Information
-
Patent Grant
-
6183320
-
Patent Number
6,183,320
-
Date Filed
Monday, August 30, 199924 years ago
-
Date Issued
Tuesday, February 6, 200123 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
- Knobbe, Martens, Olson & Bear, LLP
-
CPC
-
US Classifications
Field of Search
US
- 440 53
- 440 61
- 440 900
- 123 195 P
-
International Classifications
-
Abstract
A tilt mechanism for a marine outboard drive includes a hydraulic cylinder assembly disposed transversely offset from the center axis of the tilt mechanism. The tilt mechanism includes a swivel bracket carrying a drive unit for pivotal movement about a generally vertically extending steering axis and a clamping bracket supporting the swivel bracket for pivotal movement about a generally horizontally extending tilt axis. The swivel bracket has wall portions transversely extending from the steering axis. One of the wall portions positioned nearer to the hydraulic cylinder assembly is reinforced greater than the other wall portion. Also, the clamping bracket comprises a pair of spaced members. One of the spaced members positioned nearer to the hydraulic cylinder assembly is reinforced greater than the other spaced member.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
This invention relates to a trim and/or tilt mechanism for a marine outboard drive and more particularly to an improved trim and/or tilt mechanism that includes a hydraulic cylinder device disposed transversely offset from the center axis of the mechanism per se.
2. Description of Related Art
As an example of the marine outboard drive, generally an outboard motor has a drive unit mounted on an associated watercraft by means of a trim and/or tilt mechanism which comprises a swivel bracket and a clamping bracket. The swivel bracket carries the outboard drive unit for pivotal movement about a generally vertically extending steering axis. The clamping bracket, in turn, is affixed to the transom of an associated watercraft with a pair of horizontally spaced members and supports the swivel bracket for pivotal movement about a generally horizontally extending tilt axis.
The trim and/or tilt mechanism includes also a hydraulic cylinder assembly disposed between the swivel bracket and the clamping bracket so that the swivel bracket as well as the drive unit is tilted up or down relative to the clamping bracket and eventually to the transom of the associated watercraft. The fluid motor is, for example, a compound trim and tilt hydraulic cylinder device. An exemplary hydraulic cylinder device is shown in the U.S. Pat. No. 5,718,613.
The hydraulic cylinder device includes an outer cylinder housing, a tilt cylinder slidably supported in the outer cylinder housing, a tilt piston slidably supported in the tilt cylinder and a piston rod affixed to the tilt piston at its one end and extending outwardly from both of the tilt cylinder and the outer cylinder housing. The other end of the piston rod is pivotally connected to the swivel bracket, while the outer cylinder housing is also pivotally connected to the clamping bracket. Hydraulic fluid is contained in the cavities formed in the cylinder housing and also the tilt cylinder and pressurized selectively by a powering assembly to move the piston rod either one of the expanding direction or contracting direction.
By this selective movement of the piston rod, the drive unit can be lifted up or lowered down. If an operator of the outboard motor wishes to adjust the trim angle of the drive unit, the operator operates the hydraulic cylinder device within a trim range. During this trim range operation, the tilt cylinder acts as a trim piston and moves relatively slow but produces large force. Meanwhile, if the operator wishes to tilt up or down the drive unit, he or she operates the hydraulic cylinder device within a tilt range. In this range, the tilt piston moves and this time relatively quick but produces small force.
As described above, the mechanism will operate as a trim and tilt mechanism with this hydraulic cylinder device. Some mechanism, however, is provided with either a trim cylinder device or a tilt cylinder device. Thus, the term “tilt mechanism” will mean not only the tilt mechanism per se but also the trim and tilt mechanism and even a single trim mechanism in the broad sense hereunder wholly through this specification including claims unless depicted otherwise.
The powering assembly comprises a reversible electric motor, a reversible hydraulic pump driven by the electric motor and a fluid reservoir. In order to minimize the size of the tilt mechanism, usually the powering assembly is placed between the spaced members of the clamping bracket side by side with the hydraulic cylinder device. Since the place for the hydraulic cylinder device and the powering assembly is not so spacious, it means that the hydraulic cylinder device must be decentered transversely from the axis of the tilt mechanism. This arrangement gives rise to a problem.
That is, the lifting or lowering force exerted onto the piston rod and the outer cylinder housing affects the swivel bracket and the clamping bracket as an offset load and this offset load is likely to deform the bracket assembly. If the brackets have sufficient thickness entirely, rigidity will be enough. However, this resolution apparently increases the whole weight of the bracket assembly.
It is, therefore, a principal object of this invention to provide an improved tilt mechanism to solve the problem.
It is another object of this invention to provide a tilt mechanism that will hardly cause such a deformation in its bracket assembly without having futile weight.
SUMMARY OF THE INVENTION
In accordance with one aspect of this invention, a tilt mechanism for a marine outboard drive comprises a swivel bracket. The swivel bracket carries a drive unit for pivotal movement about a generally vertically extending steering axis. The swivel bracket has wall portions extending generally transversely at both sides of the steering axis. The tilt mechanism also includes a clamping bracket. The clamping bracket supports the swivel bracket for pivotal movement about a generally horizontally extending tilt axis. The clamping bracket has a pair of transversely spaced members adapted to be affixed to the transom of an associated watercraft. The wall portions of the swivel bracket are at least partially capable to be fitted between the spaced members. The tilt mechanism further comprises a hydraulic cylinder assembly. The hydraulic cylinder assembly is capable to expand and contract along its longitudinal axis. The hydraulic cylinder assembly has a pair of end portions. One of the end portions is pivotally connected to the swivel bracket and the other one of the end portions is pivotally connected to the clamping bracket. The hydraulic cylinder assembly is biased to one of the transversely spaced members. At least one of the wall portions and the transversely spaced members positioned nearer to the hydraulic cylinder assembly is reinforced greater than the other one of the wall portions and the transversely spaced members.
In accordance with another aspect of this invention, a tilt mechanism for a marine outboard drive comprises a swivel bracket. The swivel bracket carries a drive unit for pivotal movement about a generally vertically extending steering axis. The tilt mechanism also comprises a clamping bracket. The clamping bracket supports the swivel bracket for pivotal movement about a generally horizontally extending tilt axis. The clamping bracket has a pair of transversely spaced members adapted to be affixed to the transom of an associated watercraft. The tilt mechanism further comprises a hydraulic cylinder assembly. The hydraulic cylinder assembly is capable to expand and contract along its longitudinal axis. The hydraulic cylinder assembly has a pair of end portions. One of the end portions is pivotally connected to the swivel bracket and the other one of the end portions is pivotally connected to the clamping bracket. The hydraulic cylinder assembly is disposed between the transversely spaced members and biased to one of the transversely spaced members. Each of the transversely spaced members includes a foot section being capable to be seated at the transom of the associated watercraft. Each of the transversely spaced members also includes a standing section extending from the foot portion. The respective standing sections have bores. A pivot shaft of the other one of the end portions of the hydraulic cylinder assembly is journaled in the bores. The other one of the end portions of the hydraulic cylinder assembly is disposed on the pivot shaft at generally directly next to one of the transversely spaced members. The reminder of space on the pivot shaft is balanced with a collar.
Further aspects, features and advantages of this invention will become apparent from the detailed description of the preferred embodiments which follow.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1
is a side elevational view showing an outboard motor embodying features of this invention as attached to the trnsom of an associated watercraft shown partially in phantom.
FIG. 2
is an enlarged front elevational view of a tilt mechanism constructed in accordance with an embodiment of this invention. Some portions are shown in cross-section.
FIG. 3
is an enlarged outside elevational view of one clamping bracket member positioned at the starboard.
FIG. 4
is an enlarged inside elevational view of the same clamping bracket member as shown in FIG.
3
.
FIG. 5
is a cross-sectional view of the same clamping bracket member taken along the line
5
—
5
in FIG.
3
.
FIG. 6
is a cross-sectional view of the same clamping bracket member taken along the line
6
—
6
in FIG.
4
.
FIG. 7
is an enlarged outside elevational view of the other clamping bracket member positioned on the portside.
FIG. 8
is an enlarged inside elevational view of the same clamping bracket member as shown in FIG.
7
.
FIG. 9
is a cross-sectional view of the same clamping bracket member taken along the line
9
—
9
in FIG.
7
.
FIG. 10
is a cross-sectional view of the same clamping bracket member taken along the line
10
—
10
in FIG.
8
.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT OF THE INVENTION
Referring now in detail to
FIGS. 1 through 10
which illustrate an embodiment of this invention and initially to
FIG. 1
, an outboard motor is identified generally by the reference numeral
20
. The outboard motor
20
is shown as attached to a transom
22
of an associated watercraft
24
that is shown partially. A hydraulic trim and tilt adjustment mechanism is identified generally by the reference numeral
26
and will be described more in detail with reference to
FIGS. 2 through 10
later.
Although the invention is described in conjunction with the outboard motor
20
, it should be readily apparent that the invention is susceptible of use with other types of outboard drives such as the outboard drive portion of an inboard, outboard drive. It is believed that other usages will be readily obvious to those skilled in the art.
The outboard motor
20
includes a power head
28
which comprises a powering internal combustion engine (not shown) and a surrounding protective cowling
30
. As is typical with outboard motor practice, the engine of the power head
28
is supported so that its output shaft rotates about its vertically extending axis and drive a driveshaft
34
that is journaled within a driveshaft housing
36
. The driveshaft
34
extends through the driveshaft housing
34
and into a lower unit
38
and there drives a propulsion device such as a propeller
40
affixed on a propeller shaft
41
through a conventional forward/neutral/reverse transmission
42
.
A steering shaft
44
is affixed to a driveshaft housing
36
and is supported for steering movement within a swivel bracket
48
in a known manner. The steering shaft
44
is accommodated in a steering shaft holder portion
49
of the swivel bracket
48
. The swivel bracket
48
has a forwardly extending portion
50
that is connected by means of a pivot pin
52
to a clamping bracket
54
. Thus, the swivel bracket
48
carries the drive unit
58
for pivotal movement about a generally vertically extending steering axis
59
of the steering shaft
44
, while the clamping bracket
54
supports the swivel bracket
48
for pivotal movement about a generally horizontally extending tilt axis of the pivot pin
52
. The clamping bracket
54
is detachably affixed to the transom
22
in a manner that will be described shortly. The swivel bracket
48
and the clamping bracket
54
define a bracket assembly
56
.
The power head
28
, the driveshaft housing
36
and the lower unit
38
except for the bracket assembly
56
define a drive unit
58
. The pivotal connection
52
between the clamping bracket
54
and the swivel bracket
48
permits the drive unit
58
to be moved through a trim adjusted range that exists between the fully trimmed down position to the flully trimmed up position. In addition, the drive unit
58
may be swung through a remaining range to a tilted up out of the water position about the pivot pin
52
. A hydraulic tilt and trim cylinder assembly or device
60
is provided for effecting these movements and other movements such as a pop up movement when an underwater obstacle is struck to the drive unit
58
.
The cramping bracket
54
actually comprises a pair of transversely spaced apart side members
64
,
66
that are mounted on the rear of the transom
22
. The side member
64
is located at the starboard, while the other side member
66
is located on the port side. The swivel bracket
48
is interposed between them. That is, the swivel bracket
48
has wall portions
70
,
72
that extend generally transversely at both sides of the steering shaft holder portion
49
. The forwardly extending portion
50
is bound up with these wall portions
70
,
72
at the top of the swivel bracket
48
. The steering shaft
44
has the aforenoted steering axis
59
. This axis
59
is consistent with the center axis of the hydraulic trim and tilt adjustment mechanism
26
in the front view as shown in FIG.
2
. Thus, the center axis of the tilt mechanism
26
will be indicated with the same reference numeral
59
hereunder.
The hydraulic trim and tilt cylinder assembly
60
is nested between the side members
64
,
66
but positioned transversely offset from the steering or center axis
59
toward the starboard side member
64
. The center axis
76
of the cylinder assembly
60
is, thus, located apart from the center axis
59
with the distance (D). The reminder of the space is occupied generally by a powering assembly
77
so that both of the hydraulic cylinder assembly
60
and the powering assembly
77
are disposed side by side. That is, the hydraulic cylinder assembly
60
occupies almost the half space that extends at the starboard side from the center axis
59
and the powering assembly
77
occupies the other half space that extends on the port side from the axis
59
.
The hydraulic cylinder assembly
60
forms an integral part with the powering assembly
77
. The powering assembly
77
includes a reversible electric motor
78
at its upper end. A reversible hydraulic pump
80
is disposed below the electric motor
78
. A fluid reservoir
82
is also disposed beneath the pump
80
and contains hydraulic working fluid for the system. In addition, a suitable valve assembly may be incorporated within the pump
80
and the reservoir
82
so as to provide normal pressure relief functions and directional control of the hydraulic cylinder assembly
60
.
The hydraulic cylinder assembly
60
includes an outer cylinder housing
86
having a trunion portion
88
with a bore
90
so as to receive a lower pin
91
for providing a pivotal connection to the clamping bracket
54
and specifically the side members
64
,
66
thereof. Bores
92
,
93
of the side members
64
,
66
receive the lower pin
91
. A pair of bushes
94
are fitted around the lower pin
91
. The bushes
94
are separated at the center axis
59
from each other and each has a flange
96
at the outer side. The bushes
94
are made of metal such as, for example, stainless steel (SUS). Meanwhile, another pair of bushes
98
are provided around and at both sides of the lower pin
91
to be fitted into the bores
92
,
93
of the side members
64
,
66
. Each of these bushes
98
have a flange that meets with the respective flanges
96
of the bushes
94
. The bushes
98
are also made of metal such as, for example, stainless steel (SUS). Thus, the lower pin
91
is journaled by the side members
64
,
66
and pivotally supports the trunion
88
of the cylinder housing
86
. A collar
102
is fitted around the outer side of one of the bushes
94
so as to balance the distance between the trunion
88
of the cylinder housing
86
and the side member
66
located on the port side. In other words, the trunion
88
is accurately positioned on the lower pin
91
with the collar
102
and the flange
96
of the bush
94
. Because of this arrangement, no rattling of the outer housing
86
is produced.
As described above, since the metal bushes
94
,
98
are fitted around the lower pin
91
, the pin
91
is reinforced against the bending force exerted thereon in the decentered arrangement of the hydraulic cylinder assembly
60
.
Although any internal arrangement is available, the hydraulic cylinder assembly
60
in this embodiment is a compound or telescopic trim and tilt cylinder device that is conventional and it is, for example, disclosed in the U.S. Pat. No. 5,718,613 as aforenoted. The hydraulic cylinder device
60
contains a tilt cylinder slidably supported in a cavity of the outer cylinder housing
86
, a tilt piston slidably supported in a cavity of the tilt cylinder and a piston rod
110
affixed to the tilt piston at its one end and extending outwardly from both of the tilt cylinder and the outer cylinder housing
86
.
The tilt piston has valving passages for effecting, for example, a shock absorbing function in case of an abrupt hit to the drive unit
58
by an underwater obstacle. Also, the outer cylinder housing
86
has a passage that connects via the powering assembly
77
upper and lower chambers formed in the cavity and generally divided by the tilt piston. The passage is formed at a wall portion of the outer housing
86
. Working fluid pressurized by the powering assembly
77
will be supplied through the passage to the upper and lower chambers to move the tilt piston. This causes the expanding and contracting movements of the piston rod
110
.
The piston rod
110
has a trunion portion
112
with a bore
114
that receives an upper pin
116
for providing a pivotal connection to the swivel bracket
48
and specifically a pair of spaced portions
118
and
120
thereof A pair of bushes
122
, which have configurations similar to the bushes
94
are inserted between the upper pin
116
and the bore
114
of the trunion
112
. Another pair of bushes
124
, which have configurations similar to the bushes
98
are also inserted between the upper pin
116
and bores of the spaced portions
118
,
120
. These bushes
122
,
124
can be made of, for example, metal or synthetic resin.
With the aforedescribed connections, when the piston rod
110
expands outwardly from the outer cylinder housing
86
, the swivel bracket
48
and also the drive unit
58
supported by the swivel bracket
48
are lifted up within the trim adjusted range and further the tilt range. Also, when the piston rod
110
contacts into the outer housing
86
, the swivel bracket
48
as well as the drive unit
58
are lowered down within the same ranges.
The hydraulic tilt cylinder assembly
60
is decentered and more specifically disposed transversely offset from the center axis
59
of the hydraulic tilt adjustment mechanism
26
as described above. In other words, the hydraulic tilt cylinder assembly
60
is biased to a starboard side member
64
. Due to this arrangement, the lifting or lowering force exerted onto the piston rod
110
and the outer cylinder housing
86
affects the swivel bracket
48
and the clamping bracket
54
as an offset load. This offset load is likely to deform the bracket assembly
56
.
In order to avoid the deformation, the bracket assembly
56
has improved configurations. These configurations will now be described with reference to
FIGS. 2 through 10
.
Firstly, the port side wall portion
72
of the swivel bracket
48
, which is positioned farther from the hydraulic cylinder assembly
60
than the starboard side wall portion
70
, has a recess
130
at its transverse end. This means that the starboard side wall portion
70
is reinforced greater than the port side wall portion
72
. At this port side wall portion
72
, a bore
132
is provided. A tilt stop lever
134
is pivotably inserted into this bore
132
and its head portion
136
is positioned in the recess
130
. This tilt stop lever
134
is conventional and for holding the drive unit
58
at the fully tilted up position mechanically by positioned at a step portion
137
formed at the top of the side member
66
. Thus, the recess
130
contributes not only for reinforcement of the starboard side wall portion
70
relative to the port side wall portion
72
but also for compactness of the hydraulic tilt mechanism
26
. In addition, the port side wall portion
72
, conversely, has a weight lighter than a weight of the starboard side wall portion
70
. This contributes to reduce the whole weight of the swivel bracket
48
.
Another improvement exists in configurations of the side members
64
,
66
of the clamping bracket
54
.
The respective side members
64
,
66
are configured generally as a L-shape in a side elevational view as seen in
FIGS. 3
,
4
,
7
and
8
. That is, the upper portions in proximity to bores
140
,
142
, through which the pivot pin
52
extends, are curved to make a generally right angle. The respective side members
64
,
66
have foot sections
144
,
146
, with which the side members
64
,
66
are seated at the transom
22
of the associated watercraft
24
. The respective side members
64
,
66
have also standing sections
148
,
150
that extend from the foot sections
144
,
146
. The foot sections
144
,
146
extend simply outwardly. That is, transverse cross-sections of the side members
64
,
66
are configured as a generally L-shape. Hook portions
152
,
154
are provided for assuring the installation of the clamping bracket
54
to the transom
22
of the associated watercraft
24
.
As best seen in
FIG. 3
, the standing section
148
of the starboard side member
64
has hollow portions
156
that are recessed at the curved section. Ribs
158
are formed between the respective hollow portions
156
. The hollow portions
156
open outwardly as seen in FIG.
5
. The length distance (S) from the centroidal axis (X) of the starboard side member
64
proximate the hollow portions
156
to the point of action (Z) of the exerting force, which exists on the center axis
76
, is less than the distance (L) from the centroidal axis (Y) of the starboard side member
64
in other locations to the same center axis
76
Accordingly, the bending moment exerted upon the side member
64
is smaller than the bending moment that would be produced if the hollow portions
156
were not provided. Thus, by decreasing the section modulus of the starboard side member
64
, the maximum bending stress that can be accommodated is increased. This means that the starboard side member
64
, particularly the curved portion thereof, is reinforced.
In addition, as best seen in
FIG. 7
, the port side member
66
has only a couple of hollow portions
160
, in other words, only one rib
162
therebetween. That is, the starboard side member
64
is reinforced greater than the port side member
66
. Thus, the bending force exerted upon the starboard side member
64
is effectively absorbed by the multiple ribs
158
thereon. Conversely, the port side member
66
is lighter than the starboard side member
64
because it has no unnecessary reinforcement. The hollow portions
160
also open outwardly as shown in FIG.
9
.
In the meantime, the bottom portions of the standing sections
148
,
150
are provided with the bores
92
,
93
through which the lower pin
91
extends. As best seen in
FIGS. 4 and 8
, both portions in proximity to these bores
92
,
93
are reinforced with a couple of ribs
166
,
168
. However, only the periphery of the bore
92
is further reinforced with a bank portion
170
formed around it. Accordingly, the bottom portion of the starboard side member
64
is more rigid than the same portion of the port side member
66
.
As described above, in the bracket assembly
56
, only the portions those substantially need reinforcement have configurations that increase rigidity. Thus, the reinforcement is achieved without increasing unnecessary weight.
A plurality of apertures or recesses
174
(see
FIG. 2
) are formed on the respective foot sections
144
,
146
of the side members
64
,
66
. These apertures or recesses
174
are useful to reduce the whole weight of the clamping bracket
54
further.
Also, the respective standing sections
148
,
150
have a plurality of apertures
176
,
178
through which a trim stopper pin (not shown) will be inserted to keep the drive unit
58
at a suitable trim angle selectively and mechanically.
Of course, the foregoing description is that of a preferred embodiment of the invention, and various changes and modifications may be made without departing from the spirit and scope of the invention, as defined by the appended claims.
Claims
- 1. A tilt mechanism for a marine outboard drive comprising a swivel bracket carrying a drive unit for pivotal movement about a generally vertically extending steering axis, said swivel bracket having wall portions extending generally transversely at both sides of said steering axis, a clamping bracket supporting said swivel bracket for pivotal movement about a generally horizontally extending tilt axis, said clamping bracket having a pair of transversely spaced members adapted to be affixed to the transom of an associated watercraft, said wall portions of said swivel bracket at least partially being capable to be fitted between said transversely spaced members, a hydraulic cylinder assembly being capable to expand and contract along its longitudinal axis, said hydraulic cylinder assembly having a pair of end portions, one of said end portions being pivotally connected to said swivel bracket and the other one of said end portions being pivotally connected to said clamping bracket, said hydraulic cylinder assembly being biased to one of said transversely spaced members, and at least one of said wall portions and said transversely spaced members positioned nearer to said hydraulic cylinder assembly being reinforced greater than the other one of said wall portions and said transversely spaced members.
- 2. A tilt mechanism as set forth in claim 1 wherein the other one of said wall portions has a recess at its transverse end.
- 3. A tilt mechanism as set forth in claim 2 further comprising a tilt stop lever for supporting said drive unit at the fully tilted up position, and at least a part of said tilt stop lever being positioned at said recess.
- 4. A tilt mechanism as set forth in claim 1 wherein each one of said transversely spaced members includes a foot section being capable to be seated at the transom of the associated watercraft and a standing section extending from said foot section, and one of said standing sections positioned nearer to said hydraulic cylinder assembly is reinforced greater than the other one of said standing sections.
- 5. A tilt mechanism as set forth in claim 4 wherein both of said standing sections are provided with at least one rib, and the number of said ribs provided at said standing section positioned nearer to said hydraulic cylinder assembly is more than the number of said ribs provided at the other standing section.
- 6. A tilt mechanism as set forth in claim 5 wherein both sides of each of said ribs are formed as hollows opening toward generally outwardly.
- 7. A tilt mechanism as set forth in claim 4 wherein said respective standing sections have bores to receive a pivot shaft of said swivel bracket, and a portion located in proximity to said bore of said standing section positioned nearer to said hydraulic cylinder assembly is reinforced greater than another portion located in proximity to said bore of the other standing section.
- 8. A tilt mechanism as set forth in claim 7 wherein said respective portions are configured as curves.
- 9. A tilt mechanism as set forth in claim 4 wherein said respective standing sections have bores, a pivot shaft of the other one of said end portions of said hydraulic cylinder assembly is journaled in said bores, the other one of said end portions of said hydraulic cylinder assembly is disposed on said pivot shaft at generally directly next to one of said transversely spaced members, and the reminder of space on said pivot shaft is balanced with a collar.
- 10. A tilt mechanism as set forth in claim 1 further comprising a powering assembly for expanding and contracting said hydraulic cylinder assembly, and said powering assembly being disposed between said hydraulic cylinder assembly and one of said transversely spaced members that is positioned farther from said hydraulic cylinder assembly than the other one of said transversely spaced members.
- 11. A tilt mechanism for a marine outboard drive comprising a swivel bracket carrying a drive unit for pivotal movement about a generally vertically extending steering axis, a clamping bracket supporting said swivel bracket for pivotal movement about a generally horizontally extending tilt axis, said clamping bracket having a pair of transversely spaced members adapted to be affixed to the transom of an associated watercraft, a hydraulic cylinder assembly being capable to expand and contract along its longitudinal axis, said hydraulic cylinder assembly having a pair of end portions, one of said end portions being pivotally connected to said swivel bracket and the other one of said end portions being pivotally connected to said clamping bracket, said hydraulic cylinder assembly being disposed between said transversely spaced members and biased to one of said transversely spaced members, each of said transversely spaced members including a foot section being capable to be seated at the transom of the associated watercraft and a standing section extending from said foot portion, said respective standing sections having bores, a pivot shaft of the other one of said end portions of said hydraulic cylinder assembly being journaled in said bores, the other one of said end portions of said hydraulic cylinder assembly being disposed on said pivot shaft at generally directly next to one of said transversely spaced members, and the reminder of space on said pivot shaft being balanced with a collar.
Priority Claims (1)
Number |
Date |
Country |
Kind |
10-252989 |
Sep 1998 |
JP |
|
US Referenced Citations (1)
Number |
Name |
Date |
Kind |
5529519 |
Nakamura et al. |
Jun 1996 |
|