JPH0138977B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a forward/reverse switching device for a marine vessel propulsion device such as an inboard/outboard motor or an outboard motor.

FIG. 1 is an explanatory diagram showing an outer drive unit 3 of a general inboard/outboard motor, which is attached to the transom of a hull 1 via a support arm 2. As shown in FIG. The output of the engine located inside the hull 1 is
A propeller 9 can be rotated forward or backward through a transmission shaft 4, an input shaft 5, a forward/reverse switching device 6, a drive shaft 7, and a propeller shaft 8. here,
The forward/reverse switching device 6 meshes with the input gear 5A fixed to the input shaft 5, and selects either the forward gear 6A or the reverse gear 6B, which rotate in opposite directions, through a clutch mechanism. By integrating the drive shaft 7 with the drive shaft 7, the drive shaft 7, propeller shaft 8, and propeller 9 can be rotated forward or backward.

FIG. 2 is an explanatory diagram showing a conventional improved forward/reverse switching device for a marine vessel propulsion device. An input gear 12 fixed to the input shaft 11 meshes with a forward gear 14 and a reverse gear 15 that are rotatably supported on a drive shaft 13.
5 are rotated in opposite directions. Synchronizing disks 16 and 17 are integrated on the inner peripheral sides of the meshing teeth of the forward gear 14 and the reverse gear 15, respectively. The synchronizing disks 16, 17 are provided with inward friction conical surfaces 16A, 17A, and clutch pawls 16B, 17B on the inner peripheral side of the inward friction conical surfaces 16A, 17A. In addition, the forward gear 14 shaft support position of the drive shaft 13 and the reverse gear 15
A clutch dog 18 is spline-coupled to an intermediate portion between the shaft support position and the clutch dog 18, which slides in the axial direction of the drive shaft 13 and can be selectively shifted from a neutral position to a forward position or a reverse position. A through hole 19 formed in the drive shaft 13 is provided in the sliding surface between the drive shaft 13 and the clutch dog 18.
A clutch dog positioning mechanism is provided, which is formed by a detent ball 21 that clamps a spring 20 inserted into the clutch dog 18, and a wave-shaped positioning groove 22 provided in the clutch dog 18 and into which the detent ball 21 fits. Both end faces of the clutch dog 18 are provided with clutch pawls 18A, 18B that can engage with clutch pawls 16B, 17B integrated with the forward gear 14 or the reverse gear 15. Further, synchronizing sleeves 23 and 2 on the forward and reverse sides are provided on the outer periphery of both ends of the clutch dog 18.
4 are spline-coupled and engaged to be slidable in the axial direction. The synchronizing sleeves 23, 24 are provided with outward friction conical surfaces 23A, 24A which can be fitted onto inward friction conical surfaces 16A, 17A which are integrated into the forward gear 14 or the reverse gear 15. Further, a plurality of accommodation holes 25A, 25B are bored in the radial direction at both ends of the clutch dog 18, and springs 26A, 26B and a detent ball 27 are accommodated in the accommodation holes 25A, 25B.
A, 27B, a ring-shaped locking groove 23 formed on the inner circumferential surface of each synchronizing sleeve 23, 24
B, 24B are elastically pressed, and the clutch dog 18 and the synchronizing sleeves 23, 24 are moved under a predetermined axial direction weight.
The state of integration is maintained.

In the conventional forward/reverse switching device for a marine vessel propulsion device, when the clutch dog 18 is switched from the neutral position to the forward position, when the clutch dog 18 moves forward, that is, downward in the figure, the synchronizing sleeve 23 moves to the detent ball 27A. It moves integrally with the clutch dog 18 through engagement with the locking groove 23B. Due to the advancement of the clutch dog 18 and the synchronizing sleeve 23, the outward friction conical surface 23A of the synchronizing sleeve 23 causes the inward friction conical surface 1 of the synchronizing disc 16, which is integrated into the forward gear 14.
6A, when the shift operation force acting on the clutch dog 18 is increased, initially the outward friction conical surface 23A and the inward friction conical surface 16A
Although they are rotating as they slide against each other, they gradually become synchronized due to frictional force. In this way,
When the clutch dog 18 starts to rotate in synchronization with the forward gear 14, if the clutch dog 18 is shifted more strongly, the detent ball 27A is released from the locking groove 23B and sinks into the accommodation hole 25A. The clutch dog 18 is further shifted one step forward, and the clutch pawl 18 of the clutch dog 18
A is engaged with a clutch pawl 16B of a synchronizing disk 16 that is integrated into the forward gear 14, and the forward gear 14 is connected to the drive shaft 13 via the clutch dog 18.
The drive shaft 13 is reliably integrated with the drive shaft 13 so that the drive shaft 13 can rotate forward. That is, according to such a conventional forward/reverse switching device for a marine vessel propulsion device, after the forward gear 14 or the reverse gear 15 and the drive shaft 13 are synchronized, the clutch integrated with the forward gear 14 or the reverse gear 15 is switched. Since the clutch pawls 18A, 18B of the clutch dog 18 mesh with the pawls 16B, 17B, it is possible to prevent large shocks generated when the clutch is engaged and disengaged, and engine stoppage caused by the impact.

However, in such a conventional forward/reverse switching device for a marine propulsion device, the clutch dog 18
The axially connected state of the synchronizing sleeves 23, 24 under a predetermined load is the same as that of the springs 26A, 26B and detent balls 27A, 27B accommodated in the plurality of accommodation holes 25A, 25B provided in the clutch dog 18. , synchronous sleeve 2
Locking grooves 23B and 24B provided in 3 and 24
Because it relies on the locking action with the That is, the detent balls 27A, 2
7B is held in line contact with the inner wall surfaces of the housing holes 25A and 25B, making it unstable to maintain and release the connection between the clutch dog 18 and the synchronizing sleeves 23 and 24. Also, Clutchdog 18
Since a large number of accommodation holes 25A and 25B are formed in the thick portion of the clutch dog 18, the mechanical strength of the clutch dog 18 is reduced. Further, springs 26A, 26B and detent balls 27A,
The assembly work is difficult because it is necessary to carry out the assembly work while accommodating the 27B.

The present invention has been made in order to eliminate the above-mentioned conventional drawbacks, and provides a forward/reverse switching device for a marine propulsion device having a synchronized mesh mechanism with stable operability, high strength, and good ease of assembly. The purpose is to

In order to achieve the above object, the forward/reverse switching device for a marine vessel propulsion device according to the present invention meshes with the input gears fixed to the input shaft, and has an inward friction conical surface on the inner peripheral side of the meshing teeth. a forward gear and a reverse gear that are rotatably supported on the drive shaft and rotate in opposite directions, each having a clutch pawl on the inner circumferential side of an inwardly directed friction conical surface, and a forward gear shaft support position of the drive shaft. A clutch pawl that is slidably engaged in the axial direction at an intermediate portion between the reverse gear shaft support position, is selectively shifted from the neutral position to the forward position or the reverse position, and is capable of engaging with the clutch pawl of the forward gear or the reverse gear. a clutch dog that is provided on both end faces; and a forward side that is provided with an outward friction conical surface that engages with the outer periphery of both end sides of the clutch dog so as to be able to slide in the axial direction and that can be fitted to an inward friction conical surface of a forward gear or a reverse gear. It is accommodated in the ring-shaped accommodation grooves formed on the outer periphery of each synchronizing sleeve on the reverse side and both ends of the clutch dog, and is elasticized in the ring-shaped locking groove formed on the inner circumferential surface of each synchronous sleeve. Each of the synchronizing rings on the forward and reverse sides are engaged with each other.

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 3 and 4 are explanatory diagrams showing an embodiment of a forward/reverse switching device for a marine vessel propulsion device according to the present invention. An upper case 31 housing an outer drive unit of an inboard/outboard motor rotatably supports an input gear 33 and an input shaft 34, which are integrated with each other, via a bearing 32. Input shaft 34
is connected to an engine located inside the hull via a transmission shaft or the like. Further, a forward gear 37 is disposed in the Atsupa case 31 via bearings 35 and 36, and a bearing 3
8, and a drive shaft 42 is rotatably supported coaxially with the forward gear 37 and the reverse gear 39 through bearings 40 and 41. That is, the forward gear 37 and the reverse gear 39 each mesh with the input gear 33, are rotatably supported by the drive shaft 42, and are rotatable in opposite directions.

On the inner periphery of the meshing teeth of the forward gear 37 and the reverse gear 39, there are synchronizing disks 43, 4 made of case hardened nickel chrome molybdenum steel that has been surface hardened.
4 are integrally assembled via screws that tighten when torque is transmitted. Each synchronized disk 4
3 and 44 are provided with polished inward friction conical surfaces 43A and 44A, and a clutch pawl 4 is provided on the inner peripheral side of the inward friction conical surfaces 43A and 44A.
3B and 44B are provided.

A clutch dog 45 made of surface-hardened nickel chrome molybdenum casehardened steel is splined to the intermediate portion of the drive shaft 42 between the forward gear 37 support position and the reverse gear 39 support position so as to be slidable in the axial direction. has been done. The clutch dog 45 is remotely operated via a shift lever 46 and a shift fork 47, and can be selectively shifted from a neutral position to a forward position or a reverse position. On the sliding surface between the drive shaft 42 and the clutch dog 45, a spring 49 inserted into a through hole 48 formed in the drive shaft 42, a detent ball 50, and a spring 49 formed on the clutch dog 45 with which the detent ball 50 engages. Neutral, forward, and reverse positioning grooves 51
A dog positioning mechanism formed by A, 51B, and 51C is provided. Clutchdog 45
A forward gear 37 or a reverse gear 39 is provided on both end faces of the
Clutch pawls 43B,
Clutch pawls 52A, 52B that can mesh with 44B
is provided.

Synchronizing sleeves 53 and 54 on the forward and reverse sides, which are made of special aluminum bronze with good wear resistance, are spline-coupled to the outer periphery of both ends of the clutch dog 45 so as to be slidable in the axial direction. Each synchronizing sleeve 53, 54 has an outward friction conical surface on its outer periphery, which is capable of fitting into the inward friction conical surfaces 43A, 44A integrated with the forward gear 37 or the reverse gear 39, and has an oil groove formed therein. 53A and 54A are provided.

As shown in an enlarged view in FIG.
5A, 55B are formed, and each accommodation groove 55A, 55
B accommodates piston ring-shaped synchronization rings 56A and 56B made of special cast iron as linking means as shown in FIG. The synchronization rings 56A, 56B are connected to the housing groove 5 through a wide contact portion extending over the entire circumference between the planar support surfaces 57 formed on both sides and both inner surfaces of the housing grooves 55A, 55B.
5A and 55B can be accommodated and supported in a stable state. Further, the outer periphery of the synchronization rings 56A, 56B is a locking surface 58 having an arc shape in the cross section,
The locking surface 58 is elastically locked in a ring-shaped locking groove 59 formed on the inner peripheral surface of the synchronizing sleeves 53 and 54, and the synchronizing sleeves 53 and 54 are aligned in the axial direction with respect to the clutch dog 45. It can be held in position. A slope 60 connected to one side of the locking groove 59 is formed on the inner circumferential surface of the synchronization sleeves 53 and 54.
The synchronizing ring 56A, 5 under an axial load above a predetermined value
6B is movable from the locking groove 59 toward the slope 60, and the locking state of the synchronizing rings 56A and 56B with the locking groove 59 can be smoothly released. That is, the clutch dog 45 and the synchronizing sleeves 53, 54
Due to an axial load of a predetermined value or more acting between
It is possible to immerse yourself inside A and 55B. Note that the synchronization rings 56A, 56B cannot be moved from the locking groove 59 in the opposite direction to the slope 60.

Further, a support shaft 61 is fixed to the upper case 31 in a position parallel to the drive shaft 42 . A shift slide 62 is coupled to the support shaft 61 so as to be movable in the axial direction.
Synchronous sleeves 53 and 54 on the forward and reverse sides
It is extended in the middle of the The shift slide 62 moves the detent ball 64, which is biased by the spring 63, to three positions: an intermediate positioning groove 65A, a front positioning mechanism 65B, and a rear positioning groove 65C, which are provided at three positions in the axial direction of the support shaft 61. It is now possible to stop. shift slide 62
When the clutch dog 45 is shifted from the neutral position to the forward or reverse position, the synchronizer that is integrated with the clutch dog 45 through the locking between the synchronizer rings 56A, 56B and the locking groove 59 on the reverse or forward side. Through contact with the end surfaces of the sleeves 53 and 54, it is movable from the intermediate position to the front position or the rear position. In addition, the shift slide 62
, when the clutch dog 45 is shifted from the forward position to the neutral position, the synchronizing rings 56A, 56B are placed on the slope 60 side, and the forward side or synchronizing sleeves 53, 54 are disconnected from the clutch dog 45 in the normal position. each synchronizing sleeve 5 against the clutch dog 45 through contact with the end face of
By relatively moving the synchronizing sleeves 53 and 54, the synchronizing rings 56A and 56B are moved relative to the slope 60 and locked in the locking grooves 59, and the synchronizing sleeves 53 and 54 are moved relative to each other.
in the correct position relative to the clutch dog 45, and then in this way the synchronizing sleeves 53, 5, which move integrally with the clutch dog 45,
It is movable from the front position or the rear position to the intermediate position through contact with the end face of No. 4.

Next, the operation of the above embodiment will be explained. When the clutch dog 45 is switched from the neutral position shown in FIG. 3 to the forward position, the synchronizing ring 5
6A and the locking groove 59, the synchronizing sleeve 53 moves forward together with the clutch dog 45. The clutch dog 45 moves forward, and the outward friction conical surface 53A of the synchronizing sleeve 53 engages the forward gear 37.
When the shift operation force acting on the shift fork 47 is strengthened after the inward friction cone surface 43A is fitted into the inward friction cone surface 43A, the outward friction cone surface 53A and the inward friction cone surface 43A are initially Although they slide against each other, in the close contact state shown in FIG. 7A, the two can rotate synchronously due to frictional force. Under the condition shown in FIG. 7A, in which the outward friction conical surface 53A is in close contact with the inward friction conical surface 43A, the clutch dog 45 is integrated with the shift slide 62 located in the intermediate positioning groove 65A. The end faces of the synchronizing sleeve 54 on the reverse side come close to each other through a small gap. When the shift operation force acting on the shift fork 47 becomes stronger from the state shown in FIG.
5A, the locking surface 58 of the synchronizing ring 56A is released from the locking state of the locking groove 59 and moves toward the slope 60, and the clutch dog 45 moves one step further, as shown in FIG. 7B. , the detent ball 50 moves from the neutral positioning groove 51A to the forward positioning groove 51B, the clutch pawl 52A meshes with the clutch pawl 43B, and the rotational force of the forward gear 37 is reliably transmitted to the drive shaft 42, causing the drive shaft 42 to move forward. Make it rotatable. In the state shown in FIG. 7B, the shift slide 62 is pushed forward through the contact between the shift slide 62 and the end surface of the synchronization sleeve 54 on the reverse side, which advances integrally with the clutch dog 45. After being moved, the shift slide 62 is transferred from the intermediate positioning groove 65A to the front positioning groove 65B.
The synchronizing sleeve 5 rotates on both sides while remaining in the front positioning groove 65B.
It stands still with a slight gap between it and the end faces of 3 and 54.

When the clutch dog 45 is switched from the forward position shown in FIG. is the forward positioning groove 51B
As shown in FIG. 3, it is transferred to the neutral positioning groove 51A, and power transmission from the forward gear 37 to the drive shaft 42 is cut off. Here, the synchronization sleeve 53
By pushing the slope 60, the synchronizing ring 56A moves relative to the clutch dog 45, and by resiliently engaging the synchronizing ring 56A in the locking groove 59 again, it is brought to the normal position where it is integrated with the clutch dog 45. Return. In this case, the clutch dog 45 and the synchronizing sleeve 53 are arranged as shown in FIG. 7B.
When the synchronizing ring 56A moves integrally while remaining on the slope 60 side, the shift slide 62 comes into contact with the end surface of the synchronizing sleeve 53, as shown in FIG. 53
After preventing free movement and moving only the clutch dog 45, the synchronizing ring 56A is moved from the slope 60 side and is locked in the locking groove 59, thereby ensuring that the synchronizing sleeve 53 returns to its normal position relative to the clutch dog 45. possible. In addition, the shift slide 62
When the clutch dog 45 and the synchronizing sleeve 53 are further retreated from the state shown in FIG.
B to return to the intermediate positioning groove 65A, and the original state shown in FIG. 3 is reached.

Note that when the clutch dog 45 is switched from the neutral position to the reverse position, the reverse gear 39 is
A synchronous meshing operation between the drive shaft 42 and the drive shaft 42 is achieved. In addition, in this case as well, the shift slide 62
and the interaction with the synchronizing sleeves 53 and 54 to ensure that the synchronizing sleeve 54 returns to its normal position relative to the clutch dog 45 after the synchronizing operation is completed,
It is possible to always achieve normal synchronous meshing motion.

According to the above embodiment, after the forward gear 37 or the reverse gear 39 and the drive shaft 42 are synchronized, the clutch pawls 43B and 44B integrated with the forward gear 37 or the reverse gear 39 and the clutch dog 4
Since the clutch pawls 52A and 52B of No. 5 engage with each other, it is possible to smoothly engage and disengage the clutch without causing a large impact or stopping the engine due to the impact. Furthermore, synchronization rings 56A and 56B serve as linking means for integrating the clutch dog 45 and the synchronization sleeves 53 and 54 under a predetermined axial load.
However, it is shaped like a piston ring and the clutch dog 45
The synchronizing rings 56 are accommodated in the ring-shaped accommodation grooves 55A, 55B formed in the ring-shaped accommodation grooves 55A, 55B, and both sides of the synchronizing rings 56A, 56B can be supported on the inner surfaces of the accommodation grooves 55A, 55B via wide contact surfaces.
A, 56B do not wobble in the housing grooves 55A, 55B, and the operating state thereof can be stabilized. Further, since it is sufficient to form the ring-shaped accommodation grooves 55A and 55B only on the outer circumference of the clutch dog 45, its strength is not significantly impaired. The clutch dog 45 also includes single synchronization rings 56A and 56 on the forward and reverse sides.
By assembling B, a linking means for integrating the clutch dog 45 and the synchronizing sleeves 53, 54 can be obtained, making it possible to perform the assembly work easily. Also, Clutchdog 45
When shifting from the forward position or reverse position to the neutral position, the shift slide 62 engages the synchronizing sleeve 5.
3 and 54, and the synchronizing sleeves 53 and 54 can be corrected to their normal positions relative to the clutch dog 45, so that it is possible to always ensure normal synchronized meshing operation.

In the above embodiment, a case has been described in which the forward/reverse switching device for a marine vessel propulsion device according to the present invention is disposed inside the upper case of an inboard/outboard motor. It can also be applied to outboard motors, and may also be arranged between the drive shaft and propeller shaft in the lower case.

As described above, according to the present invention, it is possible to obtain a forward/reverse switching device for a marine vessel propulsion device having a synchronized meshing mechanism with stable operability, high strength, and good ease of assembly. .

[Brief explanation of drawings]

Fig. 1 is a partially cutaway side view of the outer drive unit of a general inboard/outboard motor, Fig. 2 is a sectional view showing a conventional forward/reverse switching device for a marine propulsion engine, and Fig. 3 is a side view of the outer drive unit of a general inboard/outboard motor. FIG. 4 is a cross-sectional view taken along the line - in FIG. 3, and FIG. 5 is an enlarged view of the main parts of the same embodiment. 6 is a side view showing the synchronizing ring taken out in the same embodiment, and FIGS. 7A, B, and C are sectional views showing different operating states of the same embodiment. 33...Input gear, 34...Input shaft, 37...
Forward gear, 39... Reverse gear, 42... Drive shaft, 43, 44... Synchronous disk, 43A, 44
A... Inward friction conical surface, 43B, 44B... Clutch pawl, 45... Clutch dog, 52A, 52
B...Clutch pawl, 53, 54...Synchronizing sleeve, 53A, 54A...Outward friction conical surface, 55
A, 55B...accommodating groove, 56A, 56B...synchronization ring, 59...locking groove, 60...slope.

Claims (1)

[Claims] 1 Each gear meshes with the input gear fixed to the input shaft, has an inward friction conical surface on the inner periphery of the meshing teeth, has a clutch pawl on the inner periphery of the inward friction cone surface, and is attached to the drive shaft. The forward gear and the reverse gear, which are rotatably supported and rotate in opposite directions, are slidably engaged in the axial direction between the forward gear shaft support position and the reverse gear shaft support position of the drive shaft, and are neutral. A clutch dog with clutch pawls on both end surfaces that can be selectively shifted from a forward position to a forward position or a reverse position and can engage with a clutch pawl of a forward gear or a reverse gear, and a clutch dog that is slidable in the axial direction on the outer periphery of both ends of the clutch dog. The synchronizing sleeves on the forward and reverse sides each have an outward friction conical surface that can be engaged with the inward conical friction surface of the forward gear or the reverse gear, and are formed on the outer periphery of both ends of the clutch dog. Each synchronization ring on the forward and reverse sides is accommodated in the ring-shaped accommodation groove and resiliently engages in the ring-shaped locking groove formed on the inner circumferential surface of each synchronization sleeve. A forward/reverse switching device for marine propulsion equipment.