JP2012159196A - Outboard motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an outboard motor including a clutch device that improves durability of an engaging convex part and an engaging concave part in engaging a forward gear or a backward gear with a dog gear or in transmitting drive power.SOLUTION: The outboard motor 10 includes a clutch device 25 including a pair of forward and backward gears 31 and 33 which are always driven in opposite directions by a drive shaft 21 driven by a drive part, and a dog gear 35 arranged round an output shaft 29, wherein a plurality of engaging convex parts 31a, 33a and engaging concave parts 36a which can be fitted to each other are provided, and wherein the dog gear is moved in one axial direction, and is thereby engaged with one of the forward and backward gears. The drive shaft includes a drive gear 23. The forward gear and the backward gear include input gears 31c, 33c always engaged with the drive gear. 7 to 10 engaging concave parts and 7 to 10 engaging convex parts are arranged radially inside the input gear in a circumferential direction.

Description

  The present invention relates to an outboard motor including a clutch device for transmitting a driving force from a drive shaft that is rotationally driven by a drive unit to an output shaft, and in particular, a forward gear and a reverse gear that are driven by the drive shaft, and an output shaft. It is related with the improvement of the meshing part with the side dog gear.

  Conventionally, as shown in FIG. 14, in an outboard motor, an engine as a drive unit (not shown) is mounted on an upper portion of a casing 61, and a drive shaft 62 driven by the engine is suspended, and a lower end portion of the drive shaft 62. A clutch device 64 connected to the drive gear 63 is disposed, and an output shaft 66 having a propeller 65 is connected to the clutch device 64.

  The clutch device 64 is rotatably disposed around the output shaft 66, and is always driven in the opposite direction by the drive gear 63 of the drive shaft 62, and the clutch device 64 around the output shaft 66. A dog gear 69 is provided between the forward gear 67 and the reverse gear 68 and is movable in the axial direction while being unable to rotate in the circumferential direction with respect to the output shaft 66.

  In this clutch device 64, when the dog gear 69 moves to either the forward gear 67 or the reverse gear 68, one of the forward gear 67 or the reverse gear 68 meshes with the dog gear 69, and the one gear 67, The driving force 68 is transmitted to the output shaft 66 so that the propeller 65 is rotated in the forward or backward direction.

  As shown in FIGS. 15 and 16, the clutch device 64 of such an outboard motor 60 is provided with meshing recesses 69 a on the opposite surfaces of the forward gear 67 and the reverse gear 68 on both sides of the dog gear 69. On the surface facing 67 and the meshing recess 69a of the reverse gear, meshing projections 67a and 68a are provided. In a state where the forward gear 67 or the reverse gear 68 is engaged, the engaging convex portions 67a and 68a are disposed in the engaging concave portion 69a, and the driving force of the engaging convex portions 67a and 68a is applied to the driving force transmission surface 69b of the engaging concave portion 69a. The transmission surfaces 67b and 68b are in contact with each other to transmit the driving force.

  As such an outboard motor clutch structure, for example, one described in Patent Document 1 below is known. Here, the noise of the drive system is reduced by making the circumferential lengths of the meshing projections 67a, 68a and the meshing recess 69a substantially the same.

JP 2005-48820 A

  However, in the conventional clutch structure, when the engine output is high, when the forward gear 67 or the reverse gear 68 and the dog gear 69 are meshed or when the driving force is transmitted in the meshed state, the meshing projections 67a and 68a mesh. There was a case where a part of the concave portion 69a was crushed, broken, or deformed.

  Accordingly, the present invention provides an outboard motor equipped with a clutch device that can improve the durability of the meshing convex portion and the meshing concave portion when meshing the forward gear or the reverse gear and the dog gear or transmitting the driving force. Is an issue.

  The invention according to claim 1, which solves the above problem, has a drive unit mounted on the upper part of the casing, and can rotate integrally with the drive shaft on the lower end side of the drive shaft driven by the drive unit. A drive gear disposed in the casing, a clutch device disposed at a lower portion of the casing and coupled to the drive gear, and an output shaft coupled to the clutch device and driving a propeller. Is arranged rotatably around the output shaft that drives the propeller, and is always driven in the opposite direction by the drive shaft driven by the drive unit, and a pair of forward gear and reverse gear, and the output shaft A dog gear disposed between the surrounding forward gear and the reverse gear, movable in the axial direction with respect to the output shaft and not rotatable in the circumferential direction, and the forward gear and the reverse gear; A plurality of meshing projections and meshing recesses that can be fitted to each other at meshing portions provided at a portion facing the gear and a portion facing the forward gear and the reverse gear of the dog gear, respectively. Is moved in one axial direction with respect to the output shaft, and the plurality of meshing recesses and the plurality of meshing projections are fitted, whereby the dog gear and one of the forward gear or the reverse gear And the output shaft is driven, the drive shaft rotates the drive gear fixed to the output shaft side, and the forward gear and the reverse gear are Input gears that are always meshed with the drive gear are provided, and the meshing convex portions and the meshing concave portions are in a range radially inward from the input gear, and each is 7 or more and 10 in the circumferential direction. Characterized in that it is lower disposed.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the meshing convex portion has a circumferential length smaller than the meshing concave portion by 1 to 12 degrees in terms of the axial center angle of the output shaft. It is formed as follows.

According to a third aspect of the present invention, in addition to the configuration according to the first or second aspect, in each of the meshing portions of the forward gear and the dog gear or in each of the meshing portions of the reverse gear and the dog gear, the driving is performed. The total area of the force transmission surfaces is 340 mm ² or more, respectively.

  According to a fourth aspect of the present invention, in addition to the configuration according to any one of the first to third aspects, the respective meshing portions of the forward gear and the dog gear or the respective meshes of the reverse gear and the dog gear. The outer edge of each driving force transmission surface is formed in a straight line along the direction orthogonal to the axial direction of the output shaft, and the total length of the outer edge of each meshing part is Each is 70 mm or more.

  According to a fifth aspect of the present invention, in addition to the configuration according to any one of the first to fourth aspects, the respective meshing portions of the forward gear and the dog gear or the respective meshes of the reverse gear and the dog gear. The portion is characterized in that a slope for guiding the other engaging convex portion to the engaging concave portion is formed at a top portion adjacent to at least one of the engaging concave portions.

  According to the first aspect of the present invention, in each meshing portion of the dog gear and each of the forward gear and the reverse gear facing each other, the meshing convex portion and the meshing concave portion are disposed radially inward from the input gear. The meshing convex portion and the meshing concave portion are provided in a limited space between the input gear and the output shaft. Therefore, although the size of the meshing projection and the meshing recess is remarkably limited, even if the size of the meshing projection and the meshing recess is limited in this way, there are 7 meshing projections and 7 meshing recesses in the circumferential direction. By providing 10 or less, the transmission torque is distributed to each of the driving force transmission surfaces of the meshing convex portion and the meshing concave portion that are opposed to each other in the circumferential direction at the time of meshing, and the durability of the meshing convex portion and the meshing concave portion is improved. Can do.

  According to the second aspect of the present invention, the meshing convex part is meshed with the meshing convex part by forming the length in the circumferential direction to be smaller than the meshing concave part by a predetermined range at the axial center angle of the output shaft. The concave portion can be easily engaged.

  According to the third aspect of the present invention, the total area of the driving force transmission surface is not less than a predetermined value at each meshing portion between the forward gear and the dog gear or each meshing portion between the reverse gear and the dog gear. Torque can be sufficiently dispersed, and durability of the meshing convex part and the meshing concave part can be improved.

  According to the fourth aspect of the present invention, in each meshing portion of the forward gear and the dog gear or each meshing portion of the reverse gear and the dog gear, the axially outer edge of each driving force transmission surface is the axis of the output shaft. Driven when meshing the forward gear or reverse gear with the dog gear because the total length of the outer edge of each meshing portion is not less than a predetermined value. It is possible to disperse the impact at the time of contact between the vicinity of the outer edges of the force transmission surface.

  According to the fifth aspect of the present invention, in each meshing portion between the forward gear and the dog gear or each meshing portion between the reverse gear and the dog gear, the other meshing convex portion is provided on the top adjacent to at least one of the meshing recesses. Since the slope that guides the meshing recess is formed, even if the pitch is small by providing 7 or more meshing projections and meshing recesses, when engaging the meshing recess and the meshing projection with different rotational speeds If the meshing projection is pressed against the top adjacent to the meshing recess, the meshing projection slides at the top and is guided by the slope, and can be easily meshed with the meshing recess.

1 is a side view of an outboard motor equipped with a clutch device according to an embodiment of the present invention. It is sectional drawing which shows the clutch apparatus of the outboard motor of embodiment of this invention. It is sectional drawing of the forward gear and reverse gear of the clutch apparatus of the embodiment. It is a front view of the forward gear and reverse gear of the clutch apparatus of the embodiment. It is sectional drawing which cut | disconnected AA of FIG. 4 of the embodiment along the circumferential direction. It is sectional drawing of the dog gear of the clutch apparatus of the embodiment. It is a top view of the dog gear of the clutch apparatus of the embodiment. It is a front view of the dog gear of the clutch apparatus of the embodiment. It is sectional drawing which cut | disconnected BB of FIG. 8 of the embodiment along the circumferential direction. It is a top view of the state which mounted | wore the output shaft with the dog gear of the clutch apparatus of the embodiment. It is CC sectional drawing of FIG. 2 of the embodiment. It is DD sectional drawing of FIG. 2 of the embodiment. It is sectional drawing for demonstrating meshing operation | movement with the meshing convex part of the forward gear of the clutch apparatus of the same embodiment, and a reverse gear, and the meshing recessed part of a dog gear. It is a side view of the lower part of the conventional outboard motor. It is a side view of the dog gear of the conventional clutch apparatus, and has shown the meshing state with the forward gear and the reverse gear. It is sectional drawing which cut | disconnected EE of FIG. 15 of the conventional clutch apparatus along the circumferential direction.

  Embodiments of the present invention will be described below.

  1 to 12 show this embodiment.

  In FIGS. 1 and 2, reference numeral 10 denotes an outboard motor. An engine as a drive unit (not shown) is covered with a cowling 16 and mounted on an upper portion of a casing 14 fixed to the hull 12. This engine has a maximum horsepower of 300 PS or more. A drive shaft 21 driven by the engine is suspended in the casing 14, and a drive gear 23 that can rotate integrally with the drive shaft 21 is provided on the lower end side of the drive shaft 21. A clutch device 25 connected to the drive gear 23 of the drive shaft 21 is disposed in the lower part of the casing 14, and an output shaft 29 having a propeller 27 is connected to the clutch device 25.

  The clutch device 25 is rotatably arranged around an output shaft 29, and is paired with a forward gear 31 and a reverse gear 33 that mesh with a drive gear 23 provided at a lower end portion of the drive shaft 21. A dog gear 35 that is connected to the output shaft 29 with the gear 33 and is selectively meshed with the forward gear 31 or the reverse gear 33 by being moved in the axial direction of the output shaft 29 is provided.

  As shown in FIGS. 3 to 5, the forward gear 31 and the reverse gear 33 have input gears 31 c and 33 c to which driving force is input from the driving gear 23 on the outer peripheral side of one side surface, and the input gears 31 c and 33 c. Further, meshing portions 31d and 33d that can mesh with the dog gear 35 are provided on the radially inner side. The forward gear 31 and the reverse gear 33 are rotatably held by bearings 26 fixed to the casing 14 without being joined to the output shaft 29 around the output shaft 29. The forward gear 31 and the reverse gear 33 are always meshed with the drive gear 23 of the drive shaft 21, and are always driven in opposite directions by the rotation of the drive shaft 21.

  As shown in FIGS. 6 to 9, the dog gear 35 is disposed around the output shaft 29 between the forward gear 31 and the reverse gear 33, and can be engaged with the forward gear 31 and the reverse gear 33 on both side surfaces. It has a substantially cylindrical shape having a meshing portion 35d, and spline teeth 35c are provided on the inner peripheral surface in the axial direction.

  In the dog gear 35, spline teeth 35 c provided in the axial direction of the dog gear 35 are coupled to spline teeth 29 a provided in the axial direction of the output shaft 29, and a fixing pin 34 of a switching mechanism 41 described later is provided in the output shaft 29. Is inserted into a long hole 29b formed in the axial direction of the shaft and a passage hole 35f of the dog gear 35, and is locked by a coil spring 28 from the periphery to be connected to the output shaft 29 so as to be movable in the axial direction. Yes.

  The dog gear 35 is coupled to the output shaft 29 so as not to rotate in the circumferential direction by connecting the spline teeth 35 c to the axial spline teeth 29 a provided on the output shaft 29.

  The meshing portions 31d and 33d of the forward gear 31 and the reverse gear 33 are provided with a plurality of meshing convex portions 31a and 33a evenly arranged in the circumferential direction as shown in FIG. In the portion 35d, meshing recesses 36a as shown in FIG. 9 are arranged at the same pitch as the meshing projections 31a and 33a.

  These meshing convex portions 31a and 33a and the meshing concave portion 36a are provided in a range inside the input gears 31c and 33c and outside the output shaft 29. As the range, for example, the shaft of the output shaft 29 is provided. It is preferable to set the radius around 20 to 32 mm. If the minimum radius in this range is too small, the diameter of the output shaft 29 is insufficient, and the strength against the driving force by the engine of 300 PS or more tends to be insufficient. On the other hand, if the maximum radius is too large, the outer diameters of the input gears 31c and 33c of the forward gear 31 and the reverse gear 33 become large, so that the clutch device 25 is enlarged and the outboard motor 10 is likely to be enlarged.

  Further, when driven by an engine of 300 PS or more, it is necessary that at least 7 meshing convex portions 31a and 33a and meshing concave portions 36a are provided, and preferably 10 or less. When there are too many meshing convex parts 31a and 33a and meshing recessed parts 36a, the meshing collision at the time of meshing increases, which is not preferable. Preferably, the number of the meshing convex portions 31a, 33a and the meshing concave portions 36a is 8 to 10, particularly preferably 9 as in this embodiment.

  A driving force transmission surface that faces the engagement recess 36a of the dog gear 35 in the circumferential direction when the dog gear 35 is engaged on the front side in the drive direction of the engagement projections 31a and 33a of the forward gear 31 and the reverse gear 33. 31b, 33b, on the other hand, on the rear side in the driving direction of each meshing recess 36a of the dog gear 35, when meshing with the forward gear 31 and the reverse gear 33, each meshing convex portion 31a of the forward gear 31 and the reverse gear 33, It has a driving force transmission surface 35b that abuts against 33a in the circumferential direction.

In this clutch device 25, the total area of the driving force transmission surfaces 31 b of all the meshing convex portions 31 a in the meshing portion 31 d of the forward gear 31 and the meshing portion 35 d of the dog gear 35 meshing with the meshing portion 31 d of the forward gear 31. The total area of the driving force transmission surfaces 35b of all the meshing recesses 36a is preferably 340 mm ² or more, and more preferably 394.625 mm ² or more.

Also. The sum of the areas of the driving force transmission surfaces 33b of all the meshing convex portions 33a in the meshing portion 33d of the reverse gear 33 and all the meshing concave portions 36a in the meshing portion 35d of the dog gear 35 that meshes with the meshing portion 33d of the reverse gear 33. The total area of the driving force transmission surfaces 35b is preferably 340 mm ² or more, and more preferably 394.625 mm ² or more.

  Here, the total area of the driving force transmission surface 31 b of the forward gear 31 and the total area of the driving force transmission surface 35 b on the forward gear 31 side, or the total area of the driving force transmission surface 33 b of the reverse gear 33 and the reverse gear 33. One of the total areas of the driving force transmission surfaces 35b on the side may be greater than or equal to this area, but preferably both are greater than or equal to this area.

  If the driving force transmission surface 31b, the driving force transmission surface 33b, and the driving force transmission surface 35b are within such ranges, the transmission torque should be sufficiently dispersed in the meshing state of the forward gear 31 or the reverse gear 33 and the dog gear 35. This is because it is easier to prevent breakage of the meshing convex part and the meshing concave part.

  Further, in this clutch device 25, the meshing convex portions 31a, 33a and the meshing concave portion 36a are formed at a pitch θ1 of 40 degrees around the axis of the output shaft 29, respectively. The circumferential length of the recess 36 a is formed in the range of 12 degrees to 23 degrees at an angle centered on the axis of the output shaft 29. This is because within this range, it is easy to ensure the strength against the driving force of the engine of 300 PS or higher.

  In that case, it is preferable that the meshing convex portions 31 a and 33 a are formed to have a circumferential length smaller than the meshing concave portion 36 a by 1 to 12 degrees at an angle centered on the axis of the output shaft 29. This is for ease of meshing. Furthermore, it is particularly preferable here to ensure a difference θ2 of 20 degrees or more between the pitch of 40 degrees and the circumferential length of the meshing protrusions 31a and 33a. This is because the engagement convex portion and the engagement concave portion can be easily and reliably fitted.

  Further, in this clutch device 25, the outer end edges 31g, 33g on the dog gear 35 side of the respective driving force transmission surfaces 31b, 33b, and the forward gear 31 side of each driving force transmission surface 35b on the forward gear 31 side of the dog gear 35, The outer end edge 35g of the dog gear 35 and the outer end edge 35g of the driving force transmission surface 35b on the reverse gear 33 side of the dog gear 35 on the reverse gear 33 side are all straight along the direction orthogonal to the axial direction of the output shaft 29. It is formed in a shape.

  Here, the sum of the lengths of the outer end edges 31g of all the driving force transmission surfaces 31b in the meshing portion 31d of the forward gear 31 and all the meshing portions 35d of the dog gear 35 meshing with the meshing portion 31d of the forward gear 31 are shown. The total length of the outer edge 35g of the driving force transmission surface 35b is preferably 70 mm or more, more preferably 71.75 mm or more.

  The total length of the outer edge 33g of all the driving force transmission surfaces 33b in the meshing portion 33d of the reverse gear 33 and all the driving force transmission in the meshing portion 35d of the dog gear 35 that meshes with the meshing portion 33d of the reverse gear 33. The total length of the outer edge 35g of the surface 35b is preferably 70 mm or more, and more preferably 71.75 mm or more.

  Here, the total of the outer edge 31g of the driving force transmission surface 31b of the forward gear 31 and the total length of the outer edge 35g of the driving force transmission surface 35b on the forward gear 31 side, or the driving force transmission surface of the reverse gear 33 One of the total length of the outer edge 33g of 33b and the total length of the outer edge 35g of the driving force transmission surface 35b on the reverse gear 33 side may be longer than this length, or both. Also good. Preferably, both are longer than this length.

  If the total length of the driving force transmission surface 31b, the driving force transmission surface 33b, and the driving force transmission surface 35b is within such a range, the driving force transmission surface is engaged when the forward gear 31 or the reverse gear 33 meshes with the dog gear 35. It is possible to disperse the impact when the vicinity of the outer end edges 31g, 33g, and 35g of 31b, 33b, and 35b contact each other.

  Further, in this clutch device 25, a slope 37b reaching the rear wall 35e is provided at a top portion 37a which is a meshing convex portion between adjacent meshing concave portions 36a, that is, a top portion 37a on the front side in the driving direction of each meshing concave portion 36a. ing. The slope 37b is formed deeper in the driving direction on the front side in the driving direction of the meshing recess 36a. The portion of the top portion 37 a other than the slope 37 b is formed on a plane orthogonal to the axis of the output shaft 29.

  In this way, by providing seven or more meshing convex portions 31a and 33a and meshing concave portions 36a, the pitch θ1 is reduced and the meshing convex portions 31a and 33a are adjacent to the meshing concave portion 36a even if it is difficult to mesh. It is because it becomes easy to fit in the meshing recessed part 36a by being pressed on the top part to slide and sliding on the slope 37b.

  As shown in FIG. 9, the slope 37b is preferably formed so as to coincide with a virtual plane 37c extending from the bottom 36b at the front end in the driving direction of each meshing recess 36a. This is because the slope 37b can be easily processed.

  The clutch device 25 is configured to be movable in the axial direction by a switching mechanism 41 in which a dog gear 35 is connected to a fixed pin 34.

  As shown in FIGS. 2 and 10 to 12, the switching mechanism 41 is arranged at the center of the end of the output shaft 29 opposite to the propeller 27, and moves in the axial direction connected to the fixing pin 34. A possible shift plunger 43, a shift follower 45 joined to the end of the shift plunger 43, a shift rod 47 for operating the shift follower 45 in the axial direction from the top of the casing 14, and the shift rod And a shift lever 49 that is fixed to the upper portion of 47 and rotates the shift rod 47.

  A positioning ball 51 is arranged on the shift plunger 43 in a state of being urged in the diametrical direction by a spring member 53, and the positioning ball 51 is output at a position where the dog gear 35 does not mesh with the forward gear 31 or the reverse gear 33. It is configured to be able to be locked to the locked portion 29c of the shaft 29.

  Further, as shown in FIGS. 11 and 12, a cam portion 55 that is eccentric from the shaft of the shift rod 47 and is connected to the shift follower 45 is provided in the vicinity of the lower end of the shift rod 47. On the other hand, a lateral groove 57 in which the cam portion 55 is slidable is provided at a portion where the shift follower 45 is connected to the cam portion 55. Therefore, when the shift rod 47 is rotated and the cam portion 55 swings around the axis of the shift rod 47, the cam portion 55 presses the lateral groove 57, and the shift follower 45 and the shift plunger 43 are axially moved. The dog gear 35 is movable in the axial direction.

  In the outboard motor 10 having the clutch device 25 configured as described above, when the drive shaft 21 is rotated by the engine, the forward gear 31 and the reverse gear 33 are rotationally driven in opposite directions by the drive gear 23. When the shift rod 47 is rotated to one side of the forward movement by the shift lever 49, the cam portion 55 of the shift rod 47 swings and presses the lateral groove 57 of the shift follower 45 to one side, thereby shifting the shift rod 47. The follower 45 and the shift plunger 43 move toward the end of the output shaft 29 in the axial direction.

  Then, the dog gear 35 moves toward the axial end of the output shaft 29 via the fixed pin 34 connected to the shift plunger 43, and one meshing portion 35 d of the dog gear 35 meshes with the forward gear 31.

  At this time, the forward gear 31 rotates at a rotational speed corresponding to the rotational speed of the engine, but the output shaft 29 and the dog gear 35 have a rotational speed different from that of the forward gear 31 such as in a stopped state. That is, the meshing convex part 31a moves at a faster speed than the meshing concave part 36a. Therefore, if the dog gear 35 is inserted at a sufficiently high moving speed in the axial direction at a position where the meshing recess 36a faces the meshing projection 31a, the meshing recess 36a can be directly fitted to the meshing projection 31a. However, normally, when the dog gear 35 is moved in the axial direction, as shown in FIGS. 13A to 13E, the adjacent engaging recesses 36a are brought into contact with the top surface of the engaging protrusion 31a. Will be.

  First, as shown in FIG. 13 (a), when the meshing concave portion 36a is moved in the arrow X direction while the meshing convex portion 31a is moving in the arrow X direction, the top surface of the meshing convex portion 31a is moved. The top 37a between the meshing recesses 36a is pressed against 31e, and the top 37a slides on the top surface 31e of the meshing projection 31a to reach the slope 37b as shown in FIG. Here, it moves along the shape of the slope 37b, and as shown in (c), the meshing concave part 36a is guided to the meshing convex part 31a side. When the engagement recess 36a reaches the position of the engagement protrusion 31a, as shown in (d), the tip portion of the drive force transmission surface 35b of the engagement recess 36a is the outer end of the drive force transmission surface 31b of the engagement protrusion 31a. The meshing convex part 31a is disposed at a predetermined position in the meshing concave part 36a in contact with the edge. Thereafter, as shown in (e), the meshing convex portion 31a is fitted into the meshing concave portion 36a, and the driving force transmission surfaces 31b and 35b are reliably brought into contact with each other so that the dog gear 35 and the forward gear 31 are meshed with each other. Is done.

  When the dog gear 35 and the forward gear 31 are engaged with each other in this way, the driving force from the drive shaft 21 is transmitted to the dock gear 35 via the forward gear 31, and is transmitted to the output shaft 29 by the spline teeth 35c of the dog gear 35. Thus, the output shaft 29 and the propeller 27 connected to the output shaft 29 can be rotated in the forward direction.

  When reversing, the shift rod 49 is rotated in the opposite direction by the shift lever 49, the shift follower 45 and the shift plunger 43 are moved in the opposite direction by the cam portion 55 of the shift rod 47, and the dog gear 35 is moved. By moving the output shaft 29 toward the propeller 27, the dog gear 35 and the reverse gear 33 may be engaged with each other in the same manner as described above.

  According to the outboard motor 10 having the clutch device 25 configured as described above, the meshing protrusions 31a, 33d, 35d of the dog gear 35, the forward gear 31, and the reverse gear 33 that face each other are engaged with each other. 33a and the meshing recess 36a are disposed radially inward of the input gears 31c and 33c, so that the meshing projections 31a and 33a and the meshing recess 36a are limited between the input gears 31c and 33c and the output shaft 29. Is placed in the space. Therefore, the sizes of the meshing convex portions 31a and 33a and the meshing concave portion 36a are remarkably limited.

  However, even in such a limited space, seven or more meshing convex portions 31a, 33a and meshing concave portions 36a are provided in the circumferential direction, and the meshing convex portions 31a, 33a and the meshing concave portion 36a are mutually connected during meshing. Since it is configured to distribute the transmission torque to each of the driving force transmission surfaces 31b, 33b, and 35b opposed in the circumferential direction, a large driving force is transmitted to the output shaft 29 from the driving unit having the maximum output of 300 PS or more. Even when engaged, when the driving force is transmitted in the engaged state, it is possible to prevent the engaging protrusions 31a, 33a and the engaging recess 36a from being crushed, broken, deformed, or the like. . For example, even if the transmission torque of the clutch device 25 is 60 kg · m or more, the breakage can be sufficiently prevented.

  The above-described embodiment can be appropriately changed within the scope of the present invention. For example, in the above description, the example in which the slope 37b is provided only for the dog gear 35 has been described. However, the forward gear 31 and the reverse gear 33 may be provided with slopes, and the forward gear 31, the reverse gear 33, and the dog gear 35 may be provided with slopes. Is also possible

DESCRIPTION OF SYMBOLS 10 Outboard motor 21 Drive shaft 23 Drive gear 25 Clutch device 29 Output shaft 31 Advance gear 31a Engagement convex part 31b Drive force transmission surface 31c, 33c Input gear 31d Engagement part 31g Outer edge 33 Retraction gear 33a Engagement convex part 33b Drive force Transmission surface 33d Meshing portion 33g Outer edge 35 Dog gear 35b Driving force transmission surface 35d Meshing portion 36a Meshing recess 37b Slope

Claims (5)

A drive unit mounted on an upper portion of the casing, and a drive shaft driven by the drive unit;
A drive gear disposed on the lower end side of the drive shaft so as to be rotatable integrally with the drive shaft;
A clutch device disposed at a lower portion of the casing and connected to the drive gear;
An output shaft coupled to the clutch device and driving a propeller,
The clutch device is
A pair of forward gears and reverse gears that are rotatably arranged around the output shaft that drives the propeller, and are always driven in opposite directions by the drive shaft driven by the drive unit;
A dog gear that is disposed between the forward gear and the reverse gear around the output shaft, is movable in the axial direction with respect to the output shaft, and is not rotatable in the circumferential direction;
Engaging protrusions that can be fitted to each other at meshing portions provided at portions of the forward gear and the reverse gear facing the dog gear and portions of the dog gear facing the forward gear and the reverse gear, respectively. A plurality of meshing recesses are provided,
The dog gear is moved in one axial direction with respect to the output shaft, and the plurality of meshing recesses and the plurality of meshing projections are fitted, whereby the dog gear and the forward gear or the reverse gear are One is meshed, and the output shaft is configured to be driven,
The drive shaft rotates the drive gear fixed to the output shaft side,
The forward gear and the reverse gear each include an input gear that is always meshed with the drive gear,
The outboard motor, wherein the meshing convex portion and the meshing concave portion are arranged in the circumferential direction in the range of 7 to 10 in the radial direction from the input gear.   2. The outboard according to claim 1, wherein the engagement convex portion is formed so that a circumferential length thereof is smaller by 1 to 12 degrees in terms of an axial center angle of the output shaft than the engagement concave portion. Machine. The total area of the driving force transmission surfaces is 340 mm ² or more in each meshing portion of the forward gear and the dog gear or each meshing portion of the reverse gear and the dog gear, respectively. The outboard motor according to 1 or 2. In each meshing portion between the forward gear and the dog gear or each meshing portion between the reverse gear and the dog gear, the outer edge of each driving force transmission surface is orthogonal to the axial direction of the output shaft. Formed in a straight line along the direction,
The outboard motor according to any one of claims 1 to 3, wherein the total length of the outer end edges of the respective meshing portions is 70 mm or more.   In each meshing part of the forward gear and the dog gear or each meshing part of the reverse gear and the dog gear, at least one of the meshing convex parts is formed on the top part adjacent to the meshing concave part. The outboard motor according to any one of claims 1 to 4, wherein a slope for guiding is formed.

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