JP2009057037A - Transmission mechanism and vehicle provided with the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission mechanism capable of suppressing the increase in rotating loss of a main shaft. <P>SOLUTION: This transmission 77 (transmission mechanism) is provided with a main shaft 47 to which the drive force of a crankshaft 33 is transmitted to be rotated, a clutch mechanism part 37 capable of disconnecting and connecting the drive force transmitted to the main shaft 47 from the crankshaft 33, and a rod member 50 and a push rod 54 connected to the clutch mechanism part 37, with the rod member and the push rod moving in an axial direction to actuate the clutch mechanism part 37 so as to disconnect and connect the drive force transmitted to the main shaft 47 from the crankshaft 33. The rod member 50 and the push rod 54 include a flange part 54d configured to press the main shaft 47 when the clutch mechanism part 37 is actuated so as to disconnect the drive force transmitted to the main shaft 47 from the crankshaft 33. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a speed change mechanism and a vehicle including the same, and more particularly to a speed change mechanism including a main shaft and a clutch mechanism portion capable of intermittently transmitting a driving force transmitted to the main shaft, and a vehicle including the speed change mechanism.

  2. Description of the Related Art Conventionally, a vehicle transmission (transmission mechanism) including a main shaft and a clutch mechanism portion that can interrupt a driving force transmitted to the main shaft is known (see, for example, Patent Document 1). The conventional vehicle transmission disclosed in Patent Document 1 includes a main shaft, a clutch capable of interrupting a driving force transmitted to the main shaft, a fixed plate that rotates together with the main shaft, and a base member that supports the main shaft. And a leaf spring disposed between the fixed plate and the base member and biasing the fixed plate. The leaf spring is configured to be constantly biased with respect to the fixed plate, and has a function of reducing the rotational speed of the main shaft after the driving force is cut with respect to the main shaft by the clutch. In other words, the vehicle transmission (transmission mechanism) according to Patent Document 1 is configured to reduce the inertial force in the rotation direction of the main shaft by reducing the rotation speed of the main shaft. As a result, even when the gear shift operation is performed immediately after the driving force is cut with respect to the main shaft, it is possible to suppress an increase in the impact received by the vehicle transmission.

JP 2000-168378 A

  However, in the conventional vehicle transmission (transmission mechanism) disclosed in Patent Document 1, the leaf spring is always biased against the fixed plate even during a shift operation, so that the rotation loss of the main shaft is small. Always occurs. For this reason, the conventional vehicle transmission disclosed in Patent Document 1 has a problem in that the rotation loss of the main shaft increases.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a speed change mechanism capable of suppressing an increase in the rotation loss of the main shaft and the speed change mechanism. Is to provide a vehicle.

Means for Solving the Problems and Effects of the Invention

  In order to achieve the above object, a speed change mechanism according to a first aspect of the present invention includes a crankshaft, a main shaft that is rotated by transmitting a driving force of the crankshaft, and a crankshaft that is transmitted from the crankshaft to the main shaft. A clutch mechanism that is capable of disconnecting and connecting the driving force, and a clutch mechanism that is connected to the clutch mechanism and is moved in the axial direction to disconnect and connect the driving force transmitted from the crankshaft to the main shaft. A rod portion that is actuated, and the rod portion is configured to push the main shaft when the clutch mechanism portion is actuated so as to cut the driving force transmitted from the crankshaft to the main shaft. including.

  In the speed change mechanism according to the first aspect, as described above, the main shaft is pressed when the clutch mechanism is operated so as to cut the driving force transmitted from the crankshaft to the main shaft. A pressing portion configured as described above is provided. Thereby, since the pressing portion presses the main shaft only when the clutch mechanism portion that is normally operated when performing the shift operation is operated, compared to the case where the pressing portion always presses against the main shaft, An increase in rotation loss of the main shaft can be suppressed. In addition, since the main shaft is pressed after the driving force transmitted from the crankshaft to the main shaft is cut, the pressing portion always presses the main shaft of the pressing portion as compared with the case where the main shaft is pressed. It can suppress that a part wears. As a result, it is possible to suppress a decline in the function of reducing the rotational speed of the main shaft after the driving force is cut with respect to the main shaft.

  A vehicle according to a second aspect of the present invention is a vehicle provided with the above-described speed change mechanism. If comprised in this way, the vehicle which can suppress that the function which makes the rotation speed of a main axis | shaft small after the driving force is cut | disconnected with respect to a main axis | shaft will decline easily can be obtained.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
FIG. 1 is a side view showing the overall structure of a motorcycle (vehicle) equipped with a speed change mechanism according to a first embodiment of the present invention. 2 to 7 are views for explaining in detail the transmission and the internal structure of the motorcycle according to the first embodiment shown in FIG. In the first embodiment, a motorcycle will be described as an example of the vehicle of the present invention. In the figure, FWD indicates the front in the traveling direction of the motorcycle. First, the structure of the motorcycle 1 according to the first embodiment will be described with reference to FIGS.

  As the structure of the motorcycle 1 according to the first embodiment of the present invention, as shown in FIG. 1, the front end portion of the main frame 3 is connected to the head pipe 2. The main frame 3 is formed to extend downward in the rear side. The main frame 3 is connected to a seat rail 4 extending upward in the rear side. A handle 5 is attached above the head pipe 2. A holder 6 is attached to the handle 5. A clutch lever 7 is rotatably attached to the holder 6. The clutch lever 7 is disposed on the handle 5 on the arrow X2 direction side (see FIG. 2), and one side of an oil hose 9 (see FIG. 3) is connected to the clutch lever 7 via a master cylinder 8. Yes. In other words, the clutch lever 7 is operated by the driver holding and rotating the clutch lever 7 so that the master cylinder 8 is operated and the oil filled in the oil hose 9 moves to the other side of the oil hose 9. Is configured to do.

  A front fork 10 is attached to the lower side of the handle 5. A front wheel 11 is rotatably attached to a lower end portion of the front fork 10. A front disc rotor 12 is attached to the front wheel 11 so as to rotate together with the front wheel 11. A front caliper 13 is attached to the front fork 10 so as to sandwich the front disk rotor 12.

  A front end portion of the swing arm 15 is attached to the rear end portion of the main frame 3 via a pivot shaft 14. A rear wheel 16 is rotatably attached to the rear end portion of the swing arm 15. A rear disc rotor 17 is attached to the rear wheel 16 so as to rotate together with the rear wheel 16. A rear caliper 18 is attached to the swing arm 15 so as to sandwich the rear disc rotor 17. A fuel tank 19 is disposed above the main frame 3. An engine 20 is mounted on the lower side of the main frame 3. A muffler 21b is connected to the engine 20 via a chamber 21a. A seat 22 is disposed above the seat rail 4.

  As shown in FIG. 2, the engine 20 includes a crankcase portion 23, a cylinder portion 25 in which the piston 24 is disposed, a cylinder head portion 26 disposed above the cylinder portion 25, and a cylinder head cover portion 27. It is constituted by. Four cylinder portions 25 and four pistons 24 of the engine 20 are provided along the vehicle width direction of the motorcycle 1 (the X direction in FIG. 2). That is, the engine 20 is a four-cylinder engine. A combustion chamber 26a is provided in the lower part of the cylinder head portion 26, and a spark plug 28 is disposed in the upper part of the combustion chamber 26a. An intake valve 29 and an exhaust valve (not shown) are disposed above the combustion chamber 26a. The intake valve 29 and the exhaust valve (not shown) are respectively connected to the combustion chamber 26a by rotation of a cam 30 and a cam (not shown) arranged above the intake valve 29 and the exhaust valve (not shown). And can be opened and closed. The cam 30 and the cam (not shown) are provided on the cam shaft 31 and the cam shaft (not shown), respectively. A sprocket 31a is provided on one side of the camshaft 31, and a chain 32 is engaged with the sprocket 31a. The chain 32 is meshed with a sprocket 33 a provided on one side of the crankshaft 33.

  The crankshaft 33 is disposed inside the crankcase portion 23, and the piston 24 is connected via a connecting rod 34. That is, the crankshaft 33 is configured to rotate in a predetermined direction when the piston 24 slides repeatedly on the inner peripheral surface of the cylinder portion 25. A generator 35 is provided on the other side of the crankshaft 33. An upstream primary reduction gear 36 is attached to a portion closer to one side (arrow X1 direction side) than the center of the crankshaft 33 so as to rotate together with the crankshaft 33.

  Further, as shown in FIG. 3, the downstream primary reduction gear 38 of the clutch mechanism portion 37 is engaged with the upstream primary reduction gear 36. A housing clutch 39 is riveted to the downstream primary reduction gear 38, and the housing clutch 39 is configured to rotate together with the downstream primary reduction gear 38. A plurality of friction plates 40 are arranged in the housing clutch 39 so as to rotate together with the housing clutch 39. A plurality of clutch plates 41 are disposed between the plurality of friction plates 40, respectively. The plurality of clutch plates 41 are arranged on the housing clutch 39 so as to rotate together with the boss clutch 42 arranged inside the housing clutch 39. In addition, a pressure plate 43 is disposed outside the housing clutch 39 in the vehicle width direction (arrow X1 direction side). The pressure plate 43 is provided to press the plurality of friction plates 40 and the plurality of clutch plates 41 in the center direction (arrow X2 direction side) in the vehicle width direction. That is, the pressure plate 43 has a function of generating frictional force between the plurality of friction plates 40 and the plurality of clutch plates 41 by pressing the plurality of friction plates 40 and the plurality of clutch plates 41 that are alternately arranged. Have

  Further, the boss clutch 42 is integrally formed with a protrusion 42a that protrudes outward in the vehicle width direction. A washer 44 and a bolt 45 are screwed into the protruding portion 42a, and the diameter of the outer peripheral portion of the washer 44 is larger than the diameter of the outer peripheral portion of the portion where the washer 44 of the protruding portion 42a is attached. It is configured. A leaf spring 46 is disposed between the surface of the washer 44 on the center side in the vehicle width direction (arrow X2 direction side) and the surface of the pressure plate 43 on the outer side in the vehicle width direction (arrow X1 direction side). ing. The leaf spring 46 is configured to bias the pressure plate 43 toward the center in the vehicle width direction (arrow X2 direction side) by being supported by the washer 44. The clutch mechanism 37 is mainly composed of the downstream primary reduction gear 38, the housing clutch 39, the friction plate 40, the clutch plate 41, the boss clutch 42, the pressure plate 43, and the like. That is, the clutch mechanism unit 37 according to the first embodiment is a wet multi-plate clutch.

  Further, one side of the main shaft 47 is attached to the boss clutch 42. The main shaft 47 is rotatably supported by a bearing 48 and a bearing 49 attached to the crankcase portion 23. The main shaft 47 and the boss clutch 42 are configured to rotate integrally. Thereby, when the pressure plate 43 presses the plurality of friction plates 40 and the plurality of clutch plates 41 in the center direction (arrow X2 direction side) in the vehicle width direction, the driving force of the upstream primary reduction gear 36 is The transmission is transmitted to the main shaft 47 through the downstream primary reduction gear 38, the housing clutch 39, the friction plate 40, the clutch plate 41, and the boss clutch 42. On the other hand, when the pressure plate 43 does not press the plurality of friction plates 40 and the plurality of clutch plates 41 in the center direction (arrow X2 direction side) in the vehicle width direction, the frictional force between the friction plates 40 and the clutch plates 41. Therefore, the driving force of the upstream primary reduction gear 36 is difficult to be transmitted to the main shaft 47.

  The main shaft 47 is formed with a through hole 47a along the axial direction of the shaft center. The through hole 47a is an example of the “hole” in the present invention. Further, the main shaft 47 is formed with a plurality of oil holes 47 b so as to penetrate from the through hole 47 a to the outer peripheral surface of the main shaft 47. As a result, oil that flows into the through hole 47a from the other side of the main shaft 47 can be supplied to the transmission 77, which will be described later, through the plurality of oil holes 47b. In addition, an aluminum rod member 50 is inserted into the through hole 47a of the main shaft 47 with a predetermined distance from the inner peripheral surface of the through hole 47a. The rod member 50 is an example of the “rod portion” and the “second rod portion” in the present invention. A plurality of intermediate members 51 and a pressing member 52 are disposed on the pressure member 43 side (arrow X1 direction side) of the rod member 50. The pressing member 52 is configured to be movable outward in the vehicle width direction (arrow X1 direction side). As a result, the pressing member 52 moves the pressure plate 43 outward in the vehicle width direction against the urging force of the leaf spring 46 when the pressing member 52 is moved outward in the vehicle width direction (arrow X1 direction side). It is comprised so that it may move to (arrow X1 direction side). Specifically, the pressing member 52 includes a shaft insertion portion 52a and a bearing support portion 52b. The shaft insertion portion 52a is inserted into the through hole 47a so as to block one side of the through hole 47a of the main shaft 47. Further, the bearing support portion 52 b is rotatably supported by a bearing 53 inserted into the pressure plate 43. The pressure plate 43 is pressed outwardly in the vehicle width direction (arrow X1 direction side) by the pressing member 52 to the rod member 50 via the intermediate member 51, so that the pressure plate 43 is outward in the vehicle width direction (arrow X1 direction side). Configured to be moved to.

  Here, in the first embodiment, an iron push rod 54 having higher hardness than the aluminum rod member 50 is attached to the opposite side (arrow X2 direction side) of the rod member 50 to the pressure plate 43 side. Yes. The push rod 54 is an example of the “rod portion” and the “first rod portion” in the present invention. Further, the rod member 50 and the push rod 54 constitute a “rod portion” of the present invention. As shown in FIGS. 3 and 4, the push rod 54 includes a piston insertion portion 54a to be inserted into a piston 61 (see FIG. 3) described later, and a main body portion extending in the vehicle width direction (arrow X1 direction and arrow X2 direction). 54b, a fitting convex portion 54c (see FIG. 3) to be fitted into the push rod insertion hole 50a (see FIG. 3) of the rod member 50, and a body portion 54b, which are integrally provided, and are axially extended from the body portion 54b. And a flange portion 54d projecting in a direction intersecting with. The flange portion 54d is an example of the “pressing portion” in the present invention. Further, as shown in FIG. 3, the push rod 54 is configured to be movable to the pressure plate 43 side (arrow X1 direction side) by a piston 61, which will be described later, and to be able to press the one end surface 47c of the main shaft 47. It is configured. The push rod 54 moves the rod member 50 to the pressure plate 43 side (arrow X1 direction side) and moves the pressure plate 43 outside in the vehicle width direction (arrow X1 direction side) via the intermediate member 51 and the pressing member 52. ).

  Further, in the first embodiment, as shown in FIG. 4, the portion that presses the main shaft 47 of the flange portion 54 d of the push rod 54 protrudes toward the one end surface 47 c side (arrow X <b> 1 direction side) of the main shaft 47. A convex portion 54e having a semicircular cross section is provided. Specifically, the convex portion 54e is formed along the outer periphery of the flange portion 54d, and is configured to be pressed in a state of being in linear contact with the one end surface 47c of the main shaft 47. Further, as shown in FIGS. 4 and 5, a plurality of oil inflow holes 54f are formed on the surface of the flange portion 54d. In the plurality of oil inflow holes 54f, the flange portion 54d presses the one end surface 47c of the main shaft 47 (see FIG. 4), thereby closing the through hole 47a (see FIG. 4) of the main shaft 47. Even in this state, the oil can flow into the through hole 47a (see FIG. 4).

  Further, the main body 54b of the push rod 54 is inserted into the opening 55a of the rod holder 55 as shown in FIG. The rod holder 55 is inserted into the holder mounting hole 23 a of the crankcase part 23. An O-ring 56 is disposed between the outer peripheral surface of the rod holder 55 and the holder mounting hole 23a. In this O-ring 56, the oil in the arrow X1 direction side from the holder mounting hole 23a of the crankcase portion 23 is positioned in the arrow X2 direction side from the rod holder 55 between the outer peripheral surface of the rod holder 55 and the holder mounting hole 23a. It has a function to suppress inflow. An oil seal 57 is disposed on the side of the opening 55a of the rod holder 55 in the direction of the arrow X2. In the oil seal 57, the oil in the direction of the arrow X 1 with respect to the rod holder 55 flows out from between the outer peripheral surface of the main body 54 b of the push rod 54 and the opening 55 a of the rod holder 55. It has a function of suppressing inflow to the arrow X2 direction side.

  A cylinder member 58 is provided on the side of the rod holder 55 in the direction of the arrow X2. The cylinder member 58 is attached so as to cover the portion on the arrow X2 direction side of the portion where the main shaft 47 of the crankcase portion 23 is disposed. That is, the cylinder member 58 is disposed on the opposite side of the push rod 54 to the rod member 50 side (arrow X2 direction side). The cylinder member 58 is firmly attached to the crankcase portion 23 by a screw member 59. Further, a leaf spring 60 is disposed at the end of the cylinder member 58 in the arrow X1 direction, and the leaf spring 60 supports a portion of the rod holder 55 in the arrow X2 direction. Thereby, even when the rod holder 55 is pressed to the arrow X2 direction side by the oil inside the crankcase part 23, it is possible to suppress the rod holder 55 from falling off in the arrow X2 direction.

  A piston 61 is slidably disposed inside the cylinder member 58 with respect to the inner peripheral surface of the cylinder member 58, and a piston insertion portion 54 a of a push rod 54 is attached to the piston 61. . In addition, a return spring 62 is arranged on the opposite side (arrow X2 direction side) of the piston 61 to the push rod 54 side, and the return spring 62 constantly urges the piston 61 toward the push rod 54 side. ing.

  Further, as shown in FIG. 3, the other side of the oil hose 9 is connected to the side (arrow X2 direction side) where the return spring 62 of the cylinder member 58 is disposed. That is, the side of the cylinder member 58 where the return spring 62 is disposed (the arrow X2 direction side) is filled with oil that can circulate with the master cylinder 8. Thus, when the driver holds the clutch lever 7, the oil in the master cylinder 8 flows from the master cylinder 8 into the cylinder member 58 through the oil hose 9, and the piston 61 is pushed. It is moved to the rod 54 side (arrow X1 direction side). As a result, the push rod 54 is moved to the pressure plate 43 side (arrow X1 direction side), so that the pressure plate 43 is moved to the outside in the vehicle width direction (arrow) via the rod member 50, the intermediate member 51, and the pressing member 52. X1 direction side).

  Further, in the first embodiment, as shown in FIG. 7, when the clutch lever 7 is gripped by the driver with the first grip amount A that is in a substantially full stroke state, the flange portion 54 d is The one end surface 47c of the shaft 47 is configured to be pressed. As shown in FIG. 3, when the clutch lever 7 is gripped by the driver with the second gripping amount B that is in a stroke less than the first gripping amount A, the flange portion 54 d is connected to the main shaft. It is comprised so that the one end surface 47c of 47 may not be pressed. That is, even when the clutch mechanism portion 37 is operated so as to cut the driving force transmitted from the crankshaft 33 to the main shaft 47 when the driver grips the clutch lever 7, the clutch lever 7 is moved to the first position. It is possible to divide into either the grip amount A or the second grip amount B. As a result, when it is desired to reduce the rotational speed of the main shaft 47 rotated by the inertial force, the clutch lever 7 is gripped to the first grip amount A. Further, when the rotational speed of the main shaft 47 that rotates due to the inertia force does not have to be reduced, the clutch lever 7 is gripped by the second grip amount B.

  Here, in general, the driver often holds the clutch lever 7 deeply to the first grip amount A when the vehicle stops. Further, the driver often grips the clutch lever 7 to the second grip amount B that is smaller than the first grip amount A during traveling. That is, the motorcycle 1 according to the first embodiment suppresses the main shaft 47 from rotating due to the inertial force of the main shaft 47 when the driver stops the clutch lever 7 to the first gripping amount A. It is configured. Further, the motorcycle 1 according to the first embodiment maintains the state in which the main shaft 47 is rotated by the inertia force of the main shaft 47 when the driver holds the clutch lever 7 with the second grip amount B. It is configured.

  The main shaft 47 is provided with an upstream first speed gear 63, an upstream second speed gear 64, an upstream third speed gear 65, an upstream fourth speed gear 66, and an upstream fifth speed gear 67. Specifically, the upstream first speed gear 63 is formed integrally with the main shaft 47 on the clutch mechanism portion 37 side (arrow X1 direction side) and is formed to be rotatable together with the main shaft 47. The upstream first speed gear 63 is an example of the “first gear” in the present invention. In addition, an upstream fourth speed gear 66 is disposed to be idle with respect to the main shaft 47 next to the upstream first speed gear 63 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side). . A plurality of recesses 66a are formed on the upstream side fourth gear 66 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side). Further, next to the upstream side fourth speed gear 66 on the side opposite to the clutch mechanism portion 37 side (arrow X2 direction side), the upstream third speed gear 65 is in the axial direction of the main shaft 47 (arrow X1 direction and arrow X2). (Moving direction). A plurality of convex portions 65a are formed on the clutch mechanism 37 side (arrow X1 direction side) of the upstream third speed gear 65. The plurality of convex portions 65a are configured to be able to engage with the plurality of concave portions 66a of the upstream side fourth speed gear 66, and the upstream side third speed gear 65 slides to the clutch mechanism portion 37 side (arrow X1 direction side). When doing so, the convex portion 65a and the concave portion 66a are engaged with each other. In this case, the upstream fourth speed gear 66 is prevented from idling by the upstream third speed gear 65.

  A plurality of recesses 65b are formed on the upstream side third speed gear 65 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side). Further, an upstream fifth gear 67 is disposed so as to be idle with respect to the main shaft 47 next to the upstream third gear 65 on the opposite side (arrow X2 direction side) to the clutch mechanism 37 side. . A plurality of convex portions 67a are formed on the clutch mechanism portion 37 side (arrow X1 direction side) of the upstream fifth gear 67. The plurality of convex portions 67a are configured to be able to engage with the plurality of concave portions 65b of the upstream side third speed gear 65, and the upstream side third speed gear 65 is on the opposite side to the clutch mechanism portion 37 side (in the direction of arrow X2). When sliding to the side), the convex portion 67a and the concave portion 65b are engaged with each other. In this case, the upstream fifth gear 67 is prevented from idling by the upstream third gear 65.

  Further, the upstream second speed gear 64 is provided on the side opposite to the clutch mechanism 37 side of the main shaft 47 (arrow X2 direction side). The upstream second speed gear 64 is fixed to the main shaft 47, unlike the upstream third speed gear 65, the upstream fourth speed gear 66 and the upstream fifth speed gear 67.

  Further, an upstream first speed gear 63, an upstream second speed gear 64, an upstream third speed gear 65, an upstream fourth speed gear 66, and an upstream fifth speed gear 67 include a downstream first speed gear 68 and a downstream side, respectively. A second gear 69, a downstream third gear 70, a downstream fourth gear 71, and a downstream fifth gear 72 are meshed. The downstream first speed gear 68, the downstream second speed gear 69, the downstream third speed gear 70, the downstream side fourth speed gear 71, and the downstream side fifth speed gear 72 are provided on the drive shaft 73, respectively. Further, an intermediate gear 74 for transmitting the driving force of the drive shaft 73 to the rear wheel 16 (see FIG. 1) is fixed to the clutch mechanism portion 37 side (arrow X1 direction side) of the drive shaft 73. The driving force transmitted to the intermediate gear 74 is transmitted to the rear wheel 16 via a gear mechanism (not shown). The drive shaft 73 is rotatably supported by bearings 75 and 76 arranged in the crankcase portion 23.

  The downstream first speed gear 68 is provided on the side opposite to the clutch mechanism 37 side of the intermediate gear 74 of the drive shaft 73 (arrow X2 direction side). The downstream first speed gear 68 is an example of the “second gear” in the present invention. The downstream first speed gear 68 is disposed so as to be idle with respect to the drive shaft 73, and on the side opposite to the clutch mechanism portion 37 side of the downstream first speed gear 68 (arrow X2 direction side) A plurality of recesses 68a are formed. Further, next to the downstream side first gear 68 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side), the downstream fourth speed gear 71 is in the axial direction of the drive shaft 73 (arrow X1 direction and arrow X2). It is arranged to be movable in the direction). A plurality of convex portions 71a are formed on the clutch mechanism portion 37 side (arrow X1 direction side) of the downstream fourth speed gear 71. The plurality of convex portions 71a are configured to be engageable with the plurality of concave portions 68a of the downstream first speed gear 68, and the downstream fourth speed gear 71 slides to the clutch mechanism portion 37 side (arrow X1 direction side). When doing so, the convex portion 71a and the concave portion 68a are engaged with each other. In this case, the downstream first speed gear 68 is prevented from idling by the downstream fourth speed gear 71.

  Further, the downstream side third speed gear 70 is disposed next to the side opposite to the clutch mechanism portion 37 side (arrow X2 direction side) of the downstream side fourth speed gear 71 so as to be idle with respect to the drive shaft 73. . A plurality of recesses 70a are formed on the downstream side third speed gear 70 on the side opposite to the clutch mechanism portion 37 side (arrow X2 direction side). Further, next to the downstream side third speed gear 70 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side), the downstream fifth speed gear 72 is in the axial direction of the drive shaft 73 (arrow X1 direction and arrow X2). It is arranged to be movable in the direction). A plurality of convex portions 72a are formed on the clutch mechanism portion 37 side (arrow X1 direction side) of the downstream fifth gear 72 and the direction opposite to the clutch mechanism portion 37 side of the downstream fifth gear 72 is formed. A plurality of convex portions 72b are formed on the side (arrow X2 direction side). The plurality of convex portions 72a are configured to be engageable with the plurality of concave portions 70a of the downstream side third speed gear 70, and when the downstream side fifth speed gear 72 slides to the clutch mechanism portion 37 side, the convex portions are formed. 72a and the recess 70a are engaged with each other. In this case, the downstream third speed gear 70 is prevented from idling by the downstream fifth speed gear 72.

  In addition, a downstream second speed gear 69 is disposed so as to be idle with respect to the drive shaft 73 next to the downstream fifth speed gear 72 on the side opposite to the clutch mechanism 37 side (arrow X2 direction side). . A plurality of recesses 69 a are formed on the downstream second gear 69 on the clutch mechanism 37 side (arrow X1 direction side). The plurality of concave portions 69a are configured to be able to engage with the plurality of convex portions 72b of the downstream side fifth speed gear 72, and the downstream side fifth speed gear 72 is opposite to the clutch mechanism portion 37 side (in the direction of the arrow X2). The concave portion 69a and the convex portion 72b are engaged with each other when slid to the side. In this case, the downstream second gear 69 is prevented from idling by the downstream fifth gear 72. The clutch mechanism 37, the main shaft 47, the upstream first gear 63, the upstream second gear 64, the upstream third gear 65, the upstream fourth gear 66, the upstream fifth gear 67, and the downstream first gear. A transmission 77 is configured by the gear 68, the downstream second gear 69, the downstream third gear 70, the downstream fourth gear 71, the downstream fifth gear 72 and the drive shaft 73. The transmission 77 is an example of the “transmission mechanism” in the present invention.

  FIG. 8 is a view for explaining an operation when the flange portion of the push rod presses one end surface of the main shaft when the motorcycle according to the first embodiment is started from a stopped state. Next, referring to FIGS. 3, 7, and 8, when the motorcycle according to the first embodiment starts from a stopped state, the operation when the flange portion of the push rod presses one end surface of the main shaft is described. explain.

  First, the clutch mechanism portion 37 is operated so as to cut the driving force transmitted from the crankshaft 33 to the main shaft 47 from the neutral state shown in FIG. 3 and the clutch mechanism portion 37 being connected. Let Specifically, when the driver rotates the clutch lever 7 to the first grip amount A, the oil inside the master cylinder 8 flows into the cylinder member 58 via the oil hose 9. As a result, as shown in FIG. 8, the piston 61 is moved to the clutch mechanism 37 side (arrow X1 direction side) by the pressure of the oil flowing into the cylinder member 58. As the piston 61 is moved toward the clutch mechanism 37 (arrow X1 direction), the push rod 54 is moved toward the clutch mechanism 37 (arrow X1 direction). As a result, the pressure plate 43 of the clutch mechanism portion 37 is moved to the arrow X1 direction side via the rod member 50, the intermediate member 51, and the pressing member 52. Therefore, the plurality of friction plates 40 and the plurality of clutches pressed against each other. The load between the plates 41 is reduced. As a result, the driving force transmitted from the crankshaft 33 to the main shaft 47 is cut off.

  Here, immediately after the driving force transmitted from the crankshaft 33 to the main shaft 47 is cut off, the main shaft 47 does not move even though the driving force transmitted from the crankshaft 33 to the main shaft 47 is cut off. , Keeps rotating due to inertial force. On the other hand, the downstream side fourth speed gear 71 meshed with the upstream side fourth speed gear 66 that idles with respect to the main shaft 47 does not substantially rotate. At this time, the upstream first speed gear 63 provided on the main shaft 47 so as to rotate with the main shaft 47 continues to rotate with the main shaft 47. Further, the downstream first speed gear 68 that is meshed with the upstream first speed gear 63 and capable of idling with respect to the drive shaft 73 is in a neutral state, and therefore is idle with respect to the drive shaft 73. Yes.

  At this time, the driver rotates the clutch lever 7 to the first gripping amount A, whereby the flange portion 54 d of the push rod 54 is pressed against the one end surface 47 c of the main shaft 47. At this time, since the driving force transmitted from the crankshaft 33 to the main shaft 47 is cut, the number of rotations of the main shaft 47 is smaller than when the flange portion 54d is not pressed against the one end surface 47c of the main shaft 47. Becomes smaller. As a result, the rotational speed of the downstream first speed gear 68 is also reduced, so that the rotational speed of the downstream first speed gear 68 approaches the rotational speed of the downstream fourth speed gear 71 that is not substantially rotating.

  And when a driver | operator operates the shift lever which is not shown in figure, the downstream 4th-speed gear 71 is moved to the arrow X1 direction. Then, the convex portion 71 a of the downstream side fourth speed gear 71 is engaged with the concave portion 68 a of the downstream side first speed gear 68. At this time, since the rotation speed of the downstream first speed gear 68 approaches the rotation speed of the downstream fourth speed gear 71 that is not substantially rotated, the convex portion 71a of the downstream fourth speed gear 71 and the downstream side The first gear 68 is smoothly engaged with the recess 68a. Accordingly, the downstream first speed gear 68 that idles with respect to the drive shaft 73 is rotated together with the downstream fourth speed gear 71 that rotates together with the drive shaft 73. That is, the downstream first speed gear 68 is rotatably connected with the drive shaft 73 and the driving force of the main shaft 47 is transmitted to the drive shaft 73.

  Thereafter, when the driver makes the clutch lever 7 shallow, the pressure plate 43 in which the leaf spring 46 is biased in the arrow X2 direction is moved in the arrow X2 direction. Accordingly, since the driving force of the crankshaft 33 is transmitted to the main shaft 47, the stopped motorcycle 1 can be started smoothly.

  In the first embodiment, as described above, when the clutch mechanism portion 37 is actuated on the push rod 54 so as to cut the driving force transmitted from the crankshaft 33 to the main shaft 47, the main shaft 47 is pressed. The flange part 54d comprised so that it may be provided is provided. As a result, the flange portion 54d presses the main shaft 47 only when the clutch mechanism portion 37 that is normally operated when performing a shift operation is operated, so the flange portion 54d always presses the main shaft 47. Compared to the case, it is possible to suppress the rotation loss of the main shaft 47 from increasing. Further, since the main shaft 47 is pressed after the driving force transmitted from the crankshaft 33 to the main shaft 47 is cut, the main portion of the flange portion 54d is compared with the case where the flange portion 54d constantly presses the main shaft 47. It can suppress that the part (convex part 54e) currently pressed on the axis | shaft 47 wears. As a result, it is possible to suppress a decline in the function of reducing the rotational speed of the main shaft 47 after the driving force is cut with respect to the main shaft 47.

  Further, in the first embodiment, as described above, the flange portion 54d is configured to press the main shaft 47 when the clutch lever 7 is gripped by the first grip amount A that is in a full stroke state. is doing. Thus, normally, when the driver stops the clutch lever 7 deeply to the first gripping amount A, the main shaft 47 is rotated by the inertial force of the main shaft 47 by pressing the flange portion 54d against the main shaft 47. Can be suppressed.

  In the first embodiment, as described above, when the clutch lever 7 is gripped with the second grip amount B smaller than the first grip amount A, the flange portion 54d is not pressed against the main shaft 47. It is configured as follows. Accordingly, it is possible to suppress the flange portion 54d from pressing the main shaft 47 when the driver normally holds the clutch lever 7 shallowly to the second grip amount B. As a result, it is possible to suppress a decrease in the rotational speed of the main shaft 47 during traveling. Further, since the flange portion 54d does not press the main shaft 47 during traveling, it is possible to suppress an increase in rotational loss of the main shaft 47.

  Further, in the first embodiment, as described above, when the motorcycle 1 is stopped, the main shaft 47 is rotating, while the downstream first speed gear 68 idles with respect to the drive shaft 73, so that the drive shaft When shifting from the neutral state where 73 is not rotating to the first speed, the flange portion 54d of the push rod 54 is configured to press the main shaft 47 when the clutch lever 7 is gripped by the first grip amount A. is doing. Further, the rotational speed of the downstream first speed gear 68 is reduced by reducing the rotational speed of the main shaft 47. Accordingly, when the convex portion 71a of the downstream fourth speed gear 71 that does not rotate with the drive shaft 73 at the time of stopping is engaged with the concave portion 68a of the downstream first speed gear 68, the rotation of the downstream first speed gear 68 is increased. The number can be reduced. As a result, the convex portion 71a and the concave portion 68a can be smoothly engaged without being pushed by the concave portion 68a that rotates together with the downstream first speed gear 68. Thereby, the operation of shifting from the neutral to the first speed can be smoothly performed when stopped.

  Further, in the first embodiment, as described above, the convex portion 54e having a semicircular cross section that protrudes toward the one end face 47c of the main shaft 47 is formed in the portion that presses the main shaft 47 of the flange portion 54d. ing. Thereby, since the convex part 54e can be pressed with respect to the one end surface 47c of the main shaft 47, the flange part 54d can be pressed against the one end surface 47c of the main shaft 47 in a stable state.

  In the first embodiment, as described above, one end surface 47c of the main shaft 47 is pressed against the flange portion 54d of the push rod 54, so that one side of the through hole 47a of the main shaft 47 is covered with the flange portion 54d. Even in such a case, an oil inflow hole portion 54f that allows oil to flow through the through hole 47a of the main shaft 47 is provided. Thereby, oil can be easily circulated through the through hole 47a of the main shaft 47.

  In the first embodiment, as described above, the push rod 54 is made of iron having higher hardness than the rod member 50 made of aluminum. Thereby, it is possible to suppress wear of the flange portion 54d provided on the push rod 54 that contacts the one end surface 47c of the main shaft 47.

  In the first embodiment, as described above, the flange portion 54d is moved along the one end surface 47c of the main shaft 47 as the push rod 54 is moved to the clutch mechanism portion 37 side (arrow X1 direction side). It is comprised so that it may press. Thereby, it is possible to suppress the main shaft 47 from rotating due to the inertial force of the main shaft 47 as the driving force transmitted from the crank shaft 33 to the main shaft 47 is cut in the clutch mechanism portion 37. .

  In the first embodiment, as described above, the flange portion 54d of the push rod 54 is configured to press the one end surface 47c of the main shaft 47 in an annular shape. Thereby, the one end surface 47c of the main shaft 47 can be easily pressed in a stable state.

(Second Embodiment)
9 to 13 are views for explaining in detail the speed change mechanism and the internal structure thereof according to the second embodiment of the present invention. Hereinafter, the structure of the transmission according to the second embodiment of the present invention will be described in detail with reference to FIGS. In the second embodiment, unlike the first embodiment, an example in which the push rod 81 is restricted from rotating in the rotation direction of the main shaft 47 will be described.

  In the second embodiment, as shown in FIG. 9, the body 81 b of the push rod 81 is inserted into the opening 82 a of the rod holder 82. Further, the push rod 81 is inserted into the opening 82a in a state where the push rod 81 is restricted from rotating with respect to the rod holder 82. Specifically, as shown in FIGS. 10 and 11, an iron pin 83 is press-fitted into the main body portion 81 b of the push rod 81. The pin 83 is disposed so as to penetrate the center in the axial direction of the main body 81 b of the push rod 81. The pin 83 is an example of the “locking member” and “first pin” in the present invention. Further, as shown in FIGS. 9 and 12, a pair of groove portions 82 b are formed on the inner peripheral surface of the opening portion 82 a of the rod holder 82, so that both end portions of the pin 83 can engage with each other. The pin 83 press-fitted into the push rod 81 is engaged with the groove 82 b of the rod holder 82. That is, the pin 83 has a function of restricting the push rod 81 from rotating with respect to the rod holder 82 by being engaged with the groove 82b. The groove 82b is an example of the “first groove” in the present invention.

  In the second embodiment, the rod holder 82 is inserted into the holder mounting hole 84 a of the crankcase part 84. Further, the rod holder 82 is inserted into the holder mounting hole 84a in a state where rotation with respect to the crankcase portion 84 is restricted. Specifically, as shown in FIGS. 9 and 12, two iron pins 85 are press-fitted into the outer peripheral surface of the rod holder 82. As shown in FIG. 13, these two pins 85 are press-fitted substantially perpendicularly to the outer peripheral surface of the rod holder 82 and at intervals of 180 degrees. The pin 85 is an example of the “locking member” and “second pin” in the present invention. Further, on the inner peripheral surface of the holder mounting hole 84a of the crankcase portion 84, groove portions 84b that can engage with two iron pins 85 are formed. The pin 85 press-fitted into the rod holder 82 is engaged with the groove portion 84 b of the crankcase portion 84. That is, the pin 85 has a function of restricting the rod holder 82 from rotating with respect to the crankcase portion 84 by being engaged with the groove portion 84b. The groove 84b is an example of the “second groove” in the present invention.

  As described above, in the second embodiment, when the push rod 81 presses the main shaft 47 by the pins 83 and 85, it is possible to restrict the push rod 81 from rotating together with the main shaft 47. That is, the push rod 81 is restricted from rotating with respect to the rod holder 82, and the rod holder 82 is restricted from rotating with respect to the crankcase portion 84. When the 47 is pressed, the push rod 81 can be restricted from rotating together with the main shaft 47.

  Since the other structure of the second embodiment is the same as that of the first embodiment, the description thereof is omitted.

  The operation of the second embodiment is the same as that of the first embodiment, and a description thereof will be omitted.

  In the second embodiment, as described above, the push rod 81 can be moved in the axial direction (arrow X1 direction and arrow X2 direction) of the main shaft 47 while being restricted from rotating in the rotation direction of the main shaft 47. It is configured. Accordingly, even when the push rod 81 presses the one end surface 47c of the main shaft 47 while the main shaft 47 is rotating, the push rod 81 can be restricted from rotating together with the main shaft 47.

  In the second embodiment, as described above, the push rod 81 is restricted from rotating relative to the rod holder 82, and the rod holder 82 is restricted from rotating relative to the crankcase portion 84. Yes. Accordingly, the push rod 81 can be easily restricted from rotating with respect to the crankcase portion 84, so that the push rod 81 can be easily restricted from rotating together with the main shaft 47.

  In the second embodiment, as described above, by providing the pins 83 and 85 that restrict the rotation of the push rod 81 together with the main shaft 47 when the push rod 81 presses the main shaft 47, the pin 83 and 85, the push rod 81 can be prevented from rotating together with the main shaft 47.

  In the second embodiment, as described above, the rod holder 82 is formed with the groove portion 82b in which the pin 83 can be engaged, and the crankcase portion 84 is formed with the groove portion 84b in which the pin 85 can be engaged. ing. Thus, since the pins 83 and 85 are stably engaged by the grooves 82b and 84b, the push rod 81 and the rod holder 82 are prevented from rotating in the rotational direction of the main shaft 47 in a stable state. Can do.

  The remaining effects of the second embodiment are similar to those of the aforementioned first embodiment.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the above-described embodiment, a motorcycle is shown as an example of a vehicle. However, the present invention is not limited to this, and other vehicles such as an automobile, a tricycle, and an ATV (All Terrain Vehicle) may be used. It can also be applied to vehicles.

  Moreover, in the said embodiment, although the flange part of the push rod pressed the one end surface of the main shaft, the example which reduces the rotation speed of the rotating main shaft was shown, but this invention is not limited to this, for example, The number of rotations of the main shaft may be reduced by providing a pressing portion that presses a portion other than the one end surface of the main shaft, such as a chamfered portion of the inner diameter of the through hole provided on the push rod side of the main shaft. Good.

  Moreover, in the said embodiment, although the example which formed the push rod and the rod member separately by the material which has different hardness was shown, this invention is not restricted to this, A push rod and a rod member are made of material with high hardness. You may form integrally.

  Further, in the above-described embodiment, when the motorcycle is started, the convex portion of the downstream fourth gear is engaged with the concave portion of the downstream first gear so that the downstream first gear is idled with respect to the drive shaft. However, the present invention is not limited to this, and the downstream first speed gear is prevented from idling with respect to the drive shaft by a gear other than the downstream fourth speed gear. It may be configured.

  Further, in the above-described embodiment, an example in which the downstream first speed gear rotates idly with respect to the drive shaft and the upstream first speed gear rotates with the main shaft is shown, but the present invention is not limited to this. The downstream first gear may be configured to rotate with the drive shaft, and the upstream first gear may be configured to idle with respect to the main shaft.

  Moreover, in the said embodiment, although the example which comprised the push rod with iron was shown, this invention is not restricted to this, As long as a push rod is a material whose hardness is higher than a rod member, it uses materials other than iron, such as ceramics. You may make it comprise.

  In the above embodiment, an example is shown in which two pins are press-fitted into the rod holder at intervals of 180 degrees, and two groove portions that can be engaged with the two pins are formed in the holder mounting holes of the crankcase portion. The present invention is not limited to this, and the three pins may be press-fitted into the rod holder at intervals of 120 degrees, and the three groove portions that can be engaged with the three pins may be formed in the holder mounting holes of the crankcase portion. Then, the four pins may be press-fitted into the rod holder at intervals of 90 degrees, and four groove portions that can be engaged with the four pins may be formed in the holder mounting holes of the crankcase portion.

1 is a side view showing an overall structure of a motorcycle on which a transmission according to a first embodiment of the present invention is mounted. FIG. 2 is a cross-sectional view for explaining the structure of the engine of the motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted. FIG. 2 is a cross-sectional view for explaining the structure of the transmission of the motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted. FIG. 2 is a view for explaining the structure of a push rod of a motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted. It is the figure seen from the arrow P direction of FIG. FIG. 2 is a cross-sectional view for explaining the structure of a push rod and a vicinity of the motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted. FIG. 2 is a cross-sectional view for explaining the structure of the transmission of the motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted. FIG. 3 is a diagram for explaining an operation when the flange portion of the push rod presses one end surface of the main shaft when starting the motorcycle on which the transmission according to the first embodiment shown in FIG. 1 is mounted from a stopped state. is there. It is sectional drawing for demonstrating the structure of the push rod of the transmission by 2nd Embodiment of this invention, and its vicinity. It is a figure for demonstrating the structure of the push rod of the transmission by 2nd Embodiment of this invention. It is the figure seen from the arrow Q direction of FIG. It is a figure for demonstrating the structure of the rod holder of the transmission by 2nd Embodiment of this invention. It is a figure for demonstrating the structure of the part vicinity to which the rod holder of the crankcase of the transmission by 2nd Embodiment of this invention is attached.

Explanation of symbols

1 Motorcycle (vehicle)
7 Clutch levers 23 and 84 Crankcase part 33 Crankshaft 37 Clutch mechanism part 47 Main shaft 47a Through hole (hole part)
47c One end face 50 Rod member (rod part, second rod part)
54, 81 Push rod (rod part, first rod part)
54d Flange part (pressing part)
54e Convex portion 54f Oil inflow hole portion 55, 82 Rod holder 63 First speed gear on the upstream side (first gear)
68 Downstream 1st gear (2nd gear)
73 Drive shaft 77 Transmission (transmission mechanism)
82b Groove (first groove)
83 pins (locking member, first pin)
84b Groove (second groove)
85 pins (locking member, second pin)
A 1st grip amount B 2nd grip amount

Claims (16)

A crankshaft,
A main shaft that is rotated by transmitting a driving force of the crankshaft;
A clutch mechanism capable of disconnecting and connecting a driving force transmitted from the crankshaft to the main shaft;
A rod portion that is connected to the clutch mechanism portion and operates in the axial direction so as to disconnect and connect the driving force transmitted from the crankshaft to the main shaft;
The rod portion includes a pressing portion configured to press the main shaft when the clutch mechanism portion is operated so as to cut a driving force transmitted from the crankshaft to the main shaft. Transmission mechanism. A clutch lever configured to be operable to move the rod portion in the axial direction by being gripped by a user;
The speed change mechanism according to claim 1, wherein the pressing portion is configured to press the main shaft when the clutch lever is gripped by a first grip amount.   The speed change according to claim 2, wherein the pressing portion is configured not to press the main shaft when the clutch lever is gripped with a second grip amount smaller than the first grip amount. mechanism. A drive shaft capable of transmitting the rotation of the main shaft;
The main shaft includes a first gear that rotates together with the main shaft,
The drive shaft includes a second gear that meshes with the first gear of the main shaft and is configured to be idle with respect to the drive shaft,
The speed change mechanism according to claim 2, wherein the pressing portion of the rod portion is configured to decrease the rotation speed of the first gear by decreasing the rotation speed of the main shaft.   2. The speed change mechanism according to claim 1, wherein the pressing portion of the rod portion includes a flange portion that is provided integrally with the rod portion and protrudes from the rod portion in a direction intersecting the axial direction.   The convex part which has the semicircle cross section which protrudes in the one end surface side of the said main shaft is formed in the part which presses the said main axis | shaft of the flange part which comprises the said press part. Transmission mechanism.   The speed change mechanism according to claim 5, wherein the flange portion is configured to press one end surface of the main shaft. The main shaft includes a hole provided substantially along the center in the axial direction,
The flange portion that constitutes the pressing portion of the rod portion has a hole in the main shaft even when one end surface of the main shaft is pressed and one side of the hole portion of the main shaft is covered with the flange portion. The speed change mechanism according to claim 5, further comprising an oil inflow hole portion through which oil can flow. The rod part is constituted by a first rod part provided with the pressing part and a second rod part not provided with the pressing part,
The speed change mechanism according to claim 1, wherein the first rod portion is made of a material having a hardness higher than that of the second rod portion. The pressing portion of the rod portion is provided integrally with the rod portion, and includes a flange portion protruding in a direction intersecting the axial direction from the rod portion,
The rod portion is configured to be movable toward the clutch mechanism portion side,
The speed change mechanism according to claim 1, wherein the flange portion of the pressing portion is configured to press one end surface of the main shaft as the rod portion is moved to the clutch mechanism portion side. .   The speed change mechanism according to claim 10, wherein the flange portion constituting the pressing portion of the rod portion is configured to annularly press one end surface of the main shaft.   The speed change mechanism according to claim 1, wherein the rod portion is configured to be movable in the axial direction of the main shaft while being restricted from rotating in the rotational direction of the main shaft. A crankcase portion in which the main shaft is disposed;
A rod holder that is disposed in the crankcase portion and into which the rod portion can be inserted;
The rod portion is restricted from rotating with respect to the rod holder,
The transmission mechanism according to claim 12, wherein the rod holder is restricted from rotating with respect to the crankcase portion.   The transmission mechanism according to claim 13, further comprising a locking member that restricts the rod portion from rotating together with the main shaft when the rod portion presses the main shaft. The locking member includes a first pin that restricts rotation of the rod portion relative to the rod holder, and a second pin that restricts rotation of the rod holder relative to the crankcase portion,
The rod holder has a first groove portion with which the first pin can be engaged,
The speed change mechanism according to claim 14, wherein the crankcase portion is formed with a second groove portion with which the second pin can be engaged.   A vehicle provided with the speed change mechanism according to any one of claims 1 to 15.

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