed on the leading end of the rotor shaft 91 is adapted to drive the starting gear 52 via a reduction gear train 93.
  • the starting gear 52, the over-running clutch 53, and the reduction gear train 93 constitute a starting transmission unit 94 for transmitting the rotational power of the starting motor 11 to the crank shaft 15.
  • the starting motor 11 since the starting motor 11 is disposed in front of and under the crank shaft 15, the starting motor 11 also does not obstruct the compactness of the rear portion of the crank case 21 and the mission case portion 95, and since the starting motor 11 is contained in the lower dead space of the front bank 4 1 , it does not obstruct the compactness of the internal combustion engine E. Further, the reduction gear train 93 is dipped in oil accumulated in the oil sump 66 on the bottom of the crank case 21 by the effect of the above arrangement of the starting motor 11; however, since the reduction gear train 93 is activated not during operation of the engine but upon start-up of the engine, it does not agitate the oil during operation of the engine and thereby does not cause the power loss.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)

Claims (6)

  1. Kraftrad mit einem V-Verbrennungsmotor, in welchem eine vordere Bank (41) und eine hintere Bank (42) vorne und hinten in einem oberen Abschnitt eines Kurbelgehäuses (21) in einer solchen Weise angeordnet sind, dass sie einander in einer V-Form zentriert an einer Kurbelwelle (15) kreuzen, welche seitlich angeordnet ist, in einem Zustand, in welchem die Kurbelwelle (15) an einem Rumpfrahmen (1) angebracht ist; ein Getriebegehäuseabschnitt (95) zur Aufnahme eines Getriebes (8) integral an einem hinteren Abschnitt des Kurbelgehäuses (21) zur Aufnahme der Kurbelwelle (15) vorgesehen ist; und ein vorderes Auspuffrohr (13,) mit einem vorderen Abschnitt der vorderen Bank (41) verbunden ist, und ein hinteres Auspuffrohr (132) mit einem hinteren Abschnitt der hinteren Bank (42) verbunden ist, dadurch gekennzeichnet, dass eine Schmierölpumpe (57) zur Zufuhr von Öl zu Abschnitten der vorderen und der hinteren Bank (41, 42), welche zu schmieren sind, und eine Kühlwasserpumpe (62) zur Zufuhr von Kühlwasser zu Wassermänteln (241, 242) der vorderen und der hinteren Bank (41, 42) in dem Kurbelgehäuse (21 ) in einer solchen Weise vorgesehen sind, dass sie vor und über der Kurbelwelle (15) seitlich angeordnet sind.
  2. Kraftrad mit einem V-Verbrennungsmotor gemäß Anspruch 1, wobei die hintere Bank (42) in der Querrichtung von der vorderen Bank (41) um einen Betrag zu einer Seite versetzt ist, der einem Spalt (S) zwischen Mittellinien benachbart angeordneter Pleuelstangen (271, 272) der beiden Bänke (41, 42) entspricht; ein Auspufftopf (14) an der zur Versatzrichtung der hinteren Bank (42) von der vorderen Bank (41) entgegengesetzten Seite in einer solchen Weise angeordnet ist, dass er sich auf eine Seite eines Hinterrads (2) erstreckt; und eine Auslassöffnung (512) der hinteren Bank (42) sich in einer Seitenfläche auf der Seite des Auspufftopfs (14) des hinteren Abschnitts der hinteren Bank (42) öffnet und das mit dem Auspufftopf (14) verbundene hintere Auspuffrohr (132) mit der Auslassöffnung (512) verbunden ist.
  3. Kraftrad mit einem V-Verbrennungsmotor gemäß Anspruch 1 oder 2, wobei einander benachbarte vordere und hintere Steuergetriebeeinheiten (461, 462) zum jeweiligen Antrieb von Ventilsystemnockenwellen (411, 412) der vorderen und der hinteren Bank (41, 42) mit einem Endabschnitt der Kurbelwelle (15) an der zur Seite des Auspufftopfs (14) entgegengesetzten Seite verbunden sind.
  4. Kraftrad mit einem V-Verbrennungsmotor für ein Kraftrad gemäß einem der Ansprüche 1 bis 3, wobei eine Seitenwand (95a) auf der Seite der hinteren Steuergetriebeeinheit (462) des Getriebegehäuseabschnitts (95) zur Seite des Auspufftopfs (14) von der hinteren Steuergetriebeeinheit (462) versetzt ist.
  5. Kraftrad mit einem V-Verbrennungsmotor für ein Kraftrad gemäß einem der Ansprüche 1 bis 4, wobei eine Eingangswelle (96) und eine Ausgangswelle (97) des Getriebes (8) vorne und hinten an der Rückseite der Kurbelwelle (15) angeordnet sind und eine obere Wand des Getriebegehäuseabschnitts (95) zur Aufnahme der Eingangswelle (96) und der Ausgangswelle (97) abgeflacht ist.
  6. Kraftrad mit einem V-Verbrennungsmotor für ein Kraftrad gemäß einem der Ansprüche 1 bis 5, wobei ein die hintere Bank (42) mit dem Auspufftopf (14) verbindendes hinteres Auspuffrohr (132) hinter dem hinteren Abschnitt des Kurbelgehäuses (29) angeordnet ist und ein mit der vorderen Bank (41) verbundenes vorderes Auspuffrohr (131) unter der Kurbelwelle (15) angeordnet ist.
EP99116636A 1998-09-14 1999-08-25 Motorradbrennkraftmaschine in V-Bauart Expired - Lifetime EP0987413B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP26070498 1998-09-14
JP26070498A JP3954732B2 (ja) 1998-09-14 1998-09-14 自動二輪車用ｖ型内燃機関

Publications (3)

Publication Number Publication Date
EP0987413A2 EP0987413A2 (de) 2000-03-22
EP0987413A3 EP0987413A3 (de) 2000-12-13
EP0987413B1 true EP0987413B1 (de) 2003-10-01

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EP99116636A Expired - Lifetime EP0987413B1 (de) 1998-09-14 1999-08-25 Motorradbrennkraftmaschine in V-Bauart

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EP (1) EP0987413B1 (de)
JP (1) JP3954732B2 (de)
KR (1) KR100360810B1 (de)
CN (1) CN1111642C (de)
AR (1) AR015321A1 (de)
BR (1) BR9904103A (de)
CO (1) CO4850638A1 (de)
DE (1) DE69911708T2 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003083161A (ja) * 2001-09-10 2003-03-19 Honda Motor Co Ltd 自動二輪車用ｖ型エンジン
JP3953298B2 (ja) 2001-10-26 2007-08-08 本田技研工業株式会社 車両用動力装置
JP2004092423A (ja) * 2002-08-29 2004-03-25 Yamaha Motor Co Ltd 自動二輪車用エンジン
JP4757060B2 (ja) 2006-02-28 2011-08-24 本田技研工業株式会社 自動二輪車用内燃機関の補機配置構造
ES2348430B1 (es) * 2007-03-28 2011-11-28 Honda Motor Co, Ltd Motor de combustion interna para vehiculo.
JP4846679B2 (ja) * 2007-08-31 2011-12-28 本田技研工業株式会社 車両用ｖ型エンジン
JP5903263B2 (ja) 2011-03-31 2016-04-13 本田技研工業株式会社 水冷式ｖ型エンジン
JP2014125930A (ja) * 2012-12-26 2014-07-07 Honda Motor Co Ltd 水冷式内燃機関のケーシング構造
JP6102265B2 (ja) * 2013-01-09 2017-03-29 スズキ株式会社 車両用エンジンのバランサ装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6145297Y2 (de) * 1981-04-20 1986-12-19
JPS5893910A (ja) * 1981-11-28 1983-06-03 Honda Motor Co Ltd 自動二輪車の内燃機関
JPS5896130A (ja) * 1981-12-03 1983-06-08 Honda Motor Co Ltd 自動二輪車等用火花点火式内燃機関
US4903483A (en) * 1988-02-17 1990-02-27 Yamaha Hatsudoki Kabushiki Kaisha Exhaust system for V-type engine

Also Published As

Publication number Publication date
KR100360810B1 (ko) 2002-11-13
BR9904103A (pt) 2000-09-26
CN1111642C (zh) 2003-06-18
EP0987413A3 (de) 2000-12-13
JP3954732B2 (ja) 2007-08-08
KR20000023139A (ko) 2000-04-25
DE69911708D1 (de) 2003-11-06
JP2000087758A (ja) 2000-03-28
EP0987413A2 (de) 2000-03-22
CN1247937A (zh) 2000-03-22
AR015321A1 (es) 2001-04-18
CO4850638A1 (es) 1999-10-26
DE69911708T2 (de) 2004-08-19

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