JPH0251796B2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention is applicable to outboard motors and Z-type drive devices (Z-drive).
It relates to an outboard drive system, such as the part located outboard of an outboard motor called an outboard motor.

These outboard drives can be balanced, trimmed and tilted by remote control from the cockpit.
tilting) and mounting the hydraulically actuated cylinder-piston assembly on the outside of the outboard drive casing;
And it is well known to be used to move outboard drives in locations that do not change location.

The object of the invention is to provide a remote control, motor-driven counterbalancing and tilting of an outboard drive with a particularly simplified construction and protection of the moving parts against environmental influences.

In order to achieve the object of the present invention, a tilting device is housed within the casing of the outboard drive device, and steering and tilting are performed by remote control from inside the boat. This eliminates the need for major changes to the interior and stern of the boat, unlike conventional outboard motors, and the structure inside and outside the stern is further simplified. In addition, all important moving parts are housed within the casing, making it difficult for them to be affected by external influences.

The invention is characterized by the specific features set out in the appended claims. "Front"
Terms such as "forward", "aft", "aft", etc. are always understood in the detailed description and claims in the normal direction of travel of the ship.

Embodiments of the invention will now be described in detail with reference to the accompanying schematic drawings.

Functionally corresponding parts are designated by like reference numerals in the accompanying drawings.

According to FIG. 1, a transverse steering shaft means in the form of a rudder post 30 is attached to a transom 10a of a ship 10 by two bearings 3 vertically aligned with each other and spaced apart by a certain distance.
Pivotally attached to 1 and 32. The rudder handle 3 is attached to the upper end of the rudder post.
3 is fixedly attached and its forward end 33a is coupled to a remote control mechanism, not shown.

An outboard motor 20 having a casing 20A and a screw 11 is suspended on a rudder post 30 by a means that allows it to tilt around a horizontal axis H of a first journal 34 (see FIG. 2). The journal 34 defines a tilting shaft means for the outboard motor. Two elongated rigid support arms 36 of non-variable length pivot at their forward ends to a second journal 35 defining a hinge axis means and spaced from the first journal 34 of the rudder post 30. Each one is arranged on either side of the rudder post 30 and the casing 20A for movement.

In each side wall of the casing 20A is an elongated linear slot 25 having a length L and arranged to extend at least generally in the direction of travel when the outboard motor is in its normal drive position. The support arm 36 is connected to the casing 20A at its rear end.
They are interconnected by connecting means in the form of a straight rod 24 passing through both slots 25 suitably passing through. The connecting rod 24 is dimensioned so that it can move freely within the slot 25 along its length.

The connecting rod 24 cooperates with the piston 22 of a hydraulically actuated cylinder-piston assembly which further includes a cylinder 21 fixedly mounted to the outboard motor 20 within the casing 20A.
It engages with the half-moon part 23b attached to the end of 3.
The half moon 23b defines an engagement means for the connecting rod 24 and is permanently pressed against this rod by the drag effect created when the screw 11 propels the ship in the forward direction intended by arrow A. Cylinder-piston assemblies 21-23 are supplied from a source of pressurized fluid 39. The liquid source 39 is sequentially operated from the cockpit by a remote control operation means 48 (not shown).

When actuated by the operating means, the piston 22 is moved within the cylinder 23 in the direction intended by arrow A, and the connecting rod 24 is moved in the slot 25 with respect to the outboard motor 20 (and not with respect to the support arm 36). Desired position or forward limit position 24'
will be moved to. The connecting rod 24 is connected to the support arm 36
Since the hinge shaft means 35 is mounted at a non-variable distance from the hinge shaft means 35, movement of the applied position of the connecting rod of the outboard motor 20 results in the outboard motor tilting upwardly and the connecting rod 34 being centered on the second journal 35. and performs a circular movement along a circle C ₁ of radius r ₁ ' corresponding to the non-variable effective length of the support arm 36.

The final position of the connecting rod 24 with respect to the ship 10 is a second rod centered on the first journal 34 and having a radius r ₂ corresponding to the spacing between the connecting rod 24 and the first journal 34 in its final position. Determined by the intersection of circle C ₂ and circle C ₁ .
In the illustrated example, this final position is F, where the effective coupling rod 24' is located when the outboard motor 20 is fully tilted up. Thus, to lift the outboard motor, the connecting rod 24 is moved within the elongated slot 25 closer to the transom 10a.

As is apparent from FIG. 1, for each intermediate position of the connecting rod 24, a circle C ₁ is located closer to the support arm 36 than where the illustrated tip circle C ₂ intersects.
A circle similar to circle _C2 can be drawn intersecting C2, which means that the outboard motor can be tilted to any desired position between the position shown and the position where slot 25 passes through point F. With small movements of this kind it is therefore possible to adjust the balance of the outboard, i.e. to set the screw shaft angle, while
Maximum tipping movement raises the outboard motor 20 completely out of the water, such as during mooring (known as tipping).

As is well known, for outboard motors as well as the outboard parts of inboard and outboard motors, it must also be possible to swing up without any assistance when the ship during navigation hits an underwater obstacle. . Such an unaided tilting movement is achieved by attaching the connecting rod 24 to the piston rod 23 by the half-moon part 23b, so that the connecting rod 24 can move within the slot 25 even when the half-moon part 23b does not follow. do it like this.

FIG. 2 shows the invention in an outboard motor, or more precisely in an outboard part 40 thereof, in which components having similar functions as in FIG. 1 are given like reference numerals. Application examples are generally shown. The outboard portion is the rudder post 3 in Figure 1.
It is carried by a journal 34 of a one-piece rigid latching frame 30A which is pivoted in sequence on two bearings 31, 32 fixed to the transom of the ship by means similar to that of the stern beam of the ship. Latch frame 30A defines a lateral steering axis means having a lateral steering axis G, and journal 34 defines a tilting axis means having a tilting axis H, as previously described.

All functions are continuous from the inboard drive unit, not shown in FIG. 2, to the outboard portion through the central space of frame 30A and an opening in the ship's transom, not shown. For the sake of clarity, the drawing only shows the torque transmission from the output shaft 13 of the drive unit via the double universal joint 12 to the output shaft 43 of the outboard part 40.

It should be understood from a consideration of FIG. Since the piston 22 must be long enough to move through a stroke equal to the length L, a fairly large longitudinal dimension M (see FIG. 1) is required.

FIG. 2, however, shows that the connecting rod 24 is located in the slot 2 shown in FIG.
5 (see FIG. 5) is actually located at the rear end of the outboard section 40, which has an exhaust port 42 at the end of the cavitation suppressing plate 41. According to another embodiment of the invention, this means that:
This is possible by moving the coupling means into the slot 24 by means of a nut and screw assembly. This nut and screw assembly does not have to double its stroke length as is the case with cylinder-piston assemblies.

FIG. 3 shows details of the structure of an outboard motor similar to the outboard motor shown in FIG.

In the casing or prime mover housing 20A, a screw spindle 26 is rotatably mounted on a thrust bearing 16 and on a radial bearing 17 with the help of a thrust cover 15. Bearing 1
6 and 17 are fixedly attached to the casing 20A. A first gear 19 is fixedly mounted on the forward end of the screw spindle. The reversible electric motor 14 with the second gear 14a is also connected to the prime mover casing 20.
It is attached to A. The gears 14a and 19 mesh with each other, and the electric motor 14 is connected to the conductor 14 from the ship's cockpit.
remotely controlled via b.

The two support arms 36 of FIG. 1 are merged into an elongated rectangular support frame 36 so that they form two elongated sides. The front short side of the support frame 36A defines a hinge axis means and is pivotally connected to a bearing 35A fixedly attached to the rudder post 30.

The rear short side of the support frame 36A is separated and attached to a nut 27 threaded onto the screw spindle 16 at a pivot point 27a. Due to this connection with the support frame 36A, the nut 27 is prevented from rotating toward the screw spindle 26.

The entire length L is a slot 25 aligned with the prime mover housing or casing 20A through which the rear end side of the support frame 36A passes. Screw spindle 26, in the illustrated example, is located in a plane similar to support frame 36A (ie, in the plane of the drawing of FIG. 3). Protective and sealing bellows 26a, 26b, for example made of rubber, which are only partially shown in the drawing, extend axially on both sides of the nut 27.

The long sides of the support frame 36A are tubular in their rear portions 36A'' to allow for the unassisted heeling movement described in connection with FIG. 1 when the outboard motor strikes an underwater obstacle. It is removable so that it can be freely withdrawn from the front portion 36A'.It is clear that this removable construction does not counteract the fact that the support means are of non-variable length during normal forward navigation of the ship.

A pressure absorbing buffer 37 made of rubber, for example.
are provided between the long side of the frame 36a and the prime mover casing 20A to absorb lateral stresses, particularly during lateral steering, and/or for overall shock absorption purposes.

When the electric motor 14 rotates in one direction of rotation, the screw spindle 26 is screwed into the nut 27 in the direction of arrow B, and the thrust bearing 16 mounted on the motor casing 20A is rotated rearward (to the right in the figure). Being pushed forward. Because of the unique suspension system shown in FIG.
This causes a lift of 0. When the electric motor 14 rotates in the opposite direction, the screw spindle 26 is pulled out of the nut 27 in a direction opposite to arrow B and the outboard motor is lowered, to some extent by its own weight.

FIG. 4 shows an interchangeable arrangement of screw spindles 26 in an outboard section 40 of an outboard motor. In this case, the screw spindle is not mounted in the same plane as the support arm 36, but forms an acute angle with the rear portion of that arm. This position means that the definitive position for the invention in this respect is the attachment position of the connecting rod to the tilting part on the tilting or hinge axis H or L (journal 35 or 34).
It is suggested to state that it is possible to move forward from a rear limit position maximally distant from the front limit position to a forward limit position closer to these axes or journals. Upon completion of such forward movement of the coupling means, the tipping position 40' of the outboard portion is shown in phantom in FIG. 4. It should be noted that arranging the motor 14 alongside or parallel to the screw spindle 26, as shown in FIG. 4, does not require any increase in the length dimension of the device.

FIG. 5 shows an interchangeable embodiment of the outboard section 40 of an outboard/outboard motor with the cover of the casing 40A removed and the support arm 36 (see FIG. 1) removed. From Figure 5, the screw spindle 26
It is clear that the bellows (see FIG. 3) is completely enclosed in its front and rear protective bellows 26a, 26b. The electric motor 14 (see FIG. 3) is arranged in a housing 14c, and a reduction gear unit, not shown, is provided between its output shaft and the screw spindle. Prime mover housing 14
The housing 18 juxtaposed to c is an electrical component;
In particular, it contains relays and limit switches for the electric motor and one or more potentiometers for the cockpit.

Shock absorbing fasteners, such as rubber shock absorbers 38,
It is aligned with the forward end of the slot 25 to receive the connecting rod 24, especially when the portion 40 is suddenly lifted off by impact with an underwater obstacle. Buffer 3
8 may be attached to either the outboard section 40 or each of the support arms 36.

The support arm 36, which is of elongated hollow cross-section, has an opening 35' for the journal 35 and a connecting means 2.
A fitting 24a for 4A is provided. A damper 37 (for receiving lateral stresses) according to FIG. 3, similar to the clamping damper 38 described below, can be arranged inside its hollow arm 36.

It is clear from FIG. 5 that the lateral steering axis G can pass very close to the front end of the lateral stabilizer surface 40B (referred to as the "lateral") in the configuration according to the invention; As a result, lateral steering can be performed with relatively little force.

FIG. 6 has a locking groove 19a for the gear 19 (see FIGS. 3 and 4) and modified thrust and radial bearings 16', 17', by means of which the screw spindle 26 is connected to the outboard section 40. Alternatively, an interchangeable embodiment of the screw spindle 26 mounted on the outboard motor 20 is shown. The coupling means is in the form of a rigid yoke 24A with an arcuate central portion 24A' which straddles the screw spindle 26 or any other object similarly arranged in the casing of the outboard drive. At the rear stage, the connecting yoke 24A is connected to the nut 27 by means of the lateral protrusion 24A'', thereby preventing rotation.
details on how it can be releasably attached.

FIG. 7 shows a schematic side view of an interchangeable embodiment of the arrangement according to FIG. The nut 27 is screwed into a screw spindle 26 mounted on the rear thrust bearing 16 and the front radial bearing 17. The front end of the screw spindle 26 is adapted to a drive gear 19 by the electric motor 14. Two rigid support arms 36 (located on opposite sides of the screw spindle) are connected to the rudder post 30 by journals 35.
Pivot with. Each support arm 36 pivots on a nut 27 by means of a coupling means 24 with a locking device 100'. The mechanism and operation of the coupling means and locking device will be described in detail below in FIGS. 8-10.
A guide rod 101 is mounted on the screw spindle 27 in bearings 16'', 17'', in which it is rotatable but not axially movable. Guide rod 10
1 is fitted at its front end with a hooking fork 103;
and interacts with nut 27 by means described below.

According to FIGS. 8-10, the nut 27A has two wings 28 that are opposite to each other and project laterally from the central portion 27b, and furthermore have a guide rod 101.
and an upwardly projecting bearing 29 for the cam element 102 which is slidably arranged on the guide rod.
Both wings 28 have similar shapes and their cross-sectional configuration is indicated by dashed hatching in FIG. Each wing 28 has a forwardly directed concave surface 28a formed to partially enclose the lateral protrusion 24A'' of the connecting yoke 24A, that is, only from the rear.
Forms an engaging means that is pressed against A from behind.
The engagement of the concave surface 28a with the yoke-shaped coupling means 24A prevents the nut 27 from pivoting relative to the screw spindle 26. This stabilizing effect is caused by the above-mentioned guide rod 10 passing through the bearing 29.
1 further promotes this. At each end 24A', a connecting yoke 24A is pivotally attached to a support arm 36 (see FIG. 1) at a location indicated by 24b (see FIG. 5) by immovable means along the arm. adapted to be

At the outer end of each wing 28 is an array of flanges 28b in which apertures 28c for pivot pins 117 are sequentially provided spaced apart from the concave surface 28a. There are blind holes 28d on both sides of the central portion 27b of the nut, which are concentric with the holes 28c in the flange 28b. Latch mechanism 100 according to FIG.
a is mounted in the space between said side or flat side of the central portion 27 and the equally flat inner surface of each outer flange 28b.

Each lock device 100 has a central portion 27b.
Two such latching mechanisms 10 on each side of the
0a, and a control yoke 105 which bridges the screw spindle 26 to the rear of the nut 27 and has an opening 105b at each end of its leg 105a. On the opening 105b, at the forward edge of each leg 105A, a shoulder 105c is provided, and at the forward edge of the central portion of the yoke, and at the forward edge of the two legs 105a.
an aligned protrusion 10 located centrally between
There is 5d.

Each latch mechanism 100a includes two similar arms 118 according to FIG.
and three pins 111a, 116 and 11
7 (see FIG. 8). The configuration of the arm and hook is most apparent from FIG. It should be noted that on the underside of the arm 118 there is a recess 119 and that the transition from this recess to the beveled front edge 118d of the arm at 119a has a smoothly curved feature. be. Arm 11
8 has the three pins 111a, 116 and 1
Three openings 118a, 1 provided for 17
18b and 118c.

The hook 115 has an opening 115a and a recess 115b. The outer shape of the recess 115b is that of the connecting yoke 24A.
corresponds to the external shape of the protruding portion 24A'' of arm 1.
Unlike the 18 recesses 119, this recess 115b
terminates in a straight section forming an acute corner 115c. When the hook 115 is located between the arms 118 (see FIGS. 8 and 9), this corner 115c projects beyond the smoothly curved portion 119a of the arm 118.
The corner portion 115c is an edge portion 1 extending tangentially over a short distance less than or equal to the horizontal diameter D of the protruding portion 24A″.
It ends at 15c' (see Figure 8). Hook 115
There is a second acute angle portion 115d at the opposite end.

The two arms 118 have one pin 111a,
Two hooks 111,1 attached by 116
15 and the end of one leg 105a of the other control yoke 105. Hook 1
11 is further prevented from rotating by a pin 111b, while the nut 115 is only attached to one pin 117 and is thus able to pivot. The entire latch assembly fits within the space between the flat lateral surfaces of the central portion 27b of the nut 27 and the internal flat surface of the outer flange 28b, and is held in place by the pivot pin 117. Pin has concentric hole 28
d, 28c, it is retained there. The springs 112 on each side of the yoke 105 are
The control yoke is urged to tilt steadily in the direction (see FIG. 8). As shown in FIG. 8, the recess 119 of the arm 118 (see FIG. 10) is located in the wing portion 2.
Formed to exceed 8. In the space between the arms 118, there are corresponding straight edge portions 11e,
There are hooks 111 and 115 which are interconnected with 115e and which together carry the tension spring 104.

The guide rod 101 has a non-circular cross-sectional shape, by way of example a square cross-sectional shape, and is supported by bearings 16'', 17'' in such a way that it can rotate about its axis but cannot move axially. Guide rod 10
1 is a cam element 10 that can move in both directions of arrow B (see Figure 9) but cannot rotate about the guide rod.
It carries 2. The bearing 29 of the central part 27b carries with it the cam element 102, and the projection 105d of the control yoke 105 is held in contact with this cam element 102 by the action of a spring 112. The operating fork 103 is fixedly attached to the front end of the guide rod 101 which can be rotated together with the cam element 102 by the action of the operating fork 103 . As a result of this rotation and configuration of the camming element 102 engaging the protrusion 105d of the control yoke 105, the yoke undergoes a small amount of oscillation on the pivot pin 107 and the shoulder 10 of the leg 105a
5c lock or release the hook 115 by engaging or disengaging with their corners 105d. In FIG. 8, hook 115 is shown locked.

There is a gap between the shoulder 115c and its own control yoke 105 so that if the shoulder is overstressed they will break off without causing damage such that a new control yoke 105 has to be applied. A line of sight 105e is provided. Such overstressing can occur, for example, when the outboard drive is submerged for a short period of time when the screw is reversed or the boat continues to move forward a short distance despite the astern gear being engaged. This can occur when colliding with an obstacle. A compatible solution to this problem is disclosed in more detail with reference to FIGS. 14 and 15.

The stud bolts 110 (see FIG. 8) - two of which are proposed - extend between the front bearings 15, 16'' and the rear bearings 17, 17''. The screw spindle 26 is protected from dirt by a front rubber sealing bellows 26a, shown extended in FIG. 8, and a rear rubber sealing bellows 26b, shown retracted in FIG.

This device works as follows: connecting yoke 24
A is the shape, that is, the concave body surface 28 of the wing section 28
a, is always engaged from behind, and in this means the force is transmitted during the forward movement. From the front, the connecting yoke 24A connects the arm 1 as well as by the locking device and more precisely by the hook 115.
18.

However, by overcoming the tension of the coil springs 104 (i.e. 15Kg of tension for each spring), each hook 115
15c can be pivoted on pin 116 until it disengages from between curved portions 119a of arm 118, and in this position the entire latch mechanism 100a is pivoted on pivot pin 11.
7 in the direction of arrow E (see FIG. 8), and the entire outboard drive can be swung upwards. This situation occurs, for example, when a traveling outboard drive collides with an underwater obstacle.

When the boat moves astern, a gear lever (not shown) is operated by known means to reverse the direction of rotation of the screw 11. Simultaneously and by the same lever - in a straight line or via a linkage such as 44 (see FIG. 7) - the forked means 103 are operated, and the cam element 102 and the spring means 112
control yoke 105 to the locking position shown in FIG.
, and reaches a position where the connecting yoke 24A cannot be released at all.

The locking device 100 thus has two different types of locking: a positive lock, such as for reversing, and a lock that can be overcome when the spring 104 is overcome, such as during impact with an underwater obstacle during forward movement. It has a staged latching actuation.

11 to 13 respectively show a cylinder 121 or 121' and a cylinder 122 of an application example of the present invention.
A gear pump 39 comprising a piston such as (see FIG. 11) and arranged by conventional means outside the outboard motor casing 20'A and within the hull.
two double-acting hydraulically actuated cylinder-piston assemblies 121, supplied by a source of pressurized fluid, such as
-123 and 121'-123' are shown.

According to the invention, the hydraulically actuated devices are installed at their forward ends of the rudder posts 30 and at their aft ends, i.e., as illustrated, the piston rods 1
Free rear end portions 123a, 123 of 23, 123'
a′, and the two hydraulic actuators are connected to the casing 2
They are connected by connecting rods 24 which pass through elongated slots 25 on each side of 0A and pass through the entire outboard drive at right angles. slot 2
The rear end 25a of 5 defines an engagement means which engages the connecting rod 24 from behind and through which the force is transmitted to the forward movement. It is clear that special engagement or conveying means can be arranged inside the casing 20'A, for example if this casing is considered too vulnerable to transmitted forces.

Area 1 indicated by cross-hatching in Figures 12 and 13
Disposed within 20 are the power generation and power transmission components of the outboard motor, the detailed configuration of which is beyond the scope of the present invention.

The connecting rod 24 locks the engagement means 2 with the aid of a locking device 100', which is shown in more detail in FIG.
5a. It is clear from FIG. 14 that locking device 100' is constructed with essentially the same construction as latching mechanism 100a.
However, instead of the control yoke 105 it includes a spring load blocking element 46 which is arranged to slide on a fixed bearing 45 and which is provided by a bar 47 with a double arrow F.
A similar blocking and releasing mechanism is provided which can be operated in both directions. As shown, in principle a single arm 118 can interact with hook 115 and hook 111 can take the form of an integral part of arm 118. Arm 118 is journalled on a shaft 117a that corresponds to pivot pin 117 of FIGS.

121- arranged outside the casing;
It has already been proposed that cylinder-piston assemblies such as 123 and 121'-123' should be mounted on separate shafts arranged to rotate with the rudder post instead of the rudder post 36. . The present invention can also be easily used with a mechanism as shown in FIG. It will also be clear that, for purposes of the present invention, the externally located cylinder-piston assembly may be replaced by an externally located nut and spindle screw assembly.

According to FIG. 13, the rudder post 30 includes a reduction gear mechanism,
Two electric motors 14, 1, not shown, which can be adapted to
4' is connected by a parallelogram mechanism 130 to the second rudder post 36 which is shaft-mounted. A screw spindle 26', 26'' projects from each electric motor, each of which is provided with a nut 27', 27''. This nut is connected by a connecting rod 24 and is thus prevented from rotating. The construction in other details corresponds to that shown in FIG. Screw spindles, etc. are not shown in FIG. 13, but their rubber sealing bellows 26a, 26b
(See Figure 8).

In connection with FIG. 8, dashed line 105e is illustrated as a feature of protection against overload when reverse gear is engaged. 15 and 16, in conjunction with FIG. 14, show another solution to this problem, namely overload latches 106, 106', which are located between the hook 115 and the blocking element 46' or 46''. are placed respectively.

As shown in FIG.
Reference numeral 6 designates the shape of a claw 108 that is attached to the hook 115 and pivoted at a reference numeral 108a of the hook 115. The pawl 108 engages the blocking element 46' and its underside is chamfered for easy return movement. Nail 1
08 is constantly acted upon by a tension spring 107,
Thus, it is pressed against the stop 108a. The tension of spring 107 determines the force when overload latch 106 is released. In practice, it is estimated that when a marine engine at full throttle is switched to reverse gear, its torque triples in a short period of time. Spring 107 is selected to counteract this force against the prime mover.

As shown in FIG. 16, the front portion of the blocking element 46'' is in the form of a pawl pivoted on the pin 46a and is pressed against the stop edge 109 by a tension spring 107'. Dimensions of the spring 107 15 or 16, the arrangement shown in FIG. 15 or 16 applies equally to the spring 107'.
It will be appreciated that instead of e, the more accurate hook 115 of the device shown in FIG. 9 may also be used.

In all illustrated embodiments, remote control balancing (also known as "power trim") is achieved by activation of the power source for the ascending and descending movements, i.e. in the illustrated embodiments. In this case, the electric motor 14, 14', 14'' or the pressurized fluid source 39 can be adjusted to achieve a selected initial position - a counterbalancing position - a subsequent lifting movement from there - a tilting, but always the same initial movement. Regardless of whether such power source is electric (electric motor 14) or not (hydraulic actuators 21-23, 121-123), the alignment described above can be performed using electric power that can be operated from the ship's cockpit. This can suitably be achieved by an arrangement of relays 48 (see FIGS. 7 and 11).

[Brief explanation of the drawing]

FIG. 1 is a side view of an outboard motor according to the present invention. FIG. 2 is a perspective view of the outboard portion of the inboard/outboard motor according to the present invention. FIG. 3 is a longitudinal sectional view of an interchangeable embodiment of the drive device according to FIG. 2; 4 shows a side view of another interchangeable embodiment of the drive device according to FIG. 2; FIG. FIG. 5 is a diagram showing another embodiment of the outboard drive device according to the present invention with the cover removed. FIG. 6 is an exploded view of a screw spindle according to the invention in connection with a bearing and a connecting yoke. FIG. 7 is a side view of a screw spindle according to the invention provided with a locking device. FIG. 8 is an enlarged view showing details of the locking device. FIG. 9 is an exploded view of the locking device of FIG. 8. FIG. 10 is an exploded view of details of the locking device of FIG. 9. FIG. 11 is a side view similar to FIG. 1 of another outboard motor. FIG. 12 is a longitudinal sectional view taken along the line XII-XII in FIG. 11. FIG. 13 is a longitudinal sectional view similar to FIG. 12 of yet another embodiment of the outboard motor.
14-16 are side views of three different embodiments of the locking device in the arrangement according to FIGS. 11-13. 10... Ship, 10a... Stern beam, 20, 20',
40...Outboard drive device, 20A, 20'A, 40
A...Casing, 23b, 25a, 27a, 2
8a...Engagement means, 24, 24A...Connection means,
25...Slot, 30, 30A...Steering shaft, 3
4...Tilt axis means, 35...Hinge axis means, 3
6,121-123,121'-123'...Support means, 100,100',106...Lock device.

Claims (1)

[Scope of Claims] 1. Supported by a tilting shaft means 34 on the outside of the transom 10a of the ship 10 so as to be able to be steered about the longitudinal axis G and tilted about the transverse axis H, and mounted within the casing 20A. a tilting device consisting of a rod-shaped link means 36 which is housed and supports a second hinge shaft means 24 which is pivotally connected to a first hinge shaft means 35 at its forward end near said transom and connected to a drive at its aft end; In the outboard drive device, the distance between at least one of the two hinge shaft means from the stern beam is variable by the action of drive means 21 and 22 so as to perform the tilting movement, transverse steering shaft means 30, 30A are mounted on the outside of said transom so as to be pivotable about said longitudinal axis G, b. Steering shaft means 30, 30A
c. fixedly attached to the lower part of said lateral steering shaft means 30, 30A such that said first hinge shaft means 35 follows all said lateral steering movements;
extending parallel to the tilting shaft means 34 and at an unchanging distance from the transom;
each member extending to the other along its side walls outside the casing, e. The casing 20A is provided with an elongated linear slot 25 in both side walls, the rear end of the slot being closer to the first end than the front end. Hinge shaft means 3
5; f said second hinge shaft means is movable within said slot 25 and comprises connecting means 24, 24A for interconnecting said two rod-like members 36; g said connecting means 24 is rearwardly connected to the drive part by means of an engagement means 23b which removably engages said means only from the front; h remote control locking means 100' engages said coupling means from the front and connects said engagement means with said coupling means; An outboard drive device characterized by being provided so as to be detachably locked to a means. 2. The engagement means has a non-variable position with respect to the outboard drive and the rear end of the support means is adjustable to a position allowing the support means to have a variable length adjustable by remote control. An outboard drive device according to claim 1. 3. The support means have a non-variable length, at least during normal forward movement of the ship, and the engagement means are movable with respect to the outboard drive in the length direction of the elongated slot with the aid of a remote control; Inside there are first parts 21 and 26 that are quantitatively attached to the outboard drive device.
and a second movable part 2 carrying engagement means.
2, 23, 27;
22, 23, 26, and 27 are arranged, The outboard drive device according to claim 1, characterized in that. 4. At least one dual cylinder-piston assembly is provided which is supplied from a power source in the form of a pressurized fluid source for adjustment of the mounting position. outboard drive. 5. According to claim 2 or 3, there is provided at least one nut and screw spindle assembly driven by a power source in the form of a reversible electric motor for adjustment of the mounting position. outboard drive. 6. The power source is adapted to be blocked by a remote control at a stage selected corresponding to the desired balance of the outboard drive, and an array of motorized relays 48 operable from the cockpit are used to control said remote control. The outboard drive device according to claim 4 or 5, characterized in that it is provided for. 7. An outboard drive as claimed in any one of claims 3 to 6, characterized in that the engagement means are defined by the trailing edges of the two elongated slots. 8. The outboard drive device according to any one of claims 1 to 7, wherein the connecting means is defined by a connecting rod-shaped body. 9. The connecting means comprises two straight circumferential sections 24 projecting laterally from the arched central part and the outer central part passing through the screw spindle of said assembly.
A'' and the nut of said assembly has two laterally extending wings 28 having forwardly facing concave surfaces 28a for fitting of the circumferential portion of said connecting yoke. 10. An outboard drive according to claim 5 or claim 6, characterized in that the locking device is provided with at least one pivotable arm 118 having a side recess 119; including at least one pivotally mounted and spring-loaded hook 115 and a remote control locking element 46, 105 for said hook, said at least one arm and at least one
8. Outboard drive according to any one of claims 1 to 7, characterized in that the two hooks are arranged to engage the coupling means from the front. 11 a flange 28b is accommodated in the outer end portion of the wing, and one said hook 115 is located in the free space between the central part 27a of the nut and each flange;
A latching mechanism 100a is provided comprising said at least one arm 118 on which is pivotally mounted, conventional locking elements for both latching mechanisms straddling the screw spindle and supporting both legs 105 thereof.
is defined by a control yoke 105 which is provided with an engagement element 105c to block said hook 115 at a, the control yoke extending parallel to the screw spindle and mounted on a stationary guide rod 101 for rotation. 11. The outboard drive device according to claim 9 or 10, wherein the outboard drive device is sequentially operable by means of cam elements (102) arranged in a slidable manner rather than rotatably. 12. Outboard drive according to claim 11, characterized in that the central part of the nut is fitted with a bearing 29 which supports the cam element with it when the nut moves along the screw spindle. Device. 13 Between the spring biased hook 15 and the remote control lock element 46, 105, there is an overload catch part 105e,
106, 106' are provided, the outboard drive device according to any one of claims 10 to 12, characterized in that the outboard drive device is provided with: 106, 106'. 14. Buffer means 37, 38 are provided between the casing of the outboard drive and the support means in order to receive transverse stresses and/or to dampen impacts. 14. The outboard drive device according to any one of Items 1 to 13.