JPH0328097A - Outboard engine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention [Objective of the Invention] <Industrial Application Field> The present invention is directed to a movable bracket and a movable bracket that are pivotally supported via a tilt axis to a fixed bracket that is fixed to a ship's hull. This invention relates to an outboard motor that is swingably supported by a swivel shaft.

<Prior art> In a conventional outboard motor, the casing supporting the engine is swingably supported by a movable bracket and a swivel shaft that are pivotally supported via a tilt shaft to a fixed bracket fixed to the hull. something is known. In this outboard motor, the casing is designed to prevent engine vibrations from being transmitted to the hull and to ensure sufficient transmission of propulsion force.
It is preferable to elastically support the shock absorber with a relatively small spring constant in order to absorb engine vibrations and a relatively large spring constant in the direction in which a large propulsive force is received via a shock absorber having an elastic body.

For example, in Japanese Patent Application Laid-Open No. 59-120597, both free ends of two left and right bolts are provided as support members extending in the form of arms from a swivel shaft supported by a swivel bracket toward a casing that supports the engine. A connecting member is spanned between the parts in a direction penetrating the casing left and right, that is, in a direction transverse to the direction of the propulsion force, and the casing is elastically supported via an elastic body fixed to the outer periphery of the connecting member. Disclosed. In this outboard motor, the propulsion force is supported by compressive deformation of the elastic body between the casing and the connecting member, and the vibration around the main axis of inertia on the casing side due to engine torque fluctuations is supported by the elastic body. It is absorbed by shear deformation of the body.

By the way, in response to engine vibrations, it is desirable to provide elastic support as close as possible to the main axis of inertia. However, according to the above structure, since the connecting member is spanned between both free ends of the two left and right bolts, it is necessary to take into consideration interference with structures inside the casing, such as the drive shaft, and this is not disclosed. In this case, an elastic body fixed to the outer periphery of the connecting member is provided between the front surface of the casing in the propulsion direction and the swivel bracket, and compared with the main axis of inertia that passes approximately in the center of the casing in the vertical direction. Since the casing is supported at distant positions, there is a problem in that it is difficult to absorb engine vibrations appropriately.

<Problems to be Solved by the Invention> In view of the problems of the prior art, the main object of the present invention is to provide an outboard structure that can elastically support the casing supporting the engine as close as possible to the main shaft of inertia. The aim is to provide the opportunity.

[Structure of the Invention] Means for Solving the Problems According to the present invention, the present invention provides a casing means for receiving a drive shaft and supporting an engine, and a fixed bracket means fixed to a hull. , a ship comprising movable bracket means pivotally supported by the fixed bracket means via a tilt shaft, swivel shaft means pivotally supported by the movable bracket means, and means for supporting the casing means on the swivel shaft means. In the external engine, the support means includes first and second arm-shaped support members protruding rearward from the swivel shaft means so as to pass at least on both sides of the drive shaft; first and second shock absorbers each consisting of a first and second rigid body fixed to the free end of each support member, and first and second elastic bodies attached to at least the rear surface of each of the rigid bodies; It has a support surface facing each of the rigid bodies of each of the buffer bodies behind each of the elastic bodies of each of the buffer bodies, and first and second recesses provided on the side surface of the casing means. This is achieved by providing an outboard motor characterized by the following.

<Function> In this way, the support position of the shock absorber can be moved as close as possible to the rear of the drive shaft, that is, the main axis of inertia of the casing, and at least in the forward direction where the maximum load is applied, the shock absorber is compressively deformed. The casing can be suitably and elastically supported by shear deformation against vibrations in the left-right direction around the main axis of inertia due to engine torque fluctuations.

<Embodiments> Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 shows the entire outboard motor 1 to which the present invention is applied, and the outboard motor 1 is fixed to a stern plate (not shown) of the hull via a vise-type stern bracket 2 as a fixing bracket means. be done.

A swivel case 4 is attached to the stern bracket 2 so as to be rotatable around a tilt axis 3 disposed in the horizontal direction.
A cylindrical hole having an axis in a direction perpendicular to the tilt axis 3 is formed in the swivel case 4, and a pair of bearings (not shown) are installed in the inner holes at both ends of the cylindrical hole in the axial direction. A swivel shaft 10, which is provided internally and is rotatable relative to the swivel case 4 via these bearings, is fitted into the cylindrical hole.

At the upper and lower shaft ends of the swivel shaft 10 that protrudes from the swivel case 4 in the vertical direction in the figure, upper and lower support brackets 5 and 6 as movable bracket means extend rearward in a direction orthogonal to the axis of the swivel shaft 10. An extension case 8 serving as a casing means for housing the drive shaft 7 of the outboard motor 1 is supported at the free ends of the support brackets 5 and 6 via a buffer means. Also,
From the upper end of the swivel case 4 are the support brackets 5 and 6.
A steering handle par 9 extending in the opposite direction is integrally fixed to the swivel shaft 10, and by operating the steering handle par 9, the hull can be rotated around the swivel case 4, that is, the swivel shaft 10. The outboard motor 1 is configured to swing left and right with respect to the direction of travel.

Above the extension case 8 connected to the stern plate as described above, an engine 12 whose entire body is covered by an engine case 11 is mounted, and below a gear case 14 that pivotally supports a propeller 13 is fixed. There is.

When the propeller 13 generates a propulsive force in the forward direction, for example, to the left in the figure, the support bracket 5 receives a force so as to be pulled rearward, to the right in the figure, and the lower support bracket 6 In order to receive a force to be pushed forward, the force in both directions is received through an elastic body made of vibration isolating rubber or the like as a buffer means.

Incidentally, in order to prevent vibrations caused by torque fluctuations of the engine 12 from being transmitted to the hull, the lower support bracket 5 absorbs the vibrations. As shown in FIG. 2, the lower support bracket 5 is fixed to a cylindrical swivel shaft 10 by spline connection to constitute swivel shaft means. Lower support bracket 5
, there are first and second arm-shaped cylindrical arms that project parallel to each other toward the rear from the bracket body that is shaped to project symmetrically on both sides of the swivel shaft 10. A pair of left and right support arms 15 as support members
a and 15b are integrally formed.

A hole 8a is formed in the center of the extension case 8 and extends vertically to receive the drive shaft 7. A pair of support arms 15a, 15b are extended,
Each free end is positioned near the main axis of inertia 17 of the extension case 8 which is rearward of the drive shaft 7. In addition, a third
As best shown in the figure, each pair of support arms 15
a and 15b are arranged vertically in parallel at intervals, and there are a total of four, two on the left and two on the left.

Each support arm 1 is attached to the front of the extension case 8.
Insertion holes 16a, 16b and notches 19a, 19b are formed to surround the intermediate portions of the arms 5a, 15b with a predetermined gap, and a pair of left and right support arms 15a are formed.
．． The first shock absorbers 20a and 120b, which will be described later, are attached to the upper and lower free ends of the buffer member 15b.
Second recesses 18a and 18b are respectively provided in the left and right side surfaces of the extension case 8 so as to open symmetrically with each other.

At the free ends of the left and right support arms 15a, 15b, which form a pair in the upper and lower sides, there are connecting members 22a, 22b, each having a prismatic shape and serving as a rigid body, for connecting the two free ends. The arms 15a and 15b are fixed by screwing mounting bolts 21a and 2lb inserted through the axial holes of the swivel shaft 10 from the swivel shaft 10 side. Each connecting member 22
In the intermediate part of a and 22b, there is an elastic body 23a, which is made of anti-vibration rubber or the like and has a rectangular cross section, as described above.
The elastic bodies 23a, 23b are integrated with the connecting members 22a, 22b by, for example, baking, as shown in FIG. , left and right buffer bodies 20a and 20b are configured as first and second buffer bodies.

Further, the intermediate portion of each recess 18a, 18b is connected to the support arm 1.
It is formed to swell slightly more than the upper and lower portions that receive the free ends of 5a and 15b, and the elastic bodies 23a and 23b are received in the swollen portions in a compressed state. In this way, the connecting members 22a, 22b, ie the support arm 15a
．． 15b and the extension case 8 are the buffer body 20.
They are connected to each other via a and 20b, and the two are integrally coupled together elastically.

A forward support surface 33 facing the forward direction of the recesses 18a, 18b
a, 33b and rearward supporting surfaces 18b, 19 facing the reverse side
b, the corresponding elastic bodies 23a, 23b, that is, the front and rear surfaces of the shock absorbers 20a, 20b, are closely and sandwiched over the entire surface, and the left and right concave portions 18a, 18b hold the left and right shock absorbers 20a, 20b. is supported. Each recess 1
The opening surface of 8a118b is closed by left and right covers 24a and 24b fixed to both side surfaces of the extension case 8 by, for example, bolts.

Recesses 18a of these covers 24a, 24b. The inner surface corresponding to the opening surface of 18b and the cover 2 of recesses 18a and 18b
Buffer bodies 20a, 2 are provided on the wall facing 4a, 24b.
The covers 24a and 24b are arranged so as to define predetermined gaps between the elastic bodies 23a and 123b on the left and right sides of the cover 0b.
The recessed portion 25a125b on the side and the four recessed portions 26a and 26b on the side of the recessed portions 18a and 18b are respectively recessed.

Historically, as shown in FIG. 3, the elastic bodies 23a, 2
3b has its upper and lower peripheral edges aligned with the recesses 18a, 18b so as not to shift in the vertical direction relative to the recesses 18a, 18b.
The extension case 8 is supported by the upper and lower edges of the above-mentioned bulge of the elastic body 8b, but since most of the upper and lower end surfaces of the elastic bodies 23a and 23b are open in the vertical direction, the extension case 8 does not vibrate in the vertical direction. If this occurs, the elastic bodies 23a and 23b can be sheared and deformed in the same direction, making it possible to suitably absorb vertical vibrations in the lower support bracket 6.

A shift rod 27 for selectively switching gears in the gear case 14 when moving forward or backward is received in the swivel shaft 10 having a cylindrical shape, passing through it in the axial direction. As shown, a water supply pipe 28 for supplying cooling water to the engine 12 is received in an inner hole formed to extend vertically behind the hole 8a of the extension case 8. . A damper 29 made of a hard rubber material, for example, is fixed to the front end face of the extension case 8 and has a rectangular block shape, and a convex stopper 30 is provided on the face of the swivel case 4 facing the damper 29. It is provided.

The construction of the outboard motor constructed in this manner will be described below.

The forward propulsive force generated by the propeller 13 acts in the left direction in FIGS. 2 and 3, but in this case,
Since the elastic bodies 23a, 23b are compressively deformed between the forward supporting surfaces 33a, 33b facing the forward direction of each recess 18a, 18b and each connecting member 22a, 22b, the elastic bodies 23a, 23b are supported with a relatively large spring constant. This increases the load capacity for propulsive force.

In addition, as described above, in the direction of vibration around the main shaft of inertia 17 due to torque fluctuations of the engine 12, the recesses 18a, 18b of the extension case 8 and the cover 24a
, 24b, and 24b.
A gap is provided between the corresponding left and right surfaces of the shock absorbers 20a and 20b. Therefore, most of the vibration is absorbed by the elastic bodies 23 on the left and right sides of the shock absorbers 20a, 20b.
Regardless of the compressive deformation of a, 23b, the elastic bodies 23a, 23b
It can be supported with a relatively small spring constant due to the shear deformation of the part that is compressively deformed when receiving the above-mentioned propulsive force, and the vibrations mentioned in 2 can be suitably absorbed.

Furthermore, if some large external force is applied around the main axis of inertia 17, the recesses 25a, 25b, 26a, 26
The elastic bodies 23a, 23b abut against the bottom surface of b, and the abutted portions of the elastic bodies 23a, 23b are compressed and deformed.
-L The load capacity against the external force is increased, and excessive shearing deformation of the elastic bodies 23a, 23b can be suitably prevented.

Furthermore, even in the case of vibrations in the vertical direction, since the vertical end surfaces of the elastic bodies 23a, 23b are open as described above, the vibrations can be sufficiently absorbed by the shear deformation of the elastic bodies 23a, 23b. . Furthermore, each support arm 1
Since the support members 5a and 15b are each composed of a pair of arm-shaped support members arranged vertically and spaced apart from each other, they have high rigidity against large external forces acting in the vertical direction. Also,
When a large force is applied in the direction of propulsion during forward movement, the damper 29 comes into contact with the stopper 32, so that excessive deformation of the elastic bodies 23a and 23b can be similarly prevented.

In this embodiment, the elastic bodies 23a and 2 of the recesses 18a and 18b are
The forward supporting surfaces 33a, 33a that come into contact with the main axis of inertia 3b are made to roughly coincide with the plane passing through the main axis of inertia 17, and since they elastically support a position extremely close to the main axis of inertia 17, vibrations around the main axis of inertia are suppressed. Can be absorbed well.

FIG. 5 is a diagram showing a modified embodiment of the elastic body. In this modified embodiment, concave portions 32 are formed on the left and right surfaces of the elastic body 31 on the side that absorbs vibrations around the main axis of inertia 17. It is set up. In this case, the recess 1 of the extension case 8
There is no need to provide recessed portions in the opposing portions of the covers 8a, 18b and the cover 24a, 24b, and the same effects as in the previous embodiment can be achieved.

FIG. 6 shows a second embodiment based on the present invention, and parts corresponding to the previous embodiment are given the same reference numerals and detailed explanation thereof will be omitted.

At the front of the extension case 8, first and second recesses 42a and 42b, which are symmetrical to each other, are provided on the left and right sides, opening on the left and right sides and the front of the extension case 8, respectively, and opening the arms. Left and right support arms 41 as first and second support members shaped like
It is shaped so as to receive the free end portions of a and 41b in a recessed state and with a gap between them. Each support arm 41
a, 4lb are lower support brackets 6 as swivel shaft means so as to pass on both sides of the drive shaft 7 located in the center of the extension case 8, as in the previous embodiment.
The main axis of inertia of the extension case 8 is located at the rear of the drive shaft 7, and each free end extends rearward from the bracket main body, which is formed to project symmetrically on both sides of the swivel shaft 10. 17.

The free ends of the support arms 41a, 4lb are provided with flange bodies 44a, 44 as rigid bodies having surfaces perpendicular to the direction of the propulsion force.
b is an annular boss portion 45a protruding toward the front thereof;
45b, mounting bolts 43a, 43 are inserted into the axial holes of the support arms 41a, 41b from the swivel 10 side.
It is fixed by screwing b. As described above, rectangular block-shaped elastic bodies 48a and 48b made of anti-vibration rubber are fixed to the rearward flange surfaces of each of the seven flange bodies 44a and 44b, for example, by baking. Rear surface 49 of each elastic body 48a, 48b
a, 49b, flange bodies 47a, 4 made of rigid bodies forming a flat plate so as to face the flange bodies 44a, 44b.
7b is similarly fixed. Flange bodies 47a, 47
As shown in FIG. 7, the lower ear-shaped portions of the recesses 42a and 42b are bolted to walls 46a and 46b, which serve as support surfaces facing the forward direction. There is.

In this way, as shown in FIG.
Buffer bodies 50a, 50b are constructed by integrally sandwiching elastic bodies 48a, 48b between opposing flange bodies 4a, 44b and flange bodies 47a, 47b. The support arms 41a, 4lb and the extension case 8 are connected to each other via buffers 50a, 50b, and are elastically integrally connected.

As described above, a pair of upper and lower annular boss portions 51a and 5lb are provided on the left and right side surfaces of the wall of the extension case 8 surrounding the drive shaft 7 so as to avoid the support arms 41a and 4lb, respectively. and each recess 42a, 4
The left and right covers 52a are fixed to the left and right outer wall surfaces of the extension case 8 and the respective annular boss portions 51a and 5lb by bolts, for example.
, 52b, respectively.

Further, since the upper and lower end surfaces of the elastic bodies 48a and 48b are open in the vertical direction, when the extension case 8 generates vibration in the vertical direction, the elastic bodies 48a
, 48b between both flange bodies 44a and 47a, and 44
Since shear deformation can occur between b and 47b, the vibration can be sufficiently absorbed.

In addition, the support arm 41a, the flange body 44a on the 4lb side,
As clearly shown in FIG. 8, a pair of left and right rod-shaped damper members 53a and 53b made of, for example, hard rubber are fixed to the front end face of the damper 44b in parallel with each other. When a propulsive force is generated in the backward direction, the elastic bodies 48a, 4
8b is between both flange bodies 44a and 47a, and 44b,
Each cover 52b is tensilely deformed and receives a propulsive force in that direction, but if a larger propulsive force occurs, each cover 52
At the rear sides of the ribs 54 a, 54 b protruding into the respective recesses 42 a 142 b on the inner surfaces of the ribs 54 a, 52 b, respectively, and at the rear wall surface of the portion surrounding the drive shaft 7 of the extension case 8, Opposing damper member 53
a and 53b are in contact with each other.

In this way, elastic stopper means is provided to prevent excessive tensile deformation of the elastic bodies 48a, 48b.

Even in the second embodiment constructed in this way, when the forward thrust generated by the propeller 13 acts in the left direction in FIGS. 6 and 7, the wall surfaces 46a and 46b
flange bodies 47a, 47b fixed to the support arms 41a, 4lb, and flange bodies 44a, 44b fixed to the support arms 41a, 4lb.
Since the elastic bodies 48a and 48b sandwiched between the two are compressively deformed, they can be supported with a relatively large spring constant, and the load capacity against the propulsive force is large.

In addition, for the direction of vibration around the main shaft of inertia 17 due to torque fluctuations of the engine 12, each flange body 44a, 44b
47a and 47b move in parallel in opposite directions, so that the elastic bodies 48a and 48b are sheared and deformed in the vibration direction, and the vibrations have a relatively small spring constant. can be absorbed sufficiently. Also, since the two downward end faces of the elastic bodies 48a, 48b are released as described above, the elastic bodies 48a, 48b are free from vibration in the vertical direction.
The vibration can be sufficiently absorbed by the shear deformation of 8b.

Note that when a large force is applied in the forward direction, the elastic body 4 is moved by the stopper 30 and the damper 29 as in the previous embodiment.
Excessive deformation of 8a and 48b can be prevented. Furthermore, the flange surfaces 55a and 155b of the flange bodies 47a and 47b that support the elastic bodies 48a and 48b and the plane passing through the principal axis of inertia 17 are made to substantially coincide with each other, and as in the previous embodiment, vibrations around the principal axis of inertia are prevented. can be properly absorbed.

Further, the first embodiment can be applied to both the upper support bracket 5 and the lower support bracket 6, and the second embodiment is relatively easy to assemble.

[Effects of the Invention] As described above, according to the present invention, the casing supporting the engine has a large spring constant due to compressive deformation of the elastic body in the longitudinal direction of the propulsion force, and is thus resistant to vibrations in the left and right directions around the main axis of inertia. By elastically supporting the area very close to the main axis of inertia with a small spring constant due to shear deformation, it is possible to suitably absorb vibration while ensuring a large load capacity for propulsive force. The effect is extremely large.

[Brief explanation of drawings]

FIG. 1 is a diagram showing the entire outboard motor to which the present invention is applied. FIG. 2 is a sectional view of the main part taken along line 1-1 in FIG. 1. FIG. 3 is a cross-sectional view of the main part taken along the line ■-■ in FIG. 2. FIG. 4 is a perspective view showing the buffer. FIG. 5 is a perspective view showing a modified embodiment of the buffer body. FIG. 6 is a diagram similar to FIG. 2 showing a second embodiment according to the invention. FIG. 7 is a cross-sectional view of the main parts taken along the line ■-■ in FIG. 6. FIG. 8 is a perspective view showing the buffer body of the second embodiment. 1... Outboard motor 2... Stern bracket 3... Tilt axis 4... Swivel case 5.
... Upper support bracket 6 ... Lower support bracket 7 ... Drive shaft 8 ... Extension case 8a ... Hole 9 ... Steering handlebar 10 ... Swivel shaft 11 ... Engine case 1
2...Engine 13...Propeller 14...
Gear cases 15a, 15b... Support arms 16a, 16b... Insertion hole 17... Main shaft of inertia 18a, 18b... Recessed portion 1
9a, 19b...Notch portion 20a120b...Buffer body 21a, 2lb...Mounting bolt 22a, 22b...Connection member 23a123b...Elastic body 24 a, 24b-fy<- 25a, 25b...・Recessed portions 26a, 26b ・I! J installation part 27... Shift rod 28... Water supply pipe 29...
Damper 30... Stopper 31... Elastic body
32... Recessed portions 33a, 33b... Forward supporting surfaces 34a, 34b... Rearward supporting surfaces 41a, 41b- = Support arms 42a, 42b- = Recessed portions 43a, 43b... Mounting bolts 44a, 44b. ...Flange bodies 45a, 45b...Annular boss portions 46a, 46b...Wall surfaces 47a, 47b...Flange bodies 48a, 48b...Elastic bodies 49a, 49b...Rear surface 50a1 51a, 51b... Annular boss portions 52a, 52b...Cover 53a, 53b...Damper member 50b...Buffer body 54a, 54b- = Rib 55a, 55b...Flange surface Fig. 1 Patent Applicant: Honda Motor Co., Ltd. Company fee
Attorney Patent Attorney Yoichi Oshima 12

Claims (1)

[Claims] (1) Casing means for receiving the drive shaft and supporting the engine, fixed bracket means fixed to the hull, movable bracket means pivoted to the fixed bracket means via a tilt shaft, and the movable bracket means In an outboard motor having a swivel shaft means pivotally supported by the swivel shaft means, and means for supporting the casing means on the swivel shaft means, the support means passes at least on both sides of the drive shaft. arm-shaped first and second support members protruding rearward from the swivel shaft means; first and second rigid bodies respectively fixed to free ends of the respective support members; and at least one of the respective rigid bodies. first and second shock absorbers each including a first and second elastic body attached to a rear surface, and facing each of the rigid bodies of each shock absorber behind each of the elastic bodies of each shock absorber; An outboard motor comprising a support surface and first and second recesses provided in a side surface of the casing means.