JPH0246834B2 - YODOGATAKANTSUGITESOCHI - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a swing type pipe joint device suitable for use in fluid cargo handling equipment and the like.

``Prior Art'' For example, a fluid handling device is generally used when loading oil from an oil tanker docked at a sea berth to an onshore storage tank, or from a storage tank to an oil tanker. FIGS. 6 and 7 show this type of fluid handling device, and in the figures, reference numeral 1 indicates a riser pipe installed upright in a sea berth or the like. At the upper end of this riser pipe 1, there is an inboard arm 4 which can be rotated horizontally by a horizontal rotation cylinder 2 and vertically by an inboard cylinder 3, and which is connected to a hollow horizontal rotation joint 5 and a hollow vertical rotation joint 6. It is installed through. Also,
An outboard arm 7 is attached to the tip of the inboard arm 4 via a hollow vertical rotation joint 8 so as to be freely rotatable up and down. An inner balancing arm 10 having a main weight 9 is provided on the root end side of the inboard arm 4 and extends in the opposite direction to the inboard arm 4. A first sheave 13 is rotatably mounted together with an outer counterbalancing arm 12 having an outer counterbalance arm 11 . A second sheave 15 connected to the first sheave 13 via a transmission cable 14 is rotatably attached to the tip of the inboard arm 4, and the outboard arm 7 is fixed to the second sheave 15. ing. Further, an outboard cylinder 16 is connected between the inner balancing arm 10 and the first sheave 13, and by expanding and contracting the outboard cylinder 16, the first sheave 13, the transmission line 14, and the The outboard arm 7 can be rotated up and down via the two sheaves 15. When carrying out cargo handling of fluid, the coupler 17 at the tip of the outboard arm 7 is connected to a cargo handling pipe on the oil tanker, and the cargo handling operation can be started.

``Problems to be Solved by the Invention'' However, in the above-mentioned fluid cargo handling device, the mechanism for rotating each arm 4, 7 is complicated, and in particular, the rotation of the outboard arm 7 requires the outboard cylinder 16. In addition, weights 9 and 11, balancing arms 10 and 12, sheaves 13 and 15, transmission cables 14, etc. are also required, resulting in a large-scale device. Another drawback was that fine adjustments were required for operation.

The present invention was made in view of the above circumstances, and
When used in a fluid cargo handling device, conventional weights 9,
11, each balance arm 10, 12, each sheave 13, 15
It is an object of the present invention to provide a swing-type pipe joint device that can perform rotational operation of an outboard arm 7 without providing any equipment, and can be applied to various pipe joint parts other than fluid cargo handling equipment. aim.

"Means for Solving the Problems" The swing type pipe joint device of the present invention includes a cylindrical first pipe joint connected to the end of one pipe line, and a first pipe joint connected to the end of the other pipe line. a cylindrical second pipe joint,
An annular sealed space is formed between the radially opposing peripheral portions of the first pipe joint and the second pipe joint, and the sealed space is fitted into the sealed space in a circumferential direction. A vent and a partition member that are partitioned to form a plurality of internal chambers are fixedly disposed on one and the other of the first pipe joint and the second pipe joint, respectively, and the first pipe joint and the second pipe joint A driving fluid conduit is connected to one of the pipe joints for causing driving fluid to flow into or out of the internal chamber to apply driving pressure to the vane.

"Operation" In the above configuration, fluid passes through the flow path of each pipe joint and flows between each pipe line. In addition, when driving pressure is applied to the vane by causing the driving fluid to flow into and out of each internal chamber through the driving fluid pipe,
The vane moves circumferentially within the sealed space, and the pipe joint to which the vane is fixed rotates relative to the pipe joint to which the partition member is fixed.

When such a swinging type pipe joint device is used as a joint between the outboard arm and inboard arm of the above-mentioned fluid handling device, the conventional weights, sheaves, cylinders, etc. for rotating the outboard arm become unnecessary. The entire cargo handling device has an extremely simple structure.

"Embodiment" An embodiment of the present invention will be described below with reference to FIGS. 1 to 5.

In the figure, 20 is a first pipe joint fixed by welding or the like to the end of one pipe (not shown), and 21 is the other pipe having the same diameter as that of the above-mentioned one pipe (this (also not shown) is a second pipe joint fixed to the end of the pipe by welding or the like. The first and second pipe joints 20,
21 is a flow path 2 having the same diameter as the flow path of each of the above-mentioned pipes.
It has a substantially cylindrical shape with 0a and 21a, and is fitted into each other with flow paths 20a and 21a communicating with each other.

The first pipe joint 20 has a concave groove 22 with a rectangular cross section and a ball with a semicircular cross section on the outer periphery of the first pipe joint 20 near the inner end 20b on the left side in FIG. The housing groove 23 connects the concave groove 22 to the inner end 20b.
They are formed along the circumferential direction at intervals in the axial direction. Further, a reduced diameter portion 20d having a predetermined length in the axial direction is formed near the outer end 20c of the first pipe joint 20 on the right side in FIG. Reduced diameter part 20 at the end part
Step portion 24 extending in the circumferential direction and having a diameter further reduced than d
In addition, a ball accommodating groove 25 similar to the ball accommodating groove 23 described above is formed along the circumferential direction near the stepped portion 24 on the outer periphery of the reduced diameter portion 20d.

On the other hand, the second pipe joint 21 has the flow passage 21a formed at the inner end 21b on the right side in FIG. 2, which is fixed to the other pipe line.
On the outer side (left side in FIG. 2), there is an inner circumferential surface that has approximately the same length in the axial direction as the reduced diameter portion 20d of the first pipe joint 20, and has a slightly larger diameter than the reduced diameter portion 20d. An inner fitting portion 21c having a
On the outer side of c, an intermediate wall portion 21d having an inner circumferential surface having an inner diameter sufficiently larger than the outer diameter of the first pipe joint 20 and a predetermined length in the axial direction is continuously provided, and the intermediate wall portion 21d Further outward of the portion 21d, a first pipe joint 2 is provided.
An outer fitting portion 21e having an inner circumferential surface having a slightly larger diameter than the outer diameter of the outer fitting portion 21e is continuously provided. The second pipe joint 21 connects the outer end of the inner end 21b to the first pipe joint 20.
The inner fitting part 21c is connected to the reduced diameter part 20d of the first pipe joint 20, and the outer fitting part 2
1e are externally fitted onto the portions of the first pipe joint 20 near the inner end 20b, respectively, and are fitted into the first pipe joint 20.

In addition, the inner fitting part 21c of the second pipe joint 21
and the first pipe joint 2 on the inner circumferential surface of the outer fitting portion 21e.
Ball accommodating grooves 26 and 27 are formed along the circumferential direction to be combined with the ball accommodating grooves 23 and 25 of 0, respectively, and the outer edge of the inner fitting part 21c and the inner part of the outer fitting part 21e are formed along the circumferential direction. Step portions 28 and 29 extending in the circumferential direction are formed on each side edge. A plurality of steel balls 30, 31 are fitted into each ball accommodation groove 23, 26; , an annular dust seal 34 is installed in the concave groove 22, and an annular main seal member 35 is installed in the stepped portion 24 of the reduced diameter portion 20d.
0,21 relative rotation is allowed, and the outer peripheral surface of the first pipe joint 20 and the intermediate wall portion 2 of the second pipe joint 21
An annular sealed space 36 is formed between the inner circumferential portion 1d and the inner peripheral portion 1d.

Inside the sealed space 36, a pair of partition members 37, 37 that divide the sealed space 36 into two equal parts in the circumferential direction are fitted in a liquid-tight manner with a distance of 180 degrees from each other in the circumferential direction.
These partition members 37, 37 are fixed to the intermediate wall 21d of the second pipe joint 21 from the outside by a plurality of bolts 38, and are secured by respective fastening pins 39, 39 that protrude inward from the intermediate wall 21d. Each of them is fixed. Further, a pair of vanes 40, 40, which are fluid-tightly fitted into the sealed space 36, are fixedly implanted on the outer circumferential surface of the first pipe joint 20 at a distance of 180 degrees from each other in the circumferential direction. , these vanes 40,4
0 and the partition members 37, the sealed space 36 is partitioned in the circumferential direction into four internal chambers 41.
a,...41d are formed. Further, the outer end surface 2 of the intermediate wall portion 21d of the second pipe joint 21
In 1f, among the internal chambers 41a, ..., 41d,
First ports 42a, 42c that communicate the pair of internal chambers 41a, 41c facing each other to the outside are formed close to one side of the partition members 37, 37, respectively, while the inner end surface of the intermediate wall 21d 21g
, a pair of other internal chambers 41b facing each other,
41d to the outside, the second port 42b, 4
2d are formed close to the other side of the partition members 37, 37, respectively. Then, the first port 4
A first hydraulic line 43 connected to a hydraulic system (not shown) is connected to the ports 2a and 42c, and a second hydraulic line 44 similarly connected to the hydraulic system is connected to the second ports 42b and 42d. is connected. In addition, in the figure, 45 is an O-ring, and 46 is each ball accommodation groove 2.
3, 26; 25, 27 are closing screws that close the holes 47 into which the steel balls 30, 31 are inserted.

Next, the operation of the pipe joint device having the above configuration will be explained. In the state shown in FIG. 1, from the hydraulic system (not shown) to the first hydraulic pipe 43 and the first port 42
Pressure oil flows into the internal chambers 41a, 41c through the second ports 42b, 42d, and the second ports 42b, 42d.
When pressure oil flows out from the internal chambers 41b, 41d through the hydraulic pipe line 44, hydraulic pressure acts on each vane 40, 40 to move it counterclockwise in FIG. 1, and as a result, the first pipe joint 20 in the counterclockwise direction in FIG.
The fitting rotates in a clockwise direction. Then, each pipe line to which the first and second pipe joints 20 and 21 are connected rotates relative to each other. In the illustrated example, this rotation is
In FIG. 1, it is possible to rotate the angle α up to 120 degrees. Also, if you want to reverse the rotation direction,
All you have to do is reverse the flow of pressure oil.

When the above-mentioned pipe joint device is used in place of the hollow vertical rotation joint 8 of the fluid cargo handling device shown in FIGS. 6 and 7, the weight 11 for rotating the outboard arm 7, each The sheaves 13, 15, transmission cable 14, etc. are no longer necessary, and the structure of the device is greatly simplified. Here, some additional notes will be made regarding how much hydraulic pressure should be applied to the pipe joint device. In Fig. 5, the length L of the outboard arm 7 is 12 m, the load W applied to the tip of the outboard arm 7 is 600 kg, and the pipe diameter is 16 inches (schedule 40). The moment M ₁ is M ₁ =600×12+78.8×12×12/2=12837.6Kg−m. On the other hand, if the hydraulic pressure P applied to the pipe joint device A is, for example, 100 Kg/cm ² and the total pressure-receiving area B of the vanes 40, 40 is 400 cm ² , then the output torque T is T=B×P×0.55/2 = 11000Kg-m. Therefore, it can be seen that the oil pressure P should be slightly higher than 100 kg/cm ² or the total pressure receiving area B of the vanes 40, 40 should be slightly larger than the above.

By the way, in the above embodiment, the vane 40,
The number of partition members 37 is not limited to two,
The number is arbitrary, and the vane 40 may be fixed to the second pipe joint 21 side, and the partition member 37 may be fixed to the first pipe joint 20 side.

"Effects of the Invention" As explained above, the swing type pipe joint device of the present invention can seal the first pipe joint provided in one pipe line and the second pipe joint provided in the other pipe line between them. forming a space and fitting each other so as to be relatively rotatable, and in the sealed space, a vane is fixed to one of the first pipe joint and the second pipe joint, and a partition member is fixed to the other, The driving fluid is caused to flow into and discharged from the plurality of internal chambers defined by the vanes and the partition member, and fluid pressure is applied to the vanes, thereby causing each pipe line to rotate relative to each other. Therefore, each conduit can be freely rotated relative to each other with an extremely simple structure. Therefore,
When this pipe joint device is used in a fluid cargo handling device, sub-weights, external balance arms, sheaves, transmission cables, etc. are completely unnecessary, making the structure of the cargo handling device extremely simple, and detailed adjustments are not required. become. Furthermore, the device of the present invention can be widely applied to various piping joints other than fluid cargo handling devices.

[Brief explanation of the drawing]

1 to 5 show an embodiment of the pipe joint device of the present invention, in which FIG. 1 is a cross-sectional view, FIG. 2 is a cross-sectional view taken along the - arrow in FIG. 1, and FIG. 4 is a view in the same direction, FIG. 5 is an explanatory diagram for calculating the necessary hydraulic pressure, etc., FIG. 6 is a side view of the fluid cargo handling device, and FIG. FIG. 20...First pipe joint, 21...Second pipe joint, 3
6... Sealed space, 40... Vane, 41a,...,
41d...internal chamber, 43...first hydraulic pipe line (driving fluid pipe line), 44...second hydraulic pipe line (driving fluid pipe line).

Claims (1)

[Claims] 1 A cylindrical first pipe joint having an internal fluid flow path, and a cylindrical second pipe joint having an internal flow path communicating with the flow path of the first pipe joint, the first pipe joint An annular sealed space is formed between the radially opposing peripheral portions of the second pipe joint and the second pipe joint, and the pipe fittings are fitted to each other so as to be relatively rotatable, and the sealed space is provided with a circumferentially circumferentially dividing section of the sealed space. A vane and a partition member forming a plurality of internal chambers are fixedly disposed on one and the other of the first pipe joint and the second pipe joint, respectively, and A swing-type pipe joint device, characterized in that a driving fluid conduit is connected to either of them to apply driving pressure to the vane by causing driving fluid to flow into or be discharged from the internal chamber.