JPH0629620B2 - Dog type clutch shift device - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dog clutch mainly used for an outboard propulsion device, and more particularly to a dog clutch which is engaged and disengaged using a shift cam.

2. Description of the Related Art Generally, an outboard propulsion apparatus equipped with this type of dog clutch has a structure as shown in FIG. That is, the lower case (2) below the main body of the outboard motor (2) has the output shaft (3) rotatably supported in the horizontal direction and the propeller at the rearward protruding end.
(4) is installed. A forward bevel gear (5) and a reverse bevel gear (6) are attached to the output shaft (3) so as to be freely rotatable at front-rear intervals, and the drive shaft is arranged to be rotatable in the vertical direction. (7) Input bevel gear provided at the lower end (8)
Mesh with the forward bevel gear (5) and the reverse bevel gear (6), respectively. A clutch dog (9) externally fitted to the output shaft (3) is mounted between the forward bevel gear (5) and the reverse bevel gear (6) so as to be movable back and forth in the axial direction.

The plunger (10), which is also inserted from the front end side of the output shaft (3), is in contact with the shift cam (12) that moves up and down in conjunction with the shift rod (11). Conventionally, this shift cam (12) is integrally connected to the shift rod (11) by, for example, a pin (13), and
Via the lever arm (14) connected to the upper end side of (11),
It was interlocked with the operation lever shaft (15) arranged on the upper side of the outboard motor body (1). That is, during the fitting / removing operation, the operation lever shaft (15) is rotated by a manual operation, whereby the shift cam (1) is moved through the shift rod (11).
2) is moved up and down while being in contact with the plunger (10) to selectively engage the clutch dog (9) with the forward bevel gear (5) or the reverse bevel gear (6). It was.

In the figure, (16) shows a detent cam fixed to the operation lever shaft (15) .By engaging a detent spring (17) with a notch provided in the detent cam (16), the shift cam (16) ) Is held in each of forward, reverse and neutral states. Note that FIG. 15 shows the neutral state.

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention In a ship, it may be necessary to rapidly activate the clutch mechanism in the event of a crash astern. Further, in this type of dog clutch, if the clutch operation is too slow, the clutch dog side claws and the gear side claws collide when the clutch dog is fitted, and the fitting operation cannot be performed smoothly, or the claw part cannot be performed. There is a possibility that the ship may not be maneuverable due to wear, chipping or breakage.

In order to prevent such a situation, the fitting speed of the clutch dog may be increased, and for that purpose, the operation member for operating the shift cam may be moved rapidly or the shape of the shift cam may be made steep.

However, in the former case, since an operating member such as a shift rod is generally operated by a human hand, there is a limit in increasing the moving speed of the shift cam from the physiological limit. On the other hand, even in the latter case, when the shape of the shift cam is made steep, the bending force acts on the plunger in contact with the shift cam, and the fitting operation does not go smoothly, or the plunger is broken. , There is a risk of burning.

The present invention has been made for the purpose of solving such problems and providing a shift device capable of performing a quick engagement operation in a dog clutch.

Means for Solving Problems Hereinafter, means for solving the problems will be described with reference to FIG. 1 corresponding to the embodiment.

That is, the clutch dog (31) mounted on the shaft (24) so as to be movable in the axial direction is in sliding contact with the shift cam (41) (42).
The shift cam (41) is operated to move in the axial direction through the clutch dog (31) and the counterpart clutch bodies (28) and (29) to engage and disengage. The shift cam (41) and the operating member (48) for operating the shift cam (41) are connected so as to be movable in the shift direction through a gap (52) provided at an appropriate position between them. ing. And the shift cam (41) has a spring
Due to the pressing forces of (39) and (55), a pair of inclined surfaces (46) and (59) having different inclination directions are formed for rapidly moving the shift cam (41) to the fitting side.

Action With the above configuration, when the shift cam (41) is moved via the operating member (48) during the clutch fitting operation, the shift cam (41) is acted by the biasing means acting on the shift cam (41). ) Rapidly moves in the clutch engaging direction independently of the operating member (48) by the amount of the gap (52).

Embodiment An embodiment in which the present invention is applied to an outboard propulsion device similar to the conventional one will be described below with reference to the drawings.

In FIG. 1, (20) indicates a lower case on the lower side of the outboard motor body (21), and the lower case (20) has a hollow portion (22) at the center thereof and a drive shaft (23) power source. A bevel gear type power switching mechanism (25) for selectively transmitting the power to the output shaft (24) is provided.

This bevel gear type power switching mechanism (25) has the following structure. That is, the output shaft (24) arranged so as to horizontally traverse the hollow portion (22) is rotated through the bearings (26) and (27) at the front and rear ends of the hollow portion (22). It is freely supported, and its rear end side penetrates the lower case (20) and projects rearward. A propeller (not shown) is attached to the rearward protruding end as in the conventional case. Also, the output shaft (24)
A forward bevel gear (28) and a reverse bevel gear (29) are rotatably and axially supported by the front and rear bevel gears (29) with a front-rear space therebetween. An input bevel gear (30) at the lower end of the vertically arranged drive shaft (23) meshes with the forward bevel gear (28) and the reverse bevel gear (29). Although not shown, an engine is connected to the upper end portion of the drive shaft (23). Therefore, the forward bevel gear (28) and the reverse bevel gear (29) receive the power of the engine transmitted through the drive shaft (23) and rotate in opposite directions.

A cylindrical clutch dog (31), which is similarly fitted over the output shaft (24), is arranged between the forward / reverse bevel gears (28) and (29). On the side wall of the output shaft (24), the output shaft (2
4) A long hole (32) is formed in the axial direction so as to penetrate in the transverse direction, and both ends of the pin (33) inserted in the long hole (32) are fitted into the clutch dog (31). is doing. Therefore, the clutch dog (31) is connected to the output shaft via the pin (33).
The output shaft (24) is held so as to rotate integrally with (24), and is freely movable in the axial direction of the output shaft (24) by the space of the elongated hole (32). A forward clutch pawl (34) and a reverse clutch pawl (35) are provided on both ends of the clutch dog (31). On the other hand, the forward / reverse bevel gears (28, 29) are provided with a forward drive pawl (36) and a reverse drive pawl (37), respectively, the forward clutch pawl (34) and the reverse clutch pawl (35). ) Is provided facing each other. That is, in the present embodiment, these forward / reverse bevel gears (28) and (29) are the counterpart clutch bodies for the clutch dog (31).

Then, the plunger (38) arranged in the horizontal direction is inserted from the front end side of the output shaft (24), and the proximal end side of the plunger (38) contacts the pin (33). There is.
(39) shows a shift spring installed in the axial direction of the output shaft (24), one end side of the shift spring (39) is in contact with the pin (33), and through the pin (33). The clutch dog (31) and the plunger (38) are biased forward.

On the other hand, a stepwise shift cam (41) is arranged on the lower side of the vertically long shift rod chamber (40) formed on the front side of the lower case (20). The shift cam (41) has a forward moving surface (43), a neutral surface (44), and a reverse moving surface (45) facing the sliding contact portion (42) on the other end side of the plunger (38) and oriented vertically. Are formed in order from the bottom, the advancing surface (43) and the neutral surface
(44) are continuous with each other through the lower transition surface (46) that is inclined obliquely upward, and the neutral surface (44) and the reverse surface (45) are also the upper transition surface (47) that is inclined obliquely upward. Are continuous with each other through.

And, when it is neutral, as shown, the plunger (38)
The sliding contact portion (42) is pressed by the shift spring (39) and is in contact with the neutral surface (44) of the shift cam (41). In this state, before the clutch dog (31)
The reverse clutch pawls (34) (35) are the forward drive pawls (36).
Also, the drive shaft for driving the drive shaft (23) is not engaged with any of the reverse drive claws (37), and thus the power of the drive shaft (23) is not transmitted to the output shaft (24).

Next, the shift device according to the present invention will be described. On the upper side of the shift cam (41), a shift rod (48) as an operating member is arranged so as to be vertically movable, and the lower end portion of the shift rod (48) is the upper end portion of the shift cam (41). It is adapted to be inserted into the shaft hole (49) formed in the vertical direction. As shown in FIG. 2, reference numeral (50) denotes a vertically elongated hole formed at the lower end of the shift rod (48). A connecting pin having the shaft hole (49) mounted in the transverse direction at the upper end portion of the shift cam (41).
(51) penetrates the elongated hole (50), and the shift cam (41) and the shift rod (48) are connected to each other via the connecting pin (51). A gap (52) is formed between the elongated hole (50) and the connecting pin (51), and the shift cam (41) and the shift rod (48) are independent of each other by the gap (52). And it can move freely in the vertical direction.

The clutch engagement operation during forward movement in this embodiment will be described below.

First, by pulling up the shift rod (48),
As shown in FIG. 3, until the sliding contact portion (42) of the plunger (38) reaches the boundary between the neutral surface (44) of the shift cam (41) and the lower transition surface (46), The shift cam (41) is the connecting pin
The (51) is moved upward while being in contact with the lower end of the elongated hole (50) of the shift rod (48). Then, when the sliding contact portion (42) crosses the boundary portion and moves to the lower transfer surface (46), the shift cam (4
An upward force is exerted on 1) by the urging force of the shift spring (39) acting on the sliding contact portion (42), whereby the connecting pin (51) is moved into the elongated hole (as shown in FIG. 4). 50) move upwards and shift cam against the shift rod (48)
(41) will move rapidly. Therefore, the clutch dog (31) is pressed by the shift spring (39) and rapidly moves forward, and the forward clutch pawl (34) is moved by the forward bevel gear (2
It will be quickly inserted into the drive pawl (36) for advancing of 8). Then, by further moving the shift rod (48) upward from such a state, the sliding contact portion (42) advances the continuous surface with the lower transfer surface (46) as shown in FIG. The contact operation with (43) ends.

In this case, from the neutral state of the forward clutch pawl (34) shown by the solid line in FIG. 6 to the front end clutch pawl (34) and the forward drive pawl (36) on both sides, as shown by the two-dot chain line. Letting (S ₁ ) be the minimum insertion stroke required to move to a state where it overlaps more than the take-up portion, as shown in FIG. 4, the plunger (38) exerts a clutch effect from the position of the neutral surface (44). The movement distance (L ₁ ) that must move before it is effectively exerted must satisfy the relationship of L ₁ > S ₁ (1). And the lower transition surface
The inclination angle of (46) is (θ), and the size of the gap (52) is (G ₁ )
Then, the relationship of G ₁ = L ₁ / tan θ (2) is established, and therefore the dimension of the gap (52) of the elongated hole (50) is G ₁ because of the relationship with the above equation (1). > S ₁ / tan θ ·············· (3) is required to be large.

Since the shift cam (41) moves relative to the shift rod (48) by the amount of the gap (52), the vertical length of the neutral surface (44) is set to the gap. It is necessary to extend it by the amount of (52).

Further, in the present embodiment, the urging force of the shift spring (39) that applies pressure to the clutch dog (31) is transmitted to the shift cam (41) via the sliding contact portion (42) of the plunger (38). Therefore, it is only necessary to connect the shift cam (41) and the shift rod (48) with the connecting pin (51) in a state having the gap (46), and there is an advantage that the structure is extremely simple.

Next, FIG. 7 to FIG. 11 show a quick fitting mechanism of the shift cam (41) to the reverse side.

Also in this embodiment, the bevel gear type power switching mechanism (2
5) is common with the embodiment of FIG. 1, and the output shaft (24)
The sliding contact portion (42) of the plunger (38) protruding forward from the shaft end portion of the shaft contacts the shift cam (41). Also in this case, the lower end side of the shift rod (48) is inserted into the shaft hole (49) provided at the upper end of the shift cam (41) as shown in FIG.
(41) Insert the connecting pin (51) attached to the upper end side so that the gap (52) remains in the upper and lower elongated holes (50) formed in the shift rod (48), and then connect the connecting pin (51). By shift rod
The (48) and the shift cam (41) are connected so as to be relatively movable in the vertical direction.

Then, in this embodiment, holes (54) and (54) are formed in the left and right side wall portions (53) and (53) of the lower case (20) in a horizontal direction substantially perpendicular to the orientation direction of the plunger (38). Then, the auxiliary springs (55) (55) as the urging means in this embodiment are respectively installed in both holes (54) (54). Holes in them (54)
A spherical body arranged on the other end side of the auxiliary springs (55) (55) by pressing one end side of the auxiliary springs (55) (55) with the plugs (56) (56) screwed from the outside of the (54) (57) (57)
Are pressed against the outer surface of the shift cam (41) from both left and right directions. Also, on the outer surface on the upper end side of the shift cam (41),
A flute (5) having a width sufficient for the spheres (57) (57) to enter.
8) and (58) are formed, and at the lower ends of the vertical grooves (58) and (58), the upper transition surface (47) on the lower side of the shift cam (41) is formed.
On the contrary, downwardly inclined surfaces (59) and (59) which are inclined obliquely downward are provided. At neutral, the spheres (57) (57) are
As shown in FIG. 7, the outer surface of the shift cam (41) is in contact with the outer surface of the shift cam (41) when it comes off from the boundary with the downward inclined surfaces (59, 59).

In the following, the quick fitting operation at the time of reverse travel in this embodiment will be described.

When moving backward, the shift rod (48) is moved downward, contrary to the previous time. Then, the shift rod (4
8) is a connecting pin on the upper end side of the long hole (50) as shown in FIG. 8 (A).
With the (51) abutting, it moves downward to the boundary between the neutral plane (44) and the upper transition plane (47). In this state, the spheres (57) and (57) have moved to the boundary with the downward slopes (59) and (59) as shown in FIG. When the spheres (57) (57) enter the above-mentioned downward slopes (59) (59) even slightly beyond the boundary part, the auxiliary spring
(55) Due to the biasing force of (55), those downward inclined surfaces (59) (5
A downward force acts on the shift cam (41) via the (9), and the shift cam (41) shifts by a length allowed by the gap (52) as shown in FIGS. 9 (A) and (B). It will move rapidly downward independently of the rod (48). Therefore, the sliding contact portion (42) moves from the neutral surface (44) to the upper transition surface (47).
The plunger (38) suddenly moves rearward, and in conjunction with this, the clutch dog (3
1) rapidly moves rearward against the shift spring (39), and the reverse clutch pawl (35) rapidly fits into the reverse drive pawl (37). Then, by further moving the shift rod (48) downward from such a state, the sliding contact portion (42) is moved to the upper transfer surface (47) as shown in FIG. 10 (A).
Then, the fitting operation is completed by contacting the reverse surface (45) which is continuous with.
In this case, as shown in FIG.
7) and (57) are in contact with the shift cam (41) in the vertical grooves (58) and (58).

In this case, from the neutral state of the reverse clutch pawl (35) shown by the solid line in FIG. 11, as shown by the two-dot chain line, the reverse clutch pawl (35) is on both sides of the reverse drive pawl (37). Assuming that the minimum insertion stroke (S ₂ ) required to move to a state where it overlaps beyond the take-up portion is (S ₂ ), the clutch effect is effective from the position of the plunger (38) on the neutral surface (44) as shown in FIG. The moving distance (L ₂ ) that has to move before it is required to satisfy the relation of L ₂ > S ₂ (4). When the length from the neutral position until the spheres (57) (57) start to slide on the downward inclined surfaces (59) (59) is (l ₁ ), this length (l ₁ ) is the plunger (38). ) Corresponds to the length (l ₀ ) from the neutral position of the shift cam (41) to the upper transfer surface (47). Further, the length by which the shift cam (41) moves relative to the plunger (38) is (l), and the inclination angle of the upper transition surface (47) is (θ ₁ ), and the downward inclined surface (59). (59) Sphere on top (57) (5
If the moving length of 7) is (l ₂ ), then l ₂ = l-l ₀ = L ₂ / tan θ ₁ (5) holds between them. Further, in order for the shift cam (41) to move freely by (l ₂ ), the length (G ₂ ) of the gap (52) must be G ₂ = l ₂ (6), so the above ( From equations 4) to (6) (G ₂ )
Needs to satisfy the relationship of G ₂ = L ₂ / tan θ ₁ > S ₂ / tan θ ₁ (7).

Also, the urging force per single auxiliary spring (55) is (P ₂ ), and the pushing force of the plunger (38) by the shift spring (39) is (P ₁ ), and the lower end of the vertical groove (58) (58) When the inclination angle of the downward inclined surfaces (59) (59) is (θ ₂ ), a force sufficient to satisfy the relationship of 2P ₂ / tanθ ₂ > P ₁ / tanθ ₁ (8) Must be provided by an auxiliary spring (55).

As shown in FIG. 12, an auxiliary spring (60) is arranged on the opposite side of the plunger (38) with the shift cam (41) interposed therebetween, and the auxiliary spring (60) moves the sphere (61) to the shift cam (41). ) It may be arranged in the vertical groove (62) on the back surface. In this case, on the upper side of the position of the sphere (61) in the neutral state, a recessed portion (63) further entering is provided, and between the recessed portion (63) and the vertical groove (62). Consecutive slopes (64)
Should be provided. In this case, the biasing force of the auxiliary spring (60) may be about twice the pushing force of the shift spring (39) against the plunger (38).

Next, in FIG. 13 and FIG. 14, an embodiment which enables rapid insertion during forward / reverse movement by slightly modifying the one for reverse rapid insertion shown in FIG. 7 to FIG. Indicates
FIG. 13 corresponds to FIG. 7, and FIG. 14 corresponds to FIG.

First, referring to FIG. 13, also in this case, as in FIG. 7, the left and right side wall portions (53) (5) of the lower case (20)
3) through the hole (54) (54), the sphere (57) (5
Auxiliary springs (55) (55) in which 7) is arranged are installed, and plugs (56) screwed from the outside of the holes (54) (54).
The auxiliary springs (55) and (55) are pressed by the (56) so that the spherical bodies (57) and (57) are pressed against the outer surface of the shift cam (41). On the other hand, the shift cam (41) has a vertical groove (having a width sufficient for the spheres (57) (57) to enter, on the upper side of the abutment position of the spheres (57) (57) in the neutral position as a reference. 58a) and (58a) are formed, and similar vertical grooves (58b) and (58b) are also formed on the lower side. Then, on the lower end side of the upper side vertical groove (58a) (58a), while forming a downward inclined surface (59a) (59a) that inclines obliquely downward, while the lower side vertical groove (58b)
On the upper end side of (58b), on the contrary, upwardly inclined surfaces (59b) and (59b) which are inclined obliquely upward are formed.

Therefore, when moving forward, by moving the shift rod (48) upward, the spherical body (57) (57) slides on the upward slopes (59b) (59b) and the lower vertical groove. (58b)
(58b), the shift cam (41) rapidly moves upward by the amount of the clearance (52) independently of the shift rod (48), and enters the quick fitting state. Therefore, it is possible to obtain better fitting characteristics than those shown in FIGS. 2 to 5. Also,
When moving in reverse, the shift rod (48) is moved downward to move the spheres (57) (57) to the downwardly inclined surface (5
9a) and (59a) into the vertical grooves (58a) and (58a) on the upper side, and in this case also, the shift cam (41) moves independently of the shift rod (48) by the gap (52). , The state of rapid insertion.

Next, referring to FIG. 14, similar to FIG. 12, the auxiliary spring (60) is arranged on the side opposite to the plunger (38) with the shift cam (41) interposed therebetween.
Move the sphere (61) by the (60) vertical groove (62) on the back of the shift cam (41)
It is placed inside. Then, also in this case, in the vertical groove (62), the recessed portions (63a) (63b) are provided on the upper side and the lower side, respectively, with reference to the contact position of the spherical body (61) in the neutral state. Between the recessed portions (63a) (63b) and the vertical groove (62), inclined surfaces (64a) (64b) inclined in opposite directions are provided. Therefore, even in this case, the shift rod (4
By moving the 8) up and down, the clearance (52) between the shift rod (48) and the shift cam (41) enables quick fitting during forward and reverse travel.

In the above embodiment, the connecting pin (51) is attached to the shift cam (41).
The connecting pin (51) is inserted through the neutral surface (44) provided on the shift rod (48), but the opposite mode, that is, the connecting member is fixed to the shift rod (48). do it,
The connecting member may be connected to the shift cam (41) with a gap. Furthermore, the shift cam (41) and the shift rod (48) may be integrally connected, and a similar structure may be provided on the upper side of the shift rod (48). However, considering the operating speed of the clutch, the smaller the equivalent mass on the shift cam (41) side, the faster the fitting speed.Therefore, by the connecting member provided close to the shift cam (41) as in the above embodiments. It is desirable to connect the shift cam (41) and the shift rod (48) with a gap (52).

Effects of the Invention As described above, in the present invention, the shift cam and the operating member for operating the shift cam are coupled so as to be movable in the shift direction through a gap provided at an appropriate position between them, By providing the biasing means for biasing the shift cam in the clutch fitting direction at the time of the fitting operation, even when the operating member is manually operated, the shift cam is operated by the biasing means so that the clearance of the gap is maintained. Therefore, it moves rapidly in the clutch engaging direction independently of the operating member. Therefore, the clutch dog mounted on the shaft rapidly moves through the sliding contact portion that is in sliding contact with the shift cam, and the clutch dog can be rapidly engaged without making the inclination angle of the shift cam steep. That will have a remarkable effect.

In particular, in the present invention, a pair of inclined surfaces having different inclination directions are formed so that the shift cam is rapidly moved not only on the forward drive side but also on the reverse drive side. There is an effect that the quick engagement operation of the clutch becomes possible. Moreover, since the rapid movement of the shift cam is realized by urging the pressing force of the spring against the inclined surface, for example, the shift rod is divided and the spring is provided between them, and the spring is temporarily provided during the shift operation. Unlike the one that accumulates pressure and moves rapidly with its resilience, the movement of the shift rod during insertion operation does not become unstable, and the device itself must be enlarged to eliminate the instability. There is no effect.

[Brief description of drawings]

FIG. 1 is an enlarged sectional view of an essential part showing an embodiment of the present invention, FIG.
The figure is also a vertical cross-sectional view around the shift cam, FIGS. 3 to 5 are operation explanatory views in the forward insertion operation, and FIG.
Similarly, FIG. 7 is a schematic explanatory view showing the arrangement state of the forward clutch pawl of the clutch dog and the forward drive pawl of the forward bevel gear at the time of the forward fitting operation, and FIG. Longitudinal sectional view, FIG. 8 (A)
FIGS. 10 (B) to 10 (A) and 10 (B) are explanatory diagrams of the operation during the reverse insertion operation, and FIG. 11 is a reverse clutch pawl for the clutch dog and the reverse drive of the reverse bevel gear during the reverse insertion operation. 12 and 14 are schematic sectional views showing the arrangement with the claws, FIG. 12 to FIG. 14 are sectional views around a shift cam showing still another embodiment of the present invention, and FIG. 15 is a partial sectional view showing a conventional example. Is. (24) …… output shaft, (28) …… forward bevel gear, (29) …… reverse bevel gear, (31) …… clutch dog, (38) …… plunger,
(39) …… Shift spring, (41) …… Shift cam, (42)
...... Plunger sliding contact part, (46) …… Inclined surface, (48) ……
Shift rod, (52) …… gap, (55) (60) …… auxiliary spring, (59) …… sloping surface.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Masayoshi Furukawa 1-32 Chayamachi, Kita-ku, Osaka City, Osaka Prefecture Yanmar Diesel Co., Ltd. (56) Reference JP 61-21450 (JP, A) JP Sho 59-9315 (JP, A) Actually opened Sho 57-141230 (JP, U) Japanese Patent Sho 37-4807 (JP, B1)

Claims (1)

[Claims] 1. A clutch dog mounted on a shaft so as to be movable in the axial direction is moved in the axial direction through a sliding contact portion which is slidably contacted with a shift cam, and the clutch dog and the mating clutch body are fitted in forward and backward directions. In a dog clutch adapted to perform a disengagement operation, the shift cam and an operating member for operating the shift cam are connected so as to be movable in the shift direction through a gap provided at an appropriate position between them. Similarly, the shift cam is inserted into the shift cam by the pressing force of the spring force from the outside, corresponding to the position immediately before the shift cam is inserted from the neutral position to the forward drive side and the position immediately before the neutral position is inserted to the reverse drive position. A dog-type clutch shift device characterized in that a pair of inclined surfaces having different inclination directions for rapidly moving to are provided.