JPS6018642Y2 - Hydraulic actuator for steering - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic actuation device used to drive the rudder of a ship.

For example, Utility Model Publication No. 44-16085 and Utility Model Publication No. 50-9
The double-acting cylinder shown in No. 8197 is not designed to be mounted around the axis of the cylinder by changing its position and being mounted at a fixed position.

Therefore, when a rack is formed on the piston rod fixed to the piston, and the pinion is angularly displaced by this rack to drive the rudder connected to the pinion, the mounting structure of the cylinder depends on the position. must be devised, making installation work complicated.

In addition, in these prior art, a connection port that communicates with the cylinder chambers formed at both ends of the piston within the cylinder is provided at the extreme end of the cylinder, and when the cylinder is fixed at a fixed position near the center in the axial direction. No efforts have been made to simplify the piping configuration.

SUMMARY OF THE INVENTION The object of the present invention is to provide a steering hydraulic actuator that can be easily mounted in multiple mounting positions around the axis of the cylinder.

Another object of the present invention is to provide a steering hydraulic actuator that can simplify external piping work when installed at a fixed position near the axial center of the cylinder.

The present invention provides a cylinder case 10 for driving a ship's rudder.
In a hydraulic actuator having a built-in cylinder 15 and a piston 16, a pair of piping connections are formed near the center of the cylinder case 10 in the axial direction and near the attachment point to the hull,
Each end of both cylinder chambers of the cylinder is connected to each of the piping connections via oil passages 23a and 23b extending in the axial direction between the inner circumferential surface of the cylinder case 10 and the outer circumferential surface of the cylinder 15. are in communication with each other, and the cylinder case 10
Form mounting portions adjacent to each other on the peripheral wall of the mounting portion, and in each mounting portion, bolt holes are formed at each vertex of a virtual parallelogram having the same size and shape, and the corresponding bolt holes have the same shape and size. , oil passages 23a and 23b formed in the cylinder case 10
In the middle, there is a convex portion 25 a that protrudes inward in the radial direction.
25b is formed, and the cylinder 15 is supported by the convex portions 25a and 25b.The oil passages 23a and 23b are closed near the center of the cylinder case 10 to form a gear chamber 27, and the cylinder 15 is supported in the gear chamber 27. A rack 30 that is notched and formed near the center of the piston 16 faces the gear chamber 27, and a pinion 31 provided in the cylinder case 10 meshes with the rack 30. The pinion 31 drives the rudder, and the pinion 31 of the piston 16 is engaged with the rack 30. Both ends are formed into a tapered truncated cone shape,
This steering hydraulic actuation device is characterized in that concave portions 18 are concentrically formed in the center of both ends thereof, and a groove 19 extending in the radial direction is formed in the peripheral convex portion of each concave portion 18.

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

FIG. 1 is a perspective view of a ship steering system including a hydraulic actuator 5 according to an embodiment of the present invention.

Hydraulic oil from a reversible hydraulic pump 2 connected to the steering wheel 1 is supplied to the hydraulic actuation device 5 from either one of the pipes 4 and 6 via the compound check valve 3, and the return oil from there is supplied to the compound check valve 3. It is returned to the reversible hydraulic pump 2 via the valve 3 from the other of the pipes 4 and 6.

By driving the piston of the hydraulic actuation device 5,
The swing arm 7 is rotated, and the rudder 9 is thereby rotated via the link 8.

FIG. 2 is a sectional view along the axis of the hydraulic actuating device 5, and FIG. 3 is a sectional view taken from the section line ■-■ in FIG.
FIG. 4 is a sectional view taken along section line IV-IV in FIG. 2.

The hydraulic actuator 5 includes a cylinder case 10 and both cylinder chambers 20a and 2 by closing both ends of the cylinder case 1o.
a cap 11.12 forming a 0b.

Internal threads 13a and 13b are provided at both ends of the cylinder case 10.
are respectively carved, and outer threads 14a and 14b of the caps 11 and 12 are screwed into these inner threads 13a and 13b, respectively.

A cylinder 15 is fitted into the cylinder case 10.

The cylinder 15 is fixed with its both end faces abutting against the cap 11.12.

A piston 16 having a bilaterally symmetrical shape in FIG. 2 is fitted into the cylinder 15 so as to be slidable in the axial direction.

Both ends of the piston 16 are formed into tapered truncated conical shapes, and concave portions 18 are formed concentrically at the centers of both ends.

A groove 19 extending in the radial direction is formed in the peripheral convex portion of each recess 18 .

Therefore, if the piston 16 is axially
Even when the recess 18 moves to the right side in the figure and comes into contact with one of the caps 11, the recess 18 is inserted into the cylinder chamber 20a through the groove 19.
The pressure receiving area of the piston 16 is ensured.

At the end of the cap 11 facing inside the cylinder case 10,
A recess 21 is formed.

Therefore, the stroke of the piston 16 can be increased by the depth of the recess 21, and the inner thread 13a and the outer thread 14a can be made longer, allowing the cap 1
1 can be reliably attached to the cylinder case 10.

The peripheral convex portion of the cap 11 that comes into contact with the cylinder 15 has a
Grooves 22 extending in the radial direction are formed at four locations at intervals of 90 degrees in the circumferential direction, and the grooves 22 communicate one oil passage 23a with the cylinder chamber 20a.

The other cap 12 also has a similar structure to the cap 11.

Both ends of the cylindrical space of the cylinder case 10 are connected to the cylinder 15
An annular oil passage 23ay 23b extending in the axial direction of the cylinder 15 is formed between the cylinder 15 and the outer periphery of the cylinder 15.

The cylinder 15 has support portions 24 a and 24 b of the cylinder case 10 near the center in the axial direction, and radially inward convex portions 25 a and 25 b formed at four locations in the circumferential direction at both ends in the axial direction. Supported.

At both ends of the piston 16, O-rings 28 that slide into sliding contact with the inner circumferential surface of the cylinder 15 are provided closer to the center in the axial direction than the truncated conical portion.

, both cylinder chambers 20a, 20 by this O-ring 28.
b and the gear chamber 27 formed in the center of the cylinder case 10 are sealed.

Support parts 24a and 24b of cylinder case 10 are each provided with an O-ring 29 that contacts the outer peripheral surface of cylinder 15, and oil passages 23a and 23b and gear chamber 27 are sealed by these O-rings 29.

The axially central portion of the piston 16 has a substantially semicircular cross section perpendicular to the axis, and a rack 30 is formed along the axis.

A pinion 31 that meshes with the rack 30 is attached to the gear chamber 27.

A rotating shaft 33 is fixed to the pinion 31 by a key 3.2.

The swing arm 7 is fixed to the rotating shaft 33 by a half-moon key 34.

FIG. 5 is a front view of the hydraulic actuating device 5, and FIG. 6 is a bottom view thereof.

As is clear from FIG. 4, the axially central portion of the cylinder case 10 has a rectangular cross section perpendicular to the axis, and the wall portion 35
Oil holes 36 and 37 are formed in the oil passages 23a and 23b, respectively.

The oil holes 36 and 37 are each provided with internal threads, into which elbows 40 and 41 are screwed together to connect the pipe connection part 3.
8.39 is formed.

The connecting ends of the elbows 40, 41 with the conduits 4, 6 are connected to one end of the cylinder case 10 in the axial direction (for example, FIGS. 2 and 5).
(left side of the figure).

Moreover, the oil holes 36 and 37 are located at different positions in the circumferential direction of the cylinder case 10 (that is, in FIG.
0 above and below the axis 10a).

Therefore, when the conduit 4.degree. 6 is connected to the elbow 40.41, both the conduits 4 and 6 can extend straight and parallel.

At the center of the cylinder case 10 in the axial direction, two adjacent
Flat mounting portions 42, 43 are formed on the two peripheral wall portions.

Bolt holes 44 a to 44 d having internal threads are provided at each vertex of a virtual parallelogram of one attachment portion 42 .

In the other mounting portion 43, bolt holes 45a to 45d are provided at each vertex of an imaginary parallelogram having the same shape and size as the parallelogram.

The imaginary parallelograms of each mounting portion 42 , 43 are located at approximately the same position in the axial direction of the hydraulic actuator 5 .

In addition, the bolt holes 44a to 44d of the mounting portion 42 and the mounting portion 4
The bolt holes 45a to 45d of No. 3 do not intersect with each other due to the virtual parallelogram shape.

Therefore, the distance between the bolt holes in the direction perpendicular to the axis 10a can be made relatively large, and therefore the moment against falling when attached to the hull wall can be increased.

Also, bolt holes 44a to 44 in each mounting portion 42.43
d and 45a to 45d are not located on the same straight line in the direction perpendicular to the axis lea, so that cracks along the wood grain can be prevented when attached to a wooden wall of a ship or the like.

Each bolt hole 44a to 44d of the mounting part 42 is connected to the mounting part 4.
3 corresponds to each of the bolt holes 45a to 45d, respectively.

These corresponding bolt holes 44a, 45a have the same shape and size, and similarly, a pair of corresponding bolt holes 44b, 45b.
44c, 45c; 44d, 45d have the same shape and size.

In this embodiment, bolt holes 44a to 44d, 45a to 45
All d have the same shape and size.

By doing so, the hydraulic actuating device 5 can be easily installed on either a vertical or horizontal hull wall depending on the ship to which it is installed.

In the prior art, the mounting portion is formed only on one vertical or horizontal side.

Therefore, as shown in FIG. 7a, when a conventional hydraulic actuator 52 with a vertical mounting part is mounted on a horizontal hull wall 50, it must be mounted using an L-shaped fitting 51, which eliminates unnecessary parts. is necessary.

Moreover, the overall height when installed increases.

In the present hydraulic actuating device 5, the horizontal hull wall 50 as shown in FIG.
However, it can be installed directly.

Moreover, the bolt holes for installation are 50.4 on the same hull wall.
9 has the advantage that it can be molded in common.

A pair of piping connections are formed near the center of the cylinder case in the axial direction and near the attachment point to the hull wall, and each end of both cylinder chambers of the cylinder is connected along the axis between the inner surface of the cylinder case and the outer peripheral surface of the cylinder. Since the piping connection portions are connected to each of the piping connection portions through the oil passages formed to extend in the direction, the piping connection portions are provided at predetermined locations near the center of the cylinder case.

Therefore, in the prior art, the piping connections are formed at both ends of the cylinder case, so the structure for attaching the caps forming the cylinder chamber to both ends of the cylinder case is complicated, but in the present hydraulic actuator, the structure is complicated. becomes easier.

Further, as shown in FIG. 8, a hull wall 53 (for example, a deck)
The hydraulic actuator 5 is attached to the protrusion 53a of the pipe line 4, 6.
When the cylinder is drawn into the hull wall 53 through the hull wall 53, in the prior art, pipe connections are formed at both ends of the cylinder case, so the pipe line floats in the air as shown by the broken line.

Therefore, the pipe line may be damaged.

In the present hydraulic actuating device 5, since the piping connection portions 38 and 39 are formed closer to the center in the axial direction of the cylinder case 10,
The conduits 4, 6 can be led directly into the interior through the hull wall 53.

Therefore, the pipes 4 and 6 will not be suspended above the hull wall 53, and there is no risk of damage.

Further, since the pipe connecting portions 38 and 39 do not protrude outward in the axial direction of the cylinder case 10 as in the prior art, the installation space can be reduced.

Furthermore, since the pipe connection parts 38 and 39 are formed near the mounting parts, a single packing 54 seals the mounting bolt holes formed in the hull wall 53 and the holes through which the pipes 4 and 6 pass. can do.

Further, as shown in FIG. 9, a hydraulic actuator 5 is provided near a vertical hull wall 55, and a pipe 4 is installed along the hull wall 55.
, 6, the hydraulic actuator 5 can shorten the piping route compared to the prior art shown by the broken line.
Moreover, a rational piping route can be provided.

Furthermore, since the piping connections 38 and 39 do not protrude outward in the axial direction of the cylinder case 10, the hydraulic actuator 5 can be installed closer to the hull wall 55.

As described above, according to the present invention, the mounting portions near the center of the cylinder case 10 in the axial direction and attached to the hull are on a plane adjacent to the circumferential wall of the cylinder case 10, and the mounting portions on this plane are Bolt holes are formed at each vertex of a virtual parallelogram with the same size and shape, and the corresponding bolt holes are made to have the same shape and size, making it possible to easily change the location of the attachment to the ship, allowing for various installations. It is easily possible to fix and implement the steering hydraulic actuation device according to the present invention on a ship.

In addition, in the present invention, a pair of piping connection parts are formed near the mounting part located near the center of the cylinder case 10 in the axial direction, and each end of the cylinder chamber is connected between the inner circumferential surface of the cylinder case 10 and the outer circumferential surface of the cylinder 15. Since the oil passages 23a and 23b are formed to extend in the axial direction and communicate with each piping connection part, there is no need to perform piping outside the cylinder case 10, which simplifies the piping work. The present invention eliminates the problem of the external piping being caught and damaged if the piping is installed externally.

Furthermore, in the present invention, the rack 30 is formed on the piston 16, and the pinion provided on the cylinder case 10 meshes with the rack 30, so that the structure can be made smaller.

Both ends of the piston 16 are shaped like a tapered truncated cone, with a concave portion 18 formed in the center thereof, and a groove 1 formed in a convex portion of the periphery of each concave portion 18.
9, the piston 16 can be driven by pressure oil even at its extreme position.

[Brief explanation of the drawing]

FIG. 1 is a perspective view of a ship's steering system including a hydraulic actuating device 5 according to an embodiment of the present invention, FIG. 2 is a cross-sectional view of the hydraulic actuating device 5 along the axis, and FIG. 3 is a cross-sectional view of FIG. 2. 4 is a sectional view taken from the line IV--IV in FIG. 2, FIG. 5 is a front view of the hydraulic actuating device 5, and FIG.
The bottom view of the figure, FIG. 7 is a view showing the installed state of the hydraulic actuating device, and FIGS. 8 and 9 are views of the installed state for comparing the prior art and the present hydraulic actuating device. 5... Hydraulic actuation device, 9... Rudder, 10
... Cylinder case, 15 ... Cylinder, 16 ... Zeston, 20 a, 20 b
= cylinder chamber, 23at23b... oil passage, 38
．． 39... Piping connection, 42, 43 @-11
@64 mounting part, 44a to 44d, 45a to 45d...
...Bolt hole.

Claims (1)

[Scope of Claim for Utility Model Registration] In a hydraulic actuating device in which a cylinder 15 and a piston 16 are built in a cylinder case 10 for driving the rudder of a ship, a hydraulic actuator that is located near the center of the cylinder case 10 in the axial direction and near the attachment point to the ship's hull. A pair of piping connections are formed in the cylinder, and oil passages 23a and 23b are formed extending in the axial direction between the inner circumferential surface of the cylinder case 10 and the outer circumferential surface of the cylinder 15 at each end of both cylinder chambers of the cylinder. 7, forming coplanar mounting portions adjacent to each other on the circumferential wall of the cylinder case 10, each of which communicates with each of the pipe connection portions through the 7. Each mounting portion has an imaginary parallelogram having the same size and the same shape. An oil passage 23at2ab is formed in the cylinder case 10 by forming a bolt hole at each vertex of and making the corresponding bolt hole the same shape and size.
In the middle, there is a convex portion 25 a that protrudes inward in the radial direction.
25b is formed, the cylinder 15 is supported by the convex parts 25a and 25b, and near the center of the cylinder case 1.0, the oil passages 23a and 23b are closed to form a gear chamber 27, and the cylinder 15 is connected to the gear chamber. A rack 30 notched at 21 and formed near the center of the piston 16 faces the gear chamber 27, and a pinion 31 provided in the cylinder case 10 meshes with the rack 30, and this pinion 31 drives the rudder. Both ends of 16 are formed into a tapered truncated cone shape,
A bell recess 18 is concentrically formed in the center of both ends, and each recess 1
A steering hydraulic actuating device characterized in that a groove 19 extending in the radial direction is formed in the peripheral convex portion of 8.