WO2003085278A1 - Structure de lubrification de mecanisme d'embrayage du moteur - Google Patents
Structure de lubrification de mecanisme d'embrayage du moteur Download PDFInfo
- Publication number
- WO2003085278A1 WO2003085278A1 PCT/JP2003/004466 JP0304466W WO03085278A1 WO 2003085278 A1 WO2003085278 A1 WO 2003085278A1 JP 0304466 W JP0304466 W JP 0304466W WO 03085278 A1 WO03085278 A1 WO 03085278A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- lubricating oil
- clutch mechanism
- engine
- crankshaft
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/74—Features relating to lubrication
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- 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
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/02—Arrangements of lubricant conduits
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- 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
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/02—Arrangements of lubricant conduits
- F01M2011/027—Arrangements of lubricant conduits for lubricating connecting rod bearings
Definitions
- the present invention relates to a clutch mechanism lubrication structure suitable for, for example, a motorcycle engine having a clutch mechanism on a rotating shaft parallel to a crankshaft.
- a motorcycle engine generally has a clutch mechanism that transmits or disconnects rotation of a crankshaft to an output shaft.
- a clutch mechanism there is an automatic centrifugal clutch mechanism in which a bowl-shaped outer clutch whose one end in the axial direction is opened is fixed to the output side, an input member is arranged in the outer clutch, and the input member is fixed to the input side.
- a bowl-shaped outer clutch whose one end in the axial direction is opened is fixed to the output side
- an input member is arranged in the outer clutch, and the input member is fixed to the input side.
- Patent Documents 1 and 2 do not employ a special structure for ensuring the lubrication of the clutch mechanism, and lubricate the lubricating oil accumulated on the bottom of the crankcase by splashing up the clutch mechanism itself as usual. It is thought that it is. Some lubricating oils are pumped by a lubricating oil pump and supplied to the clutch mechanism. Although this method can provide reliable lubrication, the lubricating oil pump becomes larger and the structure of the lubricating system increases. There is a problem that it becomes complicated.
- the present invention has been made in view of the above-described conventional circumstances, and has as its object to provide an engine clutch mechanism lubricating structure capable of obtaining sufficient lubricating performance with a simple lubricating supply structure. Disclosure of the invention
- the invention according to claim 1 is mounted on a crankshaft in which a large end portion of a rod is connected to a crankpin arranged between a pair of crank arms, and a rotating shaft arranged in parallel with the crankshaft.
- An engine clutch mechanism lubricating structure including a wet clutch mechanism, wherein lubricating oil supplied to a connection portion between the crankpin and the large end of the connector is guided to the clutch mechanism. .
- the invention of claim 2 is that, in claim 1, the clutch mechanism is arranged such that at least a part of the clutch mechanism is located in a lubricating oil scattering area from a connecting portion between the connector and the crankpin. It is characterized by.
- the inner clutch is coaxially arranged in a bowl-shaped clutch having one end opened in the axial direction, and one of the inner clutch and the clutch is arranged on the input side, and Is connected to the output side, and a plurality of inner and outer clutch plates are interposed between the inner and outer clutches.
- the wet multiple plate type is characterized in that the opening of the outer clutch faces the lubricating oil scattering area. It is a sign.
- the clutch mechanism in claim 3 includes both an automatic centrifugal type utilizing the centrifugal force of the weight and a manual type.
- the clutch mechanism further includes an input member that rotates by centrifugal force and abuts on an inner surface of the outer clutch in a bowl-shaped clutch having an axially open one end,
- An automatic centrifugal type in which the input member and the outer clutch are connected to an input side and an output side of the rotary shaft; Are directed to the lubricating oil scattering region.
- the invention according to claim 5 is the invention according to claim 3 or 4, wherein a plurality of slits are formed in the outer peripheral wall of the free clutch so as to penetrate the inside thereof, and the slit is formed in a direction in which the lubricating oil is scattered. It is characterized by being open.
- the clutch mechanism is disposed in a clutch chamber defined by a crank chamber in which the connecting portion and the crank arm are housed.
- the partition is characterized by having an introduction opening for allowing the scattered lubricating oil to enter the clutch chamber.
- the invention of claim 7 is characterized in that, in claim 6, the introduction opening is formed so as to extend over both regions of a plane including both the clutch shaft and the crank shaft.
- the invention of claim 8 is characterized in that, in claim 6, a guide portion is provided which receives the scattered lubricating oil and introduces the lubricating oil more inside than outside the clutch mechanism.
- the guide portion is disposed so as to face the scattered lubricating oil, and receives a lubricating oil; and the luer clutch receives the lubricating oil from the lubricating oil receiving portion.
- the lubricating oil is characterized by comprising a guide portion extending toward the inside and guiding the lubricating oil received by the lubricating oil receiving portion into the inside of the outer clutch.
- FIG. 1 is a left side view of a motorcycle employing an engine clutch mechanism lubrication structure according to one embodiment of the present invention.
- Fig. 2 is a cross-sectional plan view (cross-sectional view taken along the line II-11 in Fig. 6) showing the deployed state of the engine.
- Fig. 3 is a cross-sectional plan view of the continuously variable transmission mechanism and the centrifugal clutch mechanism of the engine. is there.
- FIG. 4 is a right side view of the engine.
- FIG. 5 is a left side view of the engine.
- Fig. 6 is a right side view of the engine with the continuously variable transmission mechanism and centrifugal clutch mechanism removed.
- FIG. 7 is a right side view of the crankcase of the engine.
- Fig. 8 is a cross-sectional rear view of the above-mentioned crankcase (a cross-sectional view taken along the line Vin-VIII in Fig. 5).
- Fig. 9 shows a cross-sectional rear view (cross-sectional view taken along line IX-IX in Fig. 5) of the kick device of the engine.
- FIG. 10 is a sectional view of the kick device.
- FIG. 11 is a cross-sectional rear view showing a lubricating oil path of the engine.
- FIG. 12 is a cross-sectional view of the centrifugal clutch mechanism.
- FIG. 13 is a side view of a free clutch of the centrifugal clutch mechanism.
- FIG. 14 is a front view of the centrifugal clutch mechanism.
- FIG. 15 is an enlarged sectional view of a main part of the centrifugal clutch mechanism.
- FIG. 16 is an enlarged sectional view of a main part of the centrifugal clutch mechanism.
- FIG. 17 is a cross-sectional view of a conventional general driven pulley. BEST MODE FOR CARRYING OUT THE INVENTION
- FIGS. 1 to 16 are diagrams for explaining a motorcycle engine according to an embodiment of the present invention.
- FIG. 1 is a left side view of a motorcycle equipped with the engine of the embodiment, and
- FIG. 2 is an engine.
- Fig. 3 is a sectional plan view of the continuously variable transmission mechanism and the centrifugal clutch mechanism of the engine
- Figs. 4 and 5 are right side views of the engine.
- Left side view Fig. 6 shows the continuously variable transmission mechanism of the engine, centrifugal clutch.
- Fig. 7 is a right side view of the crankcase
- Fig. 8 is a cross-sectional rear view of the crankcase (cross-sectional view taken along the line Vin-Vl II in Fig. 5)
- Fig. 9 is a kick of the engine.
- FIG. 10 is a cross-sectional view around the kick axis
- Fig. 11 is a cross-sectional view showing the lubricating oil path of the engine
- Fig. 12 is the centrifugal clutch mechanism.
- FIG. 13 is a side view of the outer clutch
- FIG. 14 is a front view of the centrifugal clutch mechanism
- FIGS. 15 and 16 are enlarged cross-sectional views of main parts of the centrifugal clutch mechanism. Note that the terms front and rear, left and right in the present embodiment mean front and rear and left and right as viewed from a seat.
- reference numeral 1 denotes a motorcycle on which an engine 2 of the present embodiment is mounted.
- the motorcycle 1 rotates a front fork 5 on which a front wheel 4 is supported by a head pipe 3 fixed to a front end of a body frame 1a.
- It has a schematic structure in which a seat 9 including a seat portion 9a and a rear occupant seat portion 9b is arranged.
- the body frame 1a includes left and right down tubes 1b extending diagonally downward from the head pipe 3, and left and right upper tubes 1c extending diagonally upward following the rear end of each down tube 1b. It is composed of left and right seat rails 1d which are connected to the tube 1b and the upper tube 1c in such a manner as to extend forward and backward.
- the vehicle body frame 1a is surrounded by a resin body cover 10 made of a front cover 10a, a leg shield 10b, a side cover 10c, and the like.
- a steering handle 11 is fixed to an upper end of the front fork 5, and the steering handle 11 is surrounded by a handle cover 1 la.
- the engine 2 includes an engine body 15, a V-belt type continuously variable transmission mechanism 16, a wet multi-plate centrifugal clutch mechanism 17 and a reduction gear mechanism 18.
- a cylinder head 20 is connected to the upper surface of the cylinder block 19, and a head cover 21 is provided above the cylinder head 20. It has a schematic structure in which a crankcase 22 in which a crankshaft 28 is housed is connected to the lower mating surface of the block 19.
- An intake port 10b communicating with the combustion recess 20a is opened on the rear surface of the cylinder head 20.
- the carburetor 23 is connected to the intake port 2Ob via an intake pipe 23a. Is connected.
- An exhaust port 20c communicating with the combustion recess 20a is opened at the front of the cylinder head 20.
- An exhaust pipe 24 is connected to the exhaust port 20c. I have.
- the exhaust pipe 24 extends obliquely downward toward the lower right side of the engine, passes under the transmission case 45 described later, passes through the right outside of the lubrication chamber bulging portion 22 b, and passes through the right side of the vehicle body.
- the rear wheel 7 extends obliquely rearward and is connected to a muffler 25 provided on the right side of the rear wheel 7.
- An ignition plug 30 is inserted into the combustion recess 20a.
- a chain chamber 19a for communicating the inside of the crankcase 22 and the inside of the cylinder head 20, and the chain chamber 19a is provided with the crankshaft.
- a timing chain 34 for rotating the camshaft 31 by the shaft 28 is provided, and the camshaft 31 drives the intake valve 32 and the exhaust valve 33 to open and close.
- a piston 26 is slidably inserted into the cylinder bore of the cylinder block 19.
- the piston 26 is connected to a small end 27 b of a condro 7, and the large end 27 a of the condro is connected between the left and right crank arms 28 a, 28 b of the crankshaft 28. It is connected to the crank pin 29 fitted on the.
- a transmission shaft 47 is disposed behind the crankshaft 28 in parallel with the crankshaft 28, and an output shaft 48 is coaxially disposed on the left side of the transmission shaft 47 in the axial direction. ing.
- a drive sprocket 49 is attached to the left end of the output shaft 48. The drive sprocket 49 is connected to the driven sprocket 51 of the rear wheel 7 via a chain 50. I have.
- a generator 42 is mounted on the left end of the crankshaft 28.
- the generator 42 has a rotor 43 fixed to a sleeve 43 fitted to a crankshaft 28 and a stator 42 b facing the rotor 42 a and a generator case 44. It has a fixed structure.
- the crankcase 12 is divided into a first case 40 on the left side in the crankshaft direction and a first case 41 on the right side.
- a generator case 44 for accommodating the generator 42 is mounted detachably on the outside of the first case 40 in the direction of the crankshaft, and the stepless case is mounted on the outside of the second case 41 in the direction of the crankshaft.
- a transmission case 45 accommodating the transmission mechanism 16 is mounted.
- the dividing line B of the second and fourth cases 40 and 41 is slightly deviated to the left from the cylinder axis A.
- the second case 40, 41 supports the crankshaft 28 inside the first and second outer peripheral walls 40a, 41a which open substantially outward in the crankshaft direction. It has a schematic structure in which the second support walls 40b, 41b are integrally formed.
- the first support wall 40b of the first case 40 is a first crank support wall 40c that supports the left crank journal portion 28c of the crankshaft 28 via the left journal bearing 35. And a speed reduction mechanism support wall portion 40d which is formed in a stepped bulge on the left side in the crankshaft direction with respect to the first crank support wall portion 40c.
- the second support wall 41b of the second case 41 has a second crank support wall 41 supporting the right crank journal 28d of the crankshaft 28 via the right journal bearing 36. And a clutch support wall portion (clutch one-side support wall) 41 d bulging in a stepped manner on the left side in the crankshaft direction with respect to the second crank support wall portion 41c.
- the first and second crank supporting walls 40c and 41c form a 04466
- crank arms 28a and 28b of the crankshaft 28 and the crank pins 29 are accommodated.
- the wet multi-plate centrifugal clutch mechanism 17 is accommodated in a clutch chamber 38 formed by the second outer peripheral wall 41a and the clutch support wall section 41d, and the clutch chamber 38 is The crank chamber 37 is defined.
- the reduction gear mechanism 18 is accommodated in a reduction chamber 39 formed by the reduction mechanism support wall 40 d and the clutch support wall 41 d, and the reduction chamber 39 is provided in the crank chamber 37. Is in communication with
- the reduction gear mechanism 18 has a reduction shaft 52 extending between the support walls 40 d and 41 d in parallel with the transmission shaft 47.
- the right side of the reduction shaft 52 is connected to the clutch support wall.
- the shaft 41 is supported by the part 41d via the reduction bearing 53, and the left end is supported by the recess 40e formed in the reduction mechanism support wall 40d via the reduction bearing 54.
- the primary reduction small gear 74 is mounted on the transmission shaft 47 located in the clutch chamber 38 so as to be relatively rotatable, and the primary reduction large gear 75 is combined with the primary reduction small gear 74 on the reduction shaft 52.
- the secondary reduction small gear 52 is integrally formed on the reduction shaft 52 located in the reduction chamber 39, and the secondary reduction small gear 52 is formed on the output shaft 48.
- the structure is such that the large secondary reduction gear 48a is integrally formed.
- the output shaft 48 is disposed on the same axis as the transmission shaft 47. At the right end of the output shaft 48, a support hole 48b into which the left end of the transmission shaft 47 is inserted is recessed, and a bearing 76 mounted in the support hole 48b is provided. The right end of the output shaft 48 is rotatably supported by the variable speed shaft 47. The left end of the output shaft 48 penetrates the deceleration mechanism support wall 40d of the first case 40, and is supported by the support wall 40d via a bearing 77. . The drive sprocket 49 is fixedly attached to the projecting end of the output shaft 48.
- the V-belt type continuously variable transmission mechanism 16 has a drive pulley 55 mounted on the right outer end of the crankshaft 28 and a driven pulley 5 driven by the right outer end of the shift shaft 47. Dress 6 And the two pulleys 55, 56 are connected by winding a V-belt 57.
- the V-belt 57 is made of heat-resistant and durable resin, and has the following structure in detail.
- a number of resin blocks 57 a formed by mixing carbon fibers or aramide fibers into a polyamide resin and forming a horizontal H shape are arranged side by side, and these are arranged as a pair of annular connection members 57 made of super heat resistant rubber. b is fitted and connected.
- the drive pulley 55 includes a fixed pulley half 55 a fixed to the right end portion of the crankshaft 28, and a fixed pulley half 55 a that can slide axially inward in the crankshaft direction. And a movable pulley half 55b arranged to rotate with the crankshaft 28 via a slide collar 59.
- a cam plate 58 and a slide collar 59 are attached to the right end of the crankshaft 28 by spline fitting, and the fixed pulley half 55a is attached to the outer side in the axial direction thereof. It is tightened and fixed by 0.
- a cylindrical weight 61 is provided. As the rotation of the crankshaft 28 rises, the weight 61 moves radially outward due to centrifugal force, and the movable pulley half
- the driven pulley 56 is fixed to the right outer end of the transmission shaft 47 and is fixedly slidable in the axial direction to the outside of the fixed pulley half 56 a in the crankshaft direction. And a movable pulley half 56b. Above fixed pulley half 5
- the cylindrical slide collar 62 fixed to the shaft center of 6a is spline-fitted to the speed change shaft 47, and the shaft of the movable pulley half 5 6b is mounted on the slide collar 62.
- a cylindrical boss portion 63 fixed to the portion is mounted movably in the axial direction.
- the guide bin 64 implanted in the slide collar 62 can slide in the slide groove 63 a formed in a slit shape in the boss portion 63, and the movable pulley half 56 Squire 66
- a spring receiving member 65 made of an annular plate is attached to the tip of the slide collar 62 by a circular clip ° 65a.
- the spring receiving member 65 and the movable plastic half A coil spring 67, which constantly urges the movable bully half 56b toward the fixed pulley half 56a, is interposed between the coil spring 67 and the movable spring half 56b.
- the driven pulley 56 is inserted and disposed so as to be immersed in the distal end 62 a of the slide collar 62, and a lock nut screwed to the distal end 47 a of the transmission shaft 47.
- the transmission shaft 47 is fixed to the transmission shaft 47 from the point 66.
- the inner diameter of the slide collar 62 is set to be larger in a stepped manner than the outer diameter of the transmission shaft 47, and the tip end 47a of the transmission shaft 47 is set to be a smaller diameter in a stepped manner. I have.
- the lock nut 66 and the washer 66a can be inserted into the slide collar 62 without hindrance. In this manner, the lock nut 66 is moved from the spring receiving member 65 of the coil spring 67 to the crankshaft. It can be positioned inside the direction.
- the movable pulley half 56 b of the driven pulley 56 attached to the speed change shaft 47 is disposed outside the fixed pulley half 56 a in the crankshaft direction.
- An empty space can be secured in the inner portion of the driven pulley 56, and the centrifugal clutch mechanism 17 can be disposed adjacent to the fixed pulley half 56a by using this empty space.
- the mouth nut 66 is fixed to the movable half-bulb 56 b, and the spring receiving member 65 supporting the coil spring 67 for urging the pulley half 56 a is axially inward from the spring receiving member 65.
- the coil springs 67 have the required length and a simple structure can reduce the protrusion to the outside in the shifting axis direction, while maintaining the required length of the coil springs 6 and 7. Enlargement of the engine vehicle width can be suppressed.
- the lock nut 203 is added. Only the transmission case 204 protrudes outward in the vehicle width direction. In contrast, in the present embodiment, since the lock nut 66 is located axially inward of the outer end of the spring receiving member 65, the protrusion of the transmission case 45 is reduced by t (about 1 Omm). it can.
- the coil spring 67 is located on the outside in the axial direction, maintenance and replacement of the coil spring 67 can be performed simply by removing the clip 65a, thereby facilitating the work.
- the movable pulley half is arranged inside the fixed pulley half, that is, the coil spring is arranged inside in the axial direction, the whole driven bully must be removed, which is low in workability.
- the transmission case 45 has a substantially hermetic structure formed independently of the crankcase 22. When viewed from the right side (see FIG. 4), most of the upper part of the crankcase 22 is formed. Has an elliptical shape that covers The transmission case 45 is made up of a resin-made case body 45 a having a bottomed box shape that opens outward in the direction of the crank axis and a lid 45 b made of aluminum alloy that airtightly closes the opening. It is fixed together with the second case 41 by bolts 70. A gap a is provided between the bottom wall 45 c of the case body 45 a and the second case 41, and the gap a prevents heat from the engine 2 being transmitted to the transmission case 45. Restrained.
- An opening 41 e having a size that allows the centrifugal clutch mechanism 17 to enter and exit is formed outside the second outer peripheral wall 41 a forming the clutch chamber 38 in the axial direction.
- a clutch cover 71 is oil-tightly mounted in the opening 41e, and the clutch cover 71 is removably fastened to an opening edge of the second outer peripheral wall 41a by a port 72. It is fixed. As a result, the transmission case 45 is removed together with the driven pulley 56, and the centrifugal clutch mechanism 17 is removed by removing the clutch cover 71. It can be removed together with 7.
- the centrifugal clutch mechanism 17 is positioned and clamped so that it cannot move in the axial direction by one-side and other-side clutch bearings 80 and 81 mounted on the left end and the center of the transmission shaft 47 in the axial direction.
- the one-side clutch bearing 80 is supported by a clutch support wall 41 d
- the other-side clutch bearing 81 is supported by the clutch cover 71
- the clutch support wall 41d supporting the reduction bearing 53 is deviated to the left in the crankshaft direction from the second crank support wall 41c supporting the right journal bearing 36, in other words, the left side described above. It is located between the first crank support wall 40c supporting the journal bearing 35 and the second crank support wall 41c. More specifically, it is located on the cylinder axis A or slightly closer to the dividing line B than the cylinder axis A.
- the clutch cover 71 supporting the other-side clutch bearing 81 is located on the right side in the crankshaft direction with respect to the second crank support wall 41b supporting the right journal bearing 36. Furthermore, the speed reduction mechanism supporting wall 40 d supporting the left bearing 77 of the output shaft 48 is located further to the left outside in the crankshaft direction than the first crank supporting wall 40 c supporting the left journal bearing 35. ing.
- the V belt 57 wound around the driving pulley 55 and the driven pulley 56 is made of resin, the heat resistance and durability of the belt itself are compared with those of the rubber belt.
- the cooling of the V-belt 57 can be eliminated.
- the transmission case 45 can be made to have a closed structure, and water and dust can be prevented from entering.
- the outer diameters of the driving and driven pulleys 55 and 56 can be reduced, and the driving and driven pulleys 55 and 56 can be reduced accordingly.
- the distance between shafts can be shortened, and the entire engine can be made compact.
- the transmission case 45 since the transmission case 45 has a closed structure independent of the crankcase 22, engine heat is shut off by the gap a generated between the two cases 22, 45. The heat from the engine 2 is not easily transmitted to the transmission case 45, and the temperature rise in the belt compartment can be suppressed.
- the case body 45a is made of resin to which heat is hardly transmitted, transmission of heat from the engine 2 to the transmission case 45 can be suppressed from this point as well.
- the crankcase 22 is divided into first and second cases 40 and 41 in the crankshaft direction, and the transmission case 45 is disposed outside the second case 41 in the crankshaft direction. Since the centrifugal clutch mechanism 17 is arranged near the inner side of the case 45 in the crankshaft direction, the output shaft 48 can be coaxially arranged on the opposite side of the continuously variable transmission mechanism 16 of the transmission shaft 47, and the engine The dimension in the front-rear direction can be reduced while suppressing an increase in the width dimension of 2.
- the centrifugal clutch mechanism 17 since the centrifugal clutch mechanism 17 is sandwiched between the clutch bearings 80 and 81 mounted on the other side and the other side mounted on the transmission shaft 47, the centrifugal clutch mechanism 17 can be configured with a simple structure without using separate parts. Can be positioned and supported in any direction.
- the one-side clutch support wall 41 d supporting the one-side clutch bearing 80 is connected to the first and second crank support walls supporting the left and right journal bearings 35, 36 of the crankshaft 28. Position between 40c and 41c, and place the clutch cover 71 supporting the other clutch bearing 81 on the outside of the second crank support wall 41c supporting the right journal bearing 36 in the crankshaft direction.
- the first crank support wall 40c and the clutch one-side support wall 41d and the second crank support wall 41c and the clutch cover 71 are located on the same line.
- the space between the clutch chamber 38 and the centrifugal clutch mechanism 17 can be secured while shortening the distance between the shaft 28 and the transmission shaft 47, and the centrifugal clutch mechanism 17 can be stored compactly, and the engine as a whole can be made compact. .
- the clutch cover 71 is detachably attached to the opening 4 1 e of the second case 41.
- the centrifugal clutch mechanism 17 can be removed together with the transmission shaft 47 by removing the transmission case 45 and the clutch cover 71, so that maintenance and parts replacement work can be easily performed.
- the output shaft 48 is disposed coaxially on the anti-transmission case 45 side of the transmission shaft 47, and the drive sprocket 49 is attached to the output shaft 48, so that the centrifugal
- the latch mechanism 17 and the drive sprocket 49 can be arranged coaxially, and the longitudinal dimension of the engine can be reduced.
- the eccentric clutch mechanism 17 is disposed close to and inside the driven pulley 56 in the crankshaft direction.
- This centrifugal clutch mechanism 17 is of a wet multi-plate type, and as shown mainly in FIGS. 3 and 12 to 16, a spline is formed so that the boss 83 b of the outer clutch 83 rotates together with the transmission shaft 47.
- the inner clutch 84 is coaxially arranged within the outer clutch 83, and the hub portion 84a of the inner clutch 84 is spline-fitted so as to rotate together with the primary reduction gear 74. It has a structure.
- the primary reduction small gear 74 is rotatably supported by the transmission shaft 47.
- the outer clutch 83 closes the right end opening of the outer peripheral wall 83c with the bottom wall 83d and opens at the other end. It has a bowl shape with 8 3 e. Further, a slit 83f is formed on the outer peripheral wall 83c so as to extend in the axial direction at predetermined angular intervals and penetrate therethrough.
- the inner clutch 84 has an opening at one end of an outer peripheral wall 84b closed by an inclined bottom wall 84c and an opening at the other end.
- slits 84d are formed in a groove shape so as to extend in the axial direction at predetermined angular intervals.
- a plurality of oil holes 84e are formed at corners between the outer peripheral wall 84b and the bottom wall 84c so as to penetrate inside and outside at predetermined angular intervals.
- outer clutch 83 a plurality of iron clutch plates 85 are arranged.
- the outer clutch plate 85 is annular and has a predetermined angle on the outer peripheral edge thereof. Protrusions 85 e formed at intervals are engaged with the slits 83 f, whereby the clutch plate 85 can move in the axial direction and rotate together with the clutch 83. .
- two pressing plates 86, 86 are arranged at both ends of the outer clutch plate 85, and the pressing clutch 86 is also rotated so that the pressing plate 86 rotates together with the outer clutch 83. It is locked to.
- An inner clutch plate 87 is disposed between the outer clutch plate 85 and the pressing plate 86.
- Each of the inner clutch plates 87 has an annular shape, and a projection 87 a is formed on the inner peripheral edge thereof at a predetermined angular interval ⁇ , and the projection 87 a is formed on the outer peripheral surface of the inner clutch 84. It is locked in the formed slit 84d. In this manner, each of the inner clutch plates 87 is movable in the axial direction and rotates together with the inner clutch 84.
- a cam surface 83a is formed inside the outer clutch 83, and a weight 88 is disposed between the cam surface 83a and the outer pressing plate 86.
- This weight 88 moves radially outward due to the centrifugal force of the outer clutch 83, moves to the left (clutch connection direction) in FIG. 12 by the cam surface 83a, and moves the pressing plate 86.
- the inner clutch plates 85 and 86 are connected to each other.
- the upper side of the axis of the centrifugal clutch mechanism 17 indicates the disconnected state, and the lower side thereof indicates the connected state.
- the centrifugal clutch mechanism 17 is provided with a clutch plate sticking prevention mechanism 90.
- the sticking prevention mechanism 90 separates the outer clutch plate 85 and the pressing plate 86 from each other between the respective clutch plates 85 and between the outer clutch plate 85 and the pressing plate 86. It is configured with a leaf spring 9 1 biased in the direction.
- Pins 92 for regulating the axial movement of the inner clutch plate 87 are passed through the inner clutch plates 87 at intervals in the circumferential direction.
- a coil spring 93 for urging the inner clutch plates 87 in a direction to separate the inner clutch plates 87 from each other is mounted therebetween.
- the weight 88 moves outward in the clutch radial direction by centrifugal force as the engine speed increases, and the axial position of the weight 88 is determined by the cam surface 83a.
- the weight 88 pushes and moves the pressing plate 86 to press the auta and the inner clutch plates 85 and 87 into pressure.
- the engine rotation is transmitted from the transmission shaft 47 to the output shaft 48 via the reduction gear mechanism 18, and the rotation of the output shaft 48 causes the rear wheel 7 via the drive sprocket 49 and the chain 50. It is driven to rotate.
- the weight 88 moves inward in the radial direction, and when the engine speed falls below a predetermined value, the pressure contact force by the weight 88 is released, and the above-mentioned rotor and inner clutch are disengaged. Plates 85 and 87 rotate relative to each other, and engine rotation is cut off between transmission shaft 47 and output shaft 48.
- the axial movement of the inner clutch plate 87 is restricted by each pin 92, so that the inner crack plate 87 can be prevented from tilting when the clutch is disconnected, and the clutch drag phenomenon is also prevented from this point. it can.
- the lubricating oil system is configured such that the lubricating oil in the lubricating oil chamber 95 formed in the bottom portion 22 a of the crankcase 22 is sucked by a lubricating oil pump 96 so that the bearings of the crankshafts 28 and the camshaft 31 are formed.
- the lubricating oil is lubricated to the lubricating part by returning to the lubricating oil chamber 95 by gravity.
- the lubricating oil pump 96 is disposed mainly below the first case 40 of the crankcase 22, as shown in FIG. 11, and has a suction port 97a and a discharge port 97b.
- a pump shaft 96a is supported by a housing 97, and a pump gear 98 is mounted on the outer end of the pump shaft 96a.
- the first case 40 is provided with a suction passage 40 f communicating with the suction port 97 a, and the suction passage 40 f is provided on the bottom surface in the lubricating oil chamber 95 via an oil strainer 99. It is open to. Further, a lubricating oil supply passage 40 g communicating with the discharge port 97 b is formed in the first case 40.
- the supply passage 40 g communicates with a main supply passage 44 a formed in the generator case 44 via an oil filter 100 on the way, and a downstream end of the main supply passage 44 a. Is connected to an oil chamber 44 c communicating with the left end face of the crankshaft 28.
- An oil passage 28 e communicating with the oil chamber 44 c is formed in the crankshaft 28 in the axial direction.
- the oil passage 28 e is a branch passage formed in the crank pin 29.
- the crankshaft 29 and the connecting rod 27 are connected to each other via a connecting pin 27 through the opening 29a.
- the lubricating oil sucked by the lubricating oil pump 96 is supplied to the oil passage 28 e through the supply passage 40 g and the main supply passage 44 a, and is then fed from the oil passage 28 e through the branch passage 29 a. And supplied to the coupling bearing 101.
- the lubricating oil supplied to the connecting bearing portion 101 is scattered into the crank chamber 37 by the supplied hydraulic pressure and the centrifugal force of the crankshaft 28, and a part of the scattered lubricating oil is reduced by the deceleration chamber. 39, lubricates the secondary reduction small gear 52a and large gear 48a, and then falls into the lubricating oil chamber 95.
- the bottom part 22 a of the crankcase 22 is located below the transmission case 45, that is, located in the projection plane of the transmission case 45 when viewed from a plane.
- a bulging portion 22b is formed (see Figs. 8 and 11). Due to the formation of the bulging portion 22 b, the center line D in the width direction of the entire lubricating oil chamber 95 is shifted toward the transmission case 45.
- the oil pump 96 is attached to an inner wall 22 c of the lubricating oil chamber 95 opposite to the transmission case 45. According to the present embodiment, since the bulging portion 22b is formed so as to be located below the transmission case 45 at the bottom portion 22a of the crankcase 22, an empty space below the transmission case 45 is formed.
- the V-belt 57 is made of resin, and the transmission case 45 is made independent of the crankcase 12, so that the belt itself is compared with the case of using a rubber belt.
- the heat resistance and durability of the engine can be improved, and the heat effect from the engine can be suppressed.
- the diameter of the driving and driven pulleys 55 and 56 can be reduced, the transmission case 45 can be reduced in size, and an empty space can be provided below the transmission case 45.
- the swollen portion 22b was formed to increase the lubricating oil capacity.
- the lubricating oil scattered from the connecting bearing portion 101 between the connecting rod 27 and the crank pin 29 is guided to the centrifugal clutch mechanism 17.
- the clutch mechanism 17 at least a part of the clutch mechanism 17 is located in a lubricating oil scattering area described later, and the opening 83 e of the outer clutch 83 is located in the lubricating oil scattering area.
- a slit 83 f formed on the outer peripheral wall 83 c of the outer clutch 83 is disposed so as to oppose the scattering direction of the lubricating oil.
- This introduction opening 103 is formed. This introduction opening 103 is shown in two points in FIG. It has a width w in the crankshaft direction indicated by a chain line, and extends on both sides (upper and lower sides) of a plane C including both the axes of the crankshaft 28 and the transmission shaft (rotating shaft) 47 as shown in FIG. It has a height dimension h.
- the above-described lubricating oil scattering region in the present embodiment is a region in which the introduction opening 103 is substantially perpendicular to a plane along the opening and projected from the crankshaft 28 side in the plane C direction. Can be.
- a guide portion 104 extending inside the clutch chamber 38 is formed integrally with the clutch support wall portion 41d.
- the guide portion 104 extends obliquely in the vertical direction so as to intersect with the plane C connecting the crankshaft 28 and the transmission shaft 47 and to substantially face the introduction opening 103.
- the guide portion 104b extends toward the inner clutch 84 so as to enter between the outer peripheral wall 84d of the inner clutch 84 and the boss portion 84a (see FIGS. 3 and 7).
- the lubricating oil supplied to the coupling bearing portion 101 is supplied to the crank chamber 37 by the supplied hydraulic pressure and by the centrifugal force generated by the rotation of the coupling bearing portion 101. And a part of the scattered lubricating oil is introduced into the clutch chamber 38 through the introduction opening P103. A part of the lubricating oil introduced into the clutch chamber 38 is received by the lubricating oil receiving portion 104, and is guided by the guide portion 104 b to the inner circumferential surface of the outer peripheral wall ⁇ 4 e of the inner clutch 84. Fall to the surface.
- the dropped lubricating oil is supplied between the outer clutch and the inner clutch plates 85 and 87 through an oil hole 84 e by centrifugal force generated by the rotation of the inner clutch 84.
- Another part of the lubricating oil introduced into the clutch chamber 38 passes through the slit 83 f formed on the outer peripheral wall of the outer clutch 83, and the luter and inner clutch plates 85, 87. Will be supplied in between.
- the crank pin 29 and the connecting rod large end 27 a Since the lubricating oil supplied to the coupling bearing portion 101 is guided to the centrifugal clutch mechanism 17, a large amount of lubricating oil that is spouted and scattered from the coupling bearing portion 101 can be supplied to the centrifugal clutch mechanism 17, There is no need to provide a special lubricating oil path, and a sufficient amount of lubricating oil can be supplied to the centrifugal clutch mechanism 17 to prevent seizure of the auta and inner clutch plates 85, 87.
- the centrifugal clutch mechanism 17 is disposed in the clutch chamber 38 defined by the crank chamber 37, and the second outer peripheral wall that defines the clutch chamber 38 and the crank chamber 37. 4 1a is formed with an inlet opening 103 that allows the ingress of lubricating oil, so the lubricating oil scattered from the crank chamber 37 side can be effectively transferred to the clutch chamber 38 with a very simple structure. Can be introduced.
- the opening 83 e of the outer clutch 83 is directed to the lubricating oil scattering area, and the slit formed on the outer peripheral wall 83 c of the outer clutch 83 is formed. Since 83 f is arranged so as to open in the lubricating oil scattering direction, the lubricating oil can be supplied between the outer clutch plate and the inner clutch plate, and seizure of the clutch plate can be avoided.
- a guide portion 104 extending inward of the clutch chamber 38 is integrally formed with the clutch support wall portion 41d, and the guide portion 104 is connected to the crankshaft 28 and the transmission shaft 47.
- a lubricating oil receiving portion 104a extending on the extension line connecting the lubricating oil receiving portion 103 and the lower end of the lubricating oil receiving portion 104a. Since the guide portion 104b extends in an arc shape so as to go round, lubricating oil can be more reliably supplied to the rotor and the inner clutch plates 85, 87.
- the lubricating oil that has entered from the introduction opening 103 is first received by the lubricating oil receiving portion 104 a, and travels from the receiving portion 104 a through the guide portion 104 b to the inner clutch 84. And falls on the inner surface of the outer peripheral wall 84b or the boss portion 84a. Then, the dropped lubricating oil is blown outward by the centrifugal force generated by the rotation of the inner clutch 84 and passes through the oil hole 84 e to the outer clutch plate 85 and the inner clutch plate 87. Is supplied between
- the present invention is not limited to a wet multi-plate clutch, and is also applicable to a so-called single-type automatic centrifugal clutch mechanism described in the above-mentioned patent document.
- a bowl-shaped outer clutch is fixed to the output shaft side, an input member is arranged so as to be located in the outer clutch, and the input member is fixed to the input shaft side.
- the shoe is swingably supported by a member, and the shoe is brought into contact with the inner surface of the outer clutch by centrifugal force.
- the opening of the outer clutch is directed to the lubricating oil scattering region, and the slit formed in the outer clutch is opposed to the lubricating oil scattering direction.
- a kick shaft 110 is disposed substantially vertically below the output shaft 48 in parallel with the output shaft 48.
- the kick shaft 110 has a portion inside the drive sprocket 49, which is supported by the boss portion 4Oh of the first case 40, and a portion outside the drive sprocket. It is supported by a pair of bosses 44 b formed on the machine cover 44.
- a kick arm 111 is attached to the outer end of the kick shaft 110.
- a kick gear 112 is spline-fitted to the inner end of the kick shaft 110 so as to be slidable in the axial direction.
- the kick gear 112 is located in the first case 40. I have.
- a return spring 113 is wound around the inner end of the kick shaft 110, and the return spring 113 biases the kick shaft 110 to the stepping position.
- a main intermediate shaft 114 and a sub intermediate shaft 115 are arranged between the kick shaft 110 and the crankshaft 28 in parallel with the kick # 110. This main intermediate shaft 1 1 4 PT / parent / hidden
- the first intermediate case 1 40 and the second case 4 1 are supported by being supported by a bridge.
- the main intermediate shaft 1 1 4 is equipped with a main intermediate gear 1 1 6 that can be combined with the kick gear 1 1 2
- the sub intermediate shaft 115 is supported by a bearing portion 40j formed in the first case 40.
- the inner and outer ends of the sub intermediate shaft 115 are the I case. It protrudes inside and outside 40.
- a first intermediate gear 1 15a is formed inside the case of the sub intermediate shaft 1 15 to be combined with the main intermediate gear 1 16 and a second intermediate gear 1 17 is formed outside the case. It is installed.
- a first crank gear 121 described later is combined with the second intermediate gear 117.
- the kick shaft 110 rotates, and with the rotation, the kick gear 112 moves in the axial direction to engage with the main intermediate gear 116, and The power is transmitted to the first crank gear 121 via the second intermediate gears 115a and 117, and the crankshaft 28 rotates.
- the one-way clutch 120 is provided with a starting gear 120a, and the starting gear 120a is provided with a drive gear 1 25 of a star motor 125 through an idler gear 124. a is connected.
- the star motor 125 is arranged and fixed to the front wall of the crankcase 22 with the motor axis oriented parallel to the crankshaft 28.
- the kick gear 112, the main intermediate gear 116, and the first intermediate gear 115a are arranged at positions inside the first case 40 communicating with the lubricating oil chamber 95. Further, the second intermediate gear 117, the first crank gear 121, and the force spring 122 are arranged outside the first case 40.
- the kick gear 112, the main intermediate gear 116, and the first intermediate gear 115a are located at the portions communicating with the lubricating oil chamber 95. 4466
- the joints of these gears can be lubricated sufficiently.
- the main intermediate shaft 1 15 penetrates from the inside of the first case 40 to the outside, transmitting the rotation of the kick shaft 110 from the inside to the outside of the main intermediate shaft 1 15, Since the gear 117 power was transmitted to the crankshaft 28 via the first crank gear 11, the first crank gear 121 could be arranged outside the crank journal portion 28 c, and the crank bearing The distance between 35 and 36 can be reduced, and the crankshaft 28 can be supported by reducing the bending moment by the condole 27. Further, a space for arranging the cam sprocket 122 and the second crank gear 127 can be secured, and the layout around the crank shaft can be easily performed.
- the kick shaft 110 is disposed substantially below the output shaft 48 in the vertical direction, the kick arm 111 can be easily depressed, and the front and rear dimensions of the engine 2 can be reduced. Can be.
- the inside of the kick shaft 110 in the rear wheel drive sprocket 49 in the vehicle width direction is axially supported by the first clutch support wall 4 O d of the crank case 22, and the outside in the vehicle width direction is the generator case 4. Since the kick arm 111 is attached to the outwardly projecting end of the generator case 44 of the kick shaft 110, the kick arm 111, and thus the kick arm 111 is mounted. It can be located at the optimal stepping position without interfering with the rear wheel drive sprocket 49.
- the kick shaft 110 is located in the axial projection plane of the transmission case 45 and the centrifugal clutch mechanism 17 when viewed in the crankshaft direction. positioned. More specifically, it is arranged so as to be located substantially vertically below driven pulley 56.
- the kick shaft 110 is arranged on the opposite side of the transmission case 45 as described above, There is no need to secure a kick shaft arrangement space in the transmission case 45, so that there is a slight gap b (see Fig. 3) between the drive pulley 55 and the driven pulley 56 of the continuously variable transmission mechanism 16 described above.
- the engine can be arranged close to each other, and the front and rear length of the engine can be reduced accordingly.
- the kick shaft 110 is arranged on the projection plane of the transmission case 45 in the crankshaft direction, the kick shaft 110 can be arranged at a position close to the crankshaft 28 and at a position where it can be easily depressed. it can.
- the centrifugal clutch mechanism 17 is disposed near the inner side of the driven burry 56 in the crankshaft direction, and the kick shaft 110 is positioned in the axial projection plane of the centrifugal clutch mechanism 17 and the transmission shaft. Since it is located approximately vertically below 7, the kick shaft 110 can be located at the position where it can be easily depressed by using the empty space in the projection surface of the centrifugal clutch mechanism, and the kick shaft 110 can be placed in front of and behind the engine 2. The length can be reduced.
- a balancer shaft 129 is disposed above and behind the crankshaft 28 in parallel with the crankshaft 28.
- the balancer shaft 1229 is supported by the first and second cases 40 and 41 via balancer bearings 130 and 131, respectively.
- the left end portion of the balancer shaft 127 projects outward from the first case 40, and a balancer gear 132 is coupled to the projection.
- a damper member 133 is provided on the inner peripheral portion of the balancer gear 132.
- the left and right crank arms 28a, 28b of the crankshaft 28 are located in the above balancer bearings 130, 131, and the balancer weight 19a of the balancer shaft 1229 is provided. Is disposed between the left and right crank 'arms 28a and 28b and close to the crankshaft 28 side so as to overlap the rotation locus of the crankpin 29. This makes the balance around the balancer axis compact.
- a second crank gear (second drive gear) 127 is mounted on the first crank gear (first drive gear) 121 press-fitted into the crankshaft 28 so as to rotate together.
- the balancer gear (second driven gear) 132 is engaged with the second crank gear 127. More specifically, an inner peripheral tooth 127 a is formed on the inner peripheral surface of the second crank gear 127, and the inner peripheral tooth 127 a of the first crank gear 122 is formed on the inner peripheral tooth 127 a. Outer peripheral teeth 121a are fitted (see Fig. 6).
- the rotation of the crankshaft 28 is transmitted from the first crank gear 121 to the balancer gear 132 via the second crank gear 127.
- the first crank gear 121 is connected to the pump gear (first driven gear) 98 via a second intermediate gear 117. In this way, the first crank gear 121 and the second intermediate gear 117 are shared for kick start and oil pump drive.
- the one-way clutch 120 mounted on the crankshaft 28 and the first crank gear 12 2 are provided with a nut 123 screwed to the left end of the crankshaft 28. By being tightened, the sleeve 43 and the journal bearing 35 are sandwiched so as not to move in the axial direction.
- the crankshaft length can be shortened accordingly and the engine width can be made more compact.
- the inner circumferential teeth 17 a of the second crank gear 127 are fitted to the first crank gear 121 press-fitted to the crankshaft 28, and the second intermediate gear 117 is fitted.
- the press-fit length of the first crank gear 111 into the crankshaft 28 can be sufficiently ensured, and the rotation of the crankshaft 28 is reliably transmitted to the pump gear 98 and the balancer gear 132. can do.
- the structure is adopted in which the outer peripheral teeth 121 a of the first crank gear 122 and the inner peripheral teeth 127 a of the second crank gear 127 are fitted.
- 1 2 7 is easy to assemble and easy to remove for maintenance 3 04466
- the arrangement structure of each shaft of the engine 2 is as follows.
- the transmission shaft 47 and the output shaft 48 are disposed on the substantially same horizontal plane behind the crankshaft 28.
- the balancer shaft 12 9 and the reduction shaft 52 are arranged, and the kick shaft 1 10 and the pump shaft 9 6 are arranged below.
- a, main and sub intermediate shafts 114 and 115 are arranged.
- the kick shaft I 10 is disposed substantially vertically below the output shaft 48, and the pump shaft 96 a is disposed substantially vertically below the balancer shaft 119. Further, the main and sub intermediate shafts 114 and 115 are arranged on a line connecting the crankshaft 28 and the kick shaft 110.
- the balancer shaft 1 19 is arranged above the horizontal plane C including the crankshaft 28 and the output shaft 48, and the kick shaft 1 10 and the pump shaft 9 of the oil pump 96 are arranged below. Since 6a is arranged, these can be arranged above and below in a well-balanced manner, and the enlargement of the engine can be avoided. That is, there is an empty space above the horizontal plane C and behind the cylinder bore, and the balancer shaft 129 is arranged using this space. Since the balancer shaft 1229 rotates with a large rotation path of the weight 1229a, the loss horsepower due to the lubricating oil agitation increases when the balancer shaft 1229 is immersed in the lubricating oil.
- the shaft 1 29 does not diffuse the lubricating oil.
- the deceleration shaft 52 is disposed above the horizontal plane C by utilizing an empty space between the balancer shaft 12 9 and the output shaft 48.
- the lubricating oil is located at the upper part where it is difficult to supply the lubricating oil.However, the lubricating oil scattered from the connecting bearing 101 of the crankshaft 28 is supplied to the reduction gear 75 etc. No problem.
- the front and rear length of the gin 2 can be reduced, and the kick shaft 110 can be arranged at a position where it can be easily depressed.
- the lubricating oil supplied to the connection between the crankpin and the large end of the connector is guided to the clutch mechanism.
- a large amount of lubricating oil scattered from the connection portion by centrifugal force can be supplied to the clutch mechanism.
- there is no need to provide a special lubricating oil supply structure and a sufficient amount of lubricating oil can be supplied to the clutch mechanism, so that seizure of the clutch mechanism can be prevented.
- the clutch mechanism is arranged so that at least a part of the clutch mechanism is located in a region where the lubricating oil scatters from the connecting portion, so that the scattered lubricating oil is reliably introduced into the clutch mechanism. be able to.
- the clutch mechanism is arranged so that the opening of the ata clutch is directed to the lubricating oil scattering region, the scattered lubricating oil can be reliably introduced into the clutch mechanism from the opening of the auta clutch. .
- the plurality of slits penetratingly formed in the outer peripheral wall of the outer clutch toward the inside are opened in the direction in which the lubricating oil is scattered, so that the lubricating oil can be more reliably supplied to the clutch mechanism.
- the clutch mechanism is arranged in the clutch chamber defined by the crank chamber, and the partition opening of both chambers is formed with an introduction opening for permitting the entry of lubricating oil.
- the introduction opening is set to a sufficient size in the lubricating oil scattering direction, the lubricating oil from the crank chamber can be introduced into the clutch chamber through the introduction opening.
- the clutch mechanism can be lubricated with a simple structure while housed in the clutch chamber.
- the lubricating oil introduced inside can be reliably supplied by centrifugal force to the outer portion, inner clutch plate portion, or the portion between the input member and the outer clutch. Can be prevented.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Mechanical Operated Clutches (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Arrangement Of Transmissions (AREA)
- Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
- Transmissions By Endless Flexible Members (AREA)
- Transmission Devices (AREA)
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE60330855T DE60330855D1 (de) | 2002-04-08 | 2003-04-08 | Kupplungsmechanismusschmierkonstruktion für motor |
EP03745705A EP1498628B1 (en) | 2002-04-08 | 2003-04-08 | Clutch mechanism lubricating structure of engine |
JP2003582429A JP3993170B2 (ja) | 2002-04-08 | 2003-04-08 | エンジンのクラッチ機構潤滑構造 |
AT03745705T ATE454565T1 (de) | 2002-04-08 | 2003-04-08 | Kupplungsmechanismusschmierkonstruktion für motor |
AU2003235997A AU2003235997A1 (en) | 2002-04-08 | 2003-04-08 | Clutch mechanism lubricating structure of engine |
BRPI0304832-2B1A BR0304832B1 (pt) | 2002-04-08 | 2003-04-08 | Motor com estrutura de lubrificação para um mecanismo de embreagem |
CN038062801A CN1646821B (zh) | 2002-04-08 | 2003-04-08 | 发动机的离合器机构润滑结构 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002-105023 | 2002-04-08 | ||
JP2002105023 | 2002-04-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003085278A1 true WO2003085278A1 (fr) | 2003-10-16 |
Family
ID=28786359
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/004466 WO2003085278A1 (fr) | 2002-04-08 | 2003-04-08 | Structure de lubrification de mecanisme d'embrayage du moteur |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP1498628B1 (ja) |
JP (1) | JP3993170B2 (ja) |
CN (1) | CN1646821B (ja) |
AT (1) | ATE454565T1 (ja) |
AU (1) | AU2003235997A1 (ja) |
BR (1) | BR0304832B1 (ja) |
DE (1) | DE60330855D1 (ja) |
ES (1) | ES2337352T3 (ja) |
WO (1) | WO2003085278A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1950460A2 (en) | 2007-01-26 | 2008-07-30 | Yamaha Hatsudoki Kabushiki Kaisha | Engine unit and straddle-type vehicle provided with the same |
WO2009098913A1 (ja) * | 2008-02-04 | 2009-08-13 | Honda Motor Co., Ltd. | 車両のパワーユニット |
WO2009119210A1 (ja) * | 2008-03-28 | 2009-10-01 | 本田技研工業株式会社 | 車両のパワーユニット |
US7637828B2 (en) | 2006-11-29 | 2009-12-29 | Yamaha Hatsudoki Kabushiki Kaisha | Belt-type continuously variable transmission and straddle-type vehicle including the same |
US8187127B2 (en) | 2006-11-29 | 2012-05-29 | Yamaha Hatsudoki Kabushiki Kaisha | Belt-type continuously variable transmission and straddle-type vehicle equipped with the same |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5030413B2 (ja) * | 2005-11-07 | 2012-09-19 | ヤマハ発動機株式会社 | 鞍乗型車両 |
JP4684975B2 (ja) * | 2006-09-29 | 2011-05-18 | 本田技研工業株式会社 | 動力伝達装置 |
JP2008298129A (ja) * | 2007-05-30 | 2008-12-11 | Yamaha Motor Co Ltd | 遠心クラッチおよびそれを備えた鞍乗型車両 |
JP5616667B2 (ja) * | 2010-03-31 | 2014-10-29 | 本田技研工業株式会社 | 動力伝達機構のオイル供給構造 |
JP6571917B2 (ja) * | 2014-09-26 | 2019-09-04 | 株式会社エフ・シー・シー | クラッチ装置 |
Citations (7)
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JPS5192949A (ja) * | 1975-02-12 | 1976-08-14 | ||
JPS59222625A (ja) * | 1983-05-30 | 1984-12-14 | Yamaha Motor Co Ltd | 摩擦クラツチ |
JPS604626A (ja) * | 1983-06-24 | 1985-01-11 | Yamaha Motor Co Ltd | 自動二輪車等の車両における動力伝達装置 |
JPH03244831A (ja) * | 1990-02-20 | 1991-10-31 | Yamaha Motor Co Ltd | 多板摩擦クラッチ |
JPH04271987A (ja) * | 1991-02-27 | 1992-09-28 | Suzuki Motor Corp | 自動二輪車のクラッチレリーズ機構 |
JPH08121497A (ja) * | 1994-10-27 | 1996-05-14 | Yamaha Motor Co Ltd | バックトルクリミッター付クラッチ |
JPH10315806A (ja) * | 1997-05-20 | 1998-12-02 | Suzuki Motor Corp | 自動二・三輪車のクラッチ装置 |
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JPS58148211A (ja) * | 1982-02-26 | 1983-09-03 | Honda Motor Co Ltd | 内燃機関のトルクリミツタ潤滑装置 |
JP2001003723A (ja) * | 1999-06-17 | 2001-01-09 | Yamaha Motor Co Ltd | 自動二輪車用エンジン |
-
2003
- 2003-04-08 AT AT03745705T patent/ATE454565T1/de not_active IP Right Cessation
- 2003-04-08 EP EP03745705A patent/EP1498628B1/en not_active Expired - Lifetime
- 2003-04-08 JP JP2003582429A patent/JP3993170B2/ja not_active Expired - Fee Related
- 2003-04-08 CN CN038062801A patent/CN1646821B/zh not_active Expired - Fee Related
- 2003-04-08 WO PCT/JP2003/004466 patent/WO2003085278A1/ja active Application Filing
- 2003-04-08 ES ES03745705T patent/ES2337352T3/es not_active Expired - Lifetime
- 2003-04-08 AU AU2003235997A patent/AU2003235997A1/en not_active Abandoned
- 2003-04-08 DE DE60330855T patent/DE60330855D1/de not_active Expired - Lifetime
- 2003-04-08 BR BRPI0304832-2B1A patent/BR0304832B1/pt not_active IP Right Cessation
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5192949A (ja) * | 1975-02-12 | 1976-08-14 | ||
JPS59222625A (ja) * | 1983-05-30 | 1984-12-14 | Yamaha Motor Co Ltd | 摩擦クラツチ |
JPS604626A (ja) * | 1983-06-24 | 1985-01-11 | Yamaha Motor Co Ltd | 自動二輪車等の車両における動力伝達装置 |
JPH03244831A (ja) * | 1990-02-20 | 1991-10-31 | Yamaha Motor Co Ltd | 多板摩擦クラッチ |
JPH04271987A (ja) * | 1991-02-27 | 1992-09-28 | Suzuki Motor Corp | 自動二輪車のクラッチレリーズ機構 |
JPH08121497A (ja) * | 1994-10-27 | 1996-05-14 | Yamaha Motor Co Ltd | バックトルクリミッター付クラッチ |
JPH10315806A (ja) * | 1997-05-20 | 1998-12-02 | Suzuki Motor Corp | 自動二・三輪車のクラッチ装置 |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7637828B2 (en) | 2006-11-29 | 2009-12-29 | Yamaha Hatsudoki Kabushiki Kaisha | Belt-type continuously variable transmission and straddle-type vehicle including the same |
US8187127B2 (en) | 2006-11-29 | 2012-05-29 | Yamaha Hatsudoki Kabushiki Kaisha | Belt-type continuously variable transmission and straddle-type vehicle equipped with the same |
EP1950460A2 (en) | 2007-01-26 | 2008-07-30 | Yamaha Hatsudoki Kabushiki Kaisha | Engine unit and straddle-type vehicle provided with the same |
JP2008184909A (ja) * | 2007-01-26 | 2008-08-14 | Yamaha Motor Co Ltd | エンジンユニットおよびそれを備えた鞍乗型車両 |
US7721700B2 (en) | 2007-01-26 | 2010-05-25 | Yamaha Hatsudoki Kabushiki Kaisha | Engine unit and straddle-type vehicle provided with the same |
WO2009098913A1 (ja) * | 2008-02-04 | 2009-08-13 | Honda Motor Co., Ltd. | 車両のパワーユニット |
JP2009184399A (ja) * | 2008-02-04 | 2009-08-20 | Honda Motor Co Ltd | パワーユニット |
WO2009119210A1 (ja) * | 2008-03-28 | 2009-10-01 | 本田技研工業株式会社 | 車両のパワーユニット |
JP2009243288A (ja) * | 2008-03-28 | 2009-10-22 | Honda Motor Co Ltd | パワーユニット |
Also Published As
Publication number | Publication date |
---|---|
DE60330855D1 (de) | 2010-02-25 |
JP3993170B2 (ja) | 2007-10-17 |
CN1646821B (zh) | 2010-05-26 |
JPWO2003085278A1 (ja) | 2005-08-11 |
BR0304832B1 (pt) | 2013-10-08 |
ES2337352T3 (es) | 2010-04-23 |
BR0304832A (pt) | 2004-08-17 |
CN1646821A (zh) | 2005-07-27 |
ATE454565T1 (de) | 2010-01-15 |
EP1498628A4 (en) | 2006-05-03 |
EP1498628B1 (en) | 2010-01-06 |
EP1498628A1 (en) | 2005-01-19 |
AU2003235997A1 (en) | 2003-10-20 |
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