Ship unloader

Abstract

To provide an unloader for vessels that can render a structure of a turning mechanism to turn a boom more compact.SOLUTION: An unloader for vessels 10 includes a turning mechanism 15 for turning a boom 13. The turning mechanism 15 includes a driven gear 29 and two driving gears 32R, 32L to be powered from a hydraulic mechanism 26. The driving gears 32R, 32L are rotary gears lined up in circumferential direction C of the driven gear 29. The hydraulic mechanism 26 is capable of executing a driving turn mode for turning a turn base 21 by the two driving gears 32R, 32L and a lock mode for locking the two driving gears 32R, 32L after reversing the turning direction of the driven gear 29 by drive of the two driving gears 32R, 32L to squash the back lash.SELECTED DRAWING: Figure 5

Description

Technical Field

[0001] The present invention relates to a ship unloader.

Background Art

[0002] A slewing crane installed on a fishing boat and supporting a net winch and a net feeder is known (see, for example, Patent Document 1). In this slewing crane, the lower portion of a slewing support member 2 that supports a boom 1 is rotatably supported via a bearing 26 by a support base 3 fixed to the hull 15 of the fishing boat. A gear 4 coaxial with the rotation center of the slewing support member 2 is integrally provided at the lower end of the slewing support member 2. Also, a pair of elongated racks 5 and 6 that mesh with the gear 4 are provided. By moving the racks 5 and 6 in the longitudinal direction of the racks 5 and 6, the gear 4 is rotated, and thereby, the boom 1 is rotated.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] By the way, in a large ship such as a bulk carrier that transports a large amount of bulk materials such as ore, a slewing crane may be used to unload the bulk materials. This slewing crane has a large boom, and the bulk materials are unloaded from the ship by a conveyor belt attached to the boom. Since this slewing crane is large, the boom and the slewing mechanism for slewing the boom are large and occupy a large space. However, various devices other than the slewing crane are installed in the limited space on the deck. For this reason, it is better that the space occupied by the slewing crane is smaller. On the other hand, in the configuration described in Patent Document 1, the long racks 5 and 6 project greatly around the slewing support member 2. In particular, when such a configuration is adopted for the slewing crane of a large ship, the rack projects greatly around the slewing base. For this reason, the space occupied by the slewing mechanism of the slewing crane becomes large.

[0005] In view of the above circumstances, an object of the present invention is to provide a ship unloader capable of making the configuration of a slewing mechanism for slewing a boom more compact.

Means for Solving the Problems

[0006] The gist of the present invention is the following ship unloader.

[0007] (1) A conveyor belt for transporting an object to be conveyed from the hull to the outside of the hull, A boom that supports the conveyor belt, A slewing mechanism for slewing the boom around a slewing axis that extends vertically with respect to the hull as an axis extending above and below the hull, Comprising The slewing mechanism includes a drive source, at least two drive gears that are powered by the drive source, and a driven gear that is driven by each of the drive gears. The driven gear is a rotating gear that is connected to the boom so as to be capable of interlocking rotation around the slewing axis, and each of the drive gears is a rotating gear that is attached to the hull and arranged in the circumferential direction of the driven gear. The drive source is configured to be capable of executing a drive slewing mode in which the boom is slewed with the rotation directions of the driven gears made the same by driving each of the drive gears, and a lock mode in which the rotation directions of the two drive gears are made opposite by driving the two drive gears and then the two drive gears are locked, for a ship unloader.

[0008] (2) The slewing mechanism is configured to be capable of executing a rotation allowance mode that allows the boom to rotate around the slewing axis with respect to the hull. In the rotation allowance mode, free rotation of each of the drive gears is allowed, or a predetermined rotational resistance is applied to the rotation of at least one of the drive gears, for the ship unloader according to (1) above.

[0009] (3) A hose extending from the hull side to the boom side, a Cablebear (registered trademark) having a plurality of link plates and holding the hose, and further includes The Cablebear (registered trademark) includes an upper region arranged around the slewing axis, a lower region arranged below the upper region, and an intermediate region arranged between the upper region and the lower region, and is configured such that the position of the intermediate region around the slewing axis moves according to the position of the boom around the slewing axis. The upper region and the lower region are arranged such that the distance between them increases as they proceed radially outward from the slewing axis, for the ship unloader according to (1) or (2) above.

[0010] (4) The upper region and the lower region are arranged symmetrically with respect to the slewing axis direction, for the ship unloader according to (3) above.

Advantages of the Invention

[0011] According to the present invention, the configuration of the slewing mechanism for slewing the boom can be made more compact.

Brief Description of the Drawings

[0012]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Embodiments for Carrying Out the Invention

[0013] Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.

[0014] Figure 1 is a schematic plan view of a ship unloader 10 according to an embodiment of the present invention and a ship 1 on which the ship unloader 10 is installed. Figure 2 is a side view of a main part of the ship unloader 10. Figure 3 is a schematic rear view of the periphery of the slewing mechanism 15 of the ship unloader 10. Figure 4 is a partial cross-sectional plan view of a main part for explaining the configuration of the slewing mechanism 15. Figure 5 is a schematic view of a main part related to the hydraulic mechanism 26 in the slewing mechanism 15. Figure 6 is a schematic perspective view of the periphery of the Cable Bear (registered trademark) 28 of the ship unloader 10. Figure 7 is a schematic partial cross-sectional side view for explaining the configuration of the Cable Bear (registered trademark) 28.

[0015] With reference to Figures 1 to 3, a ship unloader 10 is installed on a ship 1 which transports bulk materials 200 (multiple chunks) such as limestone, iron ore, coal, etc. by sea. The ship 1 has a hold 4 in which the bulk materials 200 are stored. A bulk material transport mechanism (not shown) is installed within the ship 1. This bulk material transport mechanism transports the bulk materials 200 from the hold 4 to a belt conveyor 14 of the ship unloader 10, which will be described later. The ship unloader 10 is installed on a deck 3 of a hull 2 of the ship 1.

[0016] The ship unloader 10 is installed on a block-shaped pedestal 5 installed on the deck 3 of the hull 2. When the ship 1 is moored at a quay, the ship unloader 10 transports the bulk material 200 discharged from the above-mentioned bulk material transport mechanism and discharges it to a hopper 100 installed at the quay. A belt conveyor (not shown) is connected to the hopper 100. This belt conveyor transports the bulk material 200 to a bulk material storage area (not shown).

[0017] The ship unloader 10 is configured to be able to rotate (swing) relative to the hull 2 about a vertical pivot shaft 11, and is also configured to be able to tilt (swing) about a horizontal tilt shaft 12. This allows the ship unloader 10 to move from a state in which it is disposed inside the hull 2 in a plan view to a position (protruding position) in which it protrudes outside the hull 2 in a plan view and faces the hopper 100 vertically.

[0018] The ship unloader 10 has a boom 13, a belt conveyor 14 attached to the boom 13, a rotation mechanism 15 arranged at the base end 10b of the ship unloader 10 for rotating the boom 13 around the rotation axis 11 relative to the hull 2, an elevation mechanism 16 for elevating the boom 13 around the elevation axis 12 relative to the hull 2, and a chute 18 attached to the tip end 10a of the ship unloader 10.

[0019] The boom 13 is an arm-shaped member that supports the belt conveyor 14. An arm 19 extends downward from the tip 13d of the boom 13, and a landing wheel 20 is attached to the tip of this arm 19. When unloading the bulk goods 200, the landing wheel 20 is placed on the hopper 100 and supports the boom 13. The landing wheel 20 is rotatably supported by the arm 19 about an axis extending in the left-right direction of the boom 13.

[0020] The boom 13 has an upper part 13a, a lower part 13b, and a connecting part 13c that connects the upper part 13a and the lower part 13b, and includes a truss structure. The upper part 13a and the lower part 13b of the boom 13 are arranged vertically and extend from the base end 10b to the tip end 10a of the ship unloader 10. The connecting part 13c is disposed between the upper part 13a and the lower part 13b. A belt conveyor 14 is installed on the boom 13. The bulk goods 200 are placed on the belt conveyor 14.

[0021] The belt conveyor 14 has a conveyor belt 14a for conveying the bulk goods 200 (objects to be conveyed) from the side of the hull 2 to the outside of the hull 2, a plurality of support rollers 14b for supporting the conveyor belt 14a, and a conveyor motor 14c for driving the conveyor belt 14a.

[0022] The conveyor belt 14a is a flexible belt arranged in an endless shape in side view and is arranged from the base end 10b to the tip end 10a of the ship unloader 10. An upper chute 22 from which the bulk goods 200 from the above-described bulk goods conveying mechanism are discharged is installed above the conveyor belt 14a at the base end 10b. The conveyor belt 14a conveys the bulk goods 200 from the base end 10b to the tip end 10a as the conveyor belt 14a is rotationally driven. A chute 18 is installed below the conveyor belt 14a at the tip end 10a, and the bulk goods 200 fall from the conveyor belt 14a toward the chute 18.

[0023] The conveyor motor 14c is, for example, an electric motor, and the conveyor belt 14a is rotationally driven by the output rotation of the conveyor motor 14c.

[0024] The pitching support shaft 12 is disposed at the lower part 13b of the base end portion 13e of the boom 13. The pitching support shaft 12 is a shaft that extends horizontally when the deck 3 is in a horizontal posture. The pitching support shaft 12 connects the boom 13 and the turntable 21. The turntable 21 is a rotating table disposed below the boom 13 at the base end portion 13e, and is placed on the pedestal 5 via a thrust bearing (not shown) or the like. Further, a slewing support shaft 11 extending downward from the turntable 21 is installed, and the turntable 21 is rotatable around the slewing support shaft 11 with respect to the pedestal 5 (hull 2). The turntable 21 and the boom 13 are slewed by a slewing mechanism 15.

[0025] Referring to FIGS. 2 to 6, the slewing mechanism 15 is provided for slewing the boom 13 around a slewing axis S that is an axis extending vertically with respect to the hull 2 of the hull 2. The slewing mechanism 15 is disposed below the base end portion 13e. In the present embodiment, the slewing mechanism 15 is disposed compactly around the base end portion 13e.

[0026] The slewing mechanism 15 includes a slewing support shaft 11, a turntable 21, a starboard motor unit 25R and a port motor unit 25L, a hydraulic mechanism 26 for supplying and discharging hydraulic oil to and from these motor units 25R, 25L, a first hose 27 extending from the hull 2 side to the boom 13 side, a Cable Bear (registered trademark) 28 for holding the first hose 27, a second hose 30 connected to the first hose 27, and a driven gear 29.

[0027] Referring to FIGS. 2 to 5, in the present embodiment, the turntable 21 is formed in a fan shape. A driven gear 29 is formed on the outer peripheral portion of the turntable 21. The driven gear 29 is an external gear and is integrally formed with the turntable 21 in the present embodiment. The driven gear 29 has a plurality of teeth 29a arranged at equal pitches in the circumferential direction of the turntable 21. Each tooth 29a is formed on the outer peripheral portion of the turntable 21 and is disposed in a recess 21a formed on the outer peripheral portion of the turntable 21 and extending in the circumferential direction C of the turntable 21. Each tooth 29a is formed, for example, by a pin attached to the turntable 21 and extending parallel to the turning axis S. The driven gear 29 rotates integrally with the turntable 21 about the turning axis S. The turntable 21 is connected to the boom 13 by a pitching support shaft 12 so as to be integrally rotatable about the turning axis S. Thereby, the driven gear 29 serves as a rotating gear that is connected to the boom 13 so as to be interlockingly rotatable about the turning axis S.

[0028] The two motor units 25R and 25L transmit a driving force that cooperatively rotates the turntable 21 and the boom 13 about the turning axis S to the driven gear 29. In the present embodiment, the motor units 25R and 25L are disposed adjacent to an upper chute 22 through which the bulk cargo 200 is discharged from the inside of the cargo hold 4 to the outside of the cargo hold 4. The upper chute 22 is a hollow box-shaped body that rises upward from the deck 3 and protrudes toward the boom 13 above the base end portion 13e of the boom 13, and the bulk cargo 200 passes through the inside thereof.

[0029] The upper chute 22 has a vertical wall 22a rising from the deck 3 and a protruding portion 22b protruding from the upper end of the vertical wall 22a toward the conveyor belt 14a side. The vertical wall 22a is adjacent to the turning mechanism 15, for example, on the stern side. The turning mechanism 15 is disposed below the protruding portion 22b. By disposing the turning mechanism 15 in the space below the protruding portion 22b in this way, the upper chute 22 and the turning mechanism 15 can be disposed compactly. Further, the upper chute 22 serves as a protective wall for the turning mechanism 15 and protects the turning mechanism 15 from wind and rain.

[0030] The motor units 25R and 25L are collectively arranged around the upper chute 22, and the space on the deck 3 is effectively utilized. The motor units 25R and 25L are arranged at a pitch narrower than 180 degrees in the circumferential direction C of the slewing base 21 (in this embodiment, at a pitch of 60 degrees) between the pedestal 5 and the upper chute 22.

[0031] In this embodiment, the starboard motor unit 25R is arranged on the starboard side of the hull 2, and the port motor unit 25L is arranged on the port side of the hull 2. Note that the motor units 25R and 25L may both be arranged on the starboard side of the hull 2 or on the port side of the hull 2. The motor units 25R and 25L are driven by hydraulic pressure in this embodiment.

[0032] The starboard motor unit 25R includes a starboard hydraulic motor 31R, a starboard drive gear 32R that is rotationally driven by the starboard hydraulic motor 31R, and a starboard intermediate gear body 33R that is rotationally driven by the starboard drive gear 32R.

[0033] The starboard hydraulic motor 31R is configured to be rotationally driven by the flow of hydraulic oil from the hydraulic mechanism 26. The starboard hydraulic motor 31R includes a starboard housing 34R fixed to the pedestal 5, a starboard output shaft 35R protruding from the housing 34R, and a starboard brake 36R that restricts the rotation of the starboard output shaft 35R.

[0034] The starboard housing 34R is arranged above the pedestal 5, and an operating oil passage is formed inside. The starboard housing 34R is provided with a starboard first port 41R, a starboard second port 42R, and a starboard third port 43R. Each starboard port 41R - 43R is shown in FIG. 5. Each starboard port 41R - 43R is connected to the hydraulic mechanism 26 and supplied with operating oil from the hydraulic mechanism 26. The starboard first port 41R and the starboard second port 42R are ports through which the operating oil for rotationally driving the starboard output shaft 35R passes. In this embodiment, when the operating oil enters from the starboard first port 41R and exits from the starboard second port 42R, a rotational force for rotating the driven gear 29, the slewing platform 21, and the boom 13 to the right is generated on the starboard output shaft 35R. Also, when the operating oil enters from the starboard second port 42R and exits from the starboard first port 41R, a rotational force for rotating the driven gear 29, the slewing platform 21, and the boom 13 to the left is generated on the starboard output shaft 35R. The starboard third port 43R is connected to the starboard brake 36R. When the hydraulic pressure of the operating oil from the starboard third port 43R acts on the starboard brake 36R, or when the hydraulic pressure of the operating oil from the starboard third port 43R is released, the starboard brake 36R brakes the starboard output shaft 35R so that the starboard output shaft 35R cannot rotate.

[0035] A part of the starboard output shaft 35R protrudes upward from the starboard housing 34R, and the starboard drive gear 32R is integrally and rotatably connected to this protruding part. The starboard output shaft 35R extends parallel to the slewing axis S. With the above configuration, the starboard drive gear 32R is a rotating gear attached to the hull 2, and is rotationally driven by receiving power from the hydraulic mechanism 26 as a drive source.

[0036] The starboard intermediate gear body 33R is arranged between the drive gears 32R and 32L in the circumferential direction C. The starboard intermediate gear body 33R is provided for transmitting power between the starboard drive gear 32R and the driven gear 29, for adjusting the reduction ratio between the starboard drive gear 32R and the driven gear 29, and for adjusting the height positions of the starboard drive gear 32R and the driven gear 29. In this embodiment, the starboard intermediate gear body 33R includes a starboard support shaft 33aR rotatably supported by the pedestal 5 via a bearing (not shown), a starboard lower intermediate gear 33bR formed at the lower part of the starboard support shaft 33aR and meshing with the starboard drive gear 32R, and a starboard upper intermediate gear 33cR formed at the upper part of the starboard support shaft 33aR and meshing with the driven gear 29. The starboard support shaft 33aR, the starboard lower intermediate gear 33bR, and the starboard upper intermediate gear 33cR rotate integrally about an axis parallel to the turning axis S. By changing the number of teeth of each of the starboard lower intermediate gear 33bR and the starboard upper intermediate gear 33cR, the speed ratio between the starboard drive gear 32R and the driven gear 29 can be changed. With the above configuration, the starboard hydraulic motor 31R, which is a heavy object, can be arranged at a low position on the pedestal 5, and a pedestal for lifting the starboard hydraulic motor 31R to the height position of the driven gear 29 is not required, and the ship unloader 10 can be made more compact.

[0037] In this embodiment, the port motor unit 25L is arranged symmetrically with the starboard hydraulic motor 31R in the left - right direction of the hull 2.

[0038] The port motor unit 25L includes a port hydraulic motor 31L, a port drive gear 32L rotationally driven by the port hydraulic motor 31L, and a port intermediate gear body 33L rotationally driven by the port drive gear 32L.

[0039] The port hydraulic motor 31L is configured to be rotationally driven when hydraulic oil from the hydraulic mechanism 26 flows through it. The port hydraulic motor 31L includes a port housing 34L fixed to the pedestal 5, a port output shaft 35L protruding from this housing 34L, and a port brake 36L for restricting the rotation of the port output shaft 35L.

[0040] The starboard housing 34L is disposed above the pedestal 5, and an operating oil passage is formed therein. The starboard housing 34L is provided with a starboard first port 41L, a starboard second port 42L, and a starboard third port 43L. Each of the starboard ports 41L to 43L is shown in FIG. 5. Each of the starboard ports 41L to 43L is connected to the hydraulic mechanism 26 and supplied with operating oil from the hydraulic mechanism 26. The starboard first port 41L and the starboard second port 42L are ports through which the operating oil for rotationally driving the starboard output shaft 35L passes. In the present embodiment, when the operating oil enters from the starboard first port 41L and exits from the starboard second port 42L, a rotational force for rotating the driven gear 29, the slewing platform 21, and the boom 13 clockwise is generated on the starboard output shaft 35L. Also, when the operating oil enters from the starboard second port 42L and exits from the starboard first port 41L, a rotational force for rotating the driven gear 29, the slewing platform 21, and the boom 13 counterclockwise is generated on the starboard output shaft 35L. The starboard third port 43L is connected to the starboard brake 36L, and when the hydraulic pressure of the operating oil from the starboard third port 43L acts on the starboard brake 36L, or when the hydraulic pressure of the operating oil from the starboard third port 43L is released, the starboard brake 36L brakes the starboard output shaft 35L so as not to rotate the starboard output shaft 35L.

[0041] A part of the starboard output shaft 35L protrudes upward from the starboard housing 34L, and a starboard drive gear 32L1 is integrally and rotatably connected to this protruding portion. The starboard output shaft 35L extends parallel to the slewing axis S. With the above configuration, the starboard drive gear 32L is a rotating gear attached to the hull 2, and is rotationally driven by receiving power from the hydraulic mechanism 26 as a drive source.

[0042] The starboard intermediate gear body 33L is disposed between the drive gears 32R and 32L in the circumferential direction C. The starboard intermediate gear body 33L is provided for transmitting power between the starboard drive gear 32L and the driven gear 29, for adjusting the reduction ratio between the starboard drive gear 32L and the driven gear 29, and for adjusting the height positions of the starboard drive gear 32L and the driven gear 29. In the present embodiment, the starboard intermediate gear body 33L includes a starboard support shaft 33aL rotatably supported by the pedestal 5 via a bearing (not shown) in the circumferential direction C, a starboard lower intermediate gear 33bL formed at the lower part of the starboard support shaft 33aL and meshing with the starboard drive gear 32L, and a starboard upper intermediate gear 33cL formed at the upper part of the starboard support shaft 33aL and meshing with the driven gear 29. The starboard support shaft 33aL, the starboard lower intermediate gear 33bL, and the starboard upper intermediate gear 33cL rotate integrally about an axis parallel to the turning axis S. By changing the number of teeth of each of the starboard lower intermediate gear 33bL and the starboard upper intermediate gear 33cL, the transmission ratio between the starboard drive gear 32L and the driven gear 29 can be changed. With the above configuration, the starboard hydraulic motor 31L, which is a heavy object, can be disposed at a low position on the pedestal 5, and a pedestal for lifting the starboard hydraulic motor 31L to the height position of the driven gear 29 is unnecessary, and the ship unloader 10 can be made more compact.

[0043] In the present embodiment, the pitch circle diameters of the two drive gears 32R and 32L are smaller than the pitch circle diameter of the driven gear 29. Also, the pitch circle diameters of the two intermediate gear bodies 33R and 33L are smaller than the pitch circle diameter of the driven gear 29.

[0044] With the above configuration, the two drive gears 32R and 32L powered by the hydraulic mechanism 26 drive the driven gear 29 via the corresponding intermediate gear bodies 33R and 33L. Note that the two drive gears 32R and 32L may mesh directly with the driven gear 29.

[0045] The hydraulic mechanism 26 is an example of the "drive source" of the present invention. The hydraulic mechanism 26 may be arranged, for example, inside the pedestal 5, or may be arranged on the pedestal 5 around the hydraulic motors 31R and 31L. The hydraulic mechanism 26 supplies and discharges (supplies and discharges) hydraulic oil from a hydraulic pump driven by a power source such as a diesel engine of the ship 1 to the ports 41R to 43R and 41L to 43L of each of the hydraulic motors 31R and 31L. The hydraulic mechanism 26 has a plurality of ports. Each port of the hydraulic mechanism 26 is connected to the corresponding ports 41R to 43R and 41L to 43L of the hydraulic motors 31R and 31L via a hydraulic hose or the like.

[0046] <Configuration for operating the boom 13 and the slewing platform 21> (1. Configuration for executing a driving slewing mode in which the boom 13 and the slewing platform 21 are slewed by the hydraulic oil of the hydraulic mechanism 26) When starting or completing the unloading of the bulk cargo 200, etc., the boom 13 may be slewed right or left around the slewing axis S between the left - right center position of the ship 1 and the hopper 100. In this case, when the hydraulic mechanism 26 slews the slewing platform 21 to the right, it supplies hydraulic oil to the first ports 41R and 41L of each of the hydraulic motors 31R and 31L, and discharges hydraulic oil from the second ports 42R and 42L of each of the hydraulic motors 31R and 31L. On the other hand, when the hydraulic mechanism 26 slews the slewing platform 21 to the left, it supplies hydraulic oil to the second ports 42R and 42L of each of the hydraulic motors 31R and 31L, and discharges hydraulic oil from the first ports 41R and 41L of each of the hydraulic motors 31R and 31L. At this time, the hydraulic mechanism 26 supplies and discharges hydraulic oil to the third ports 43R and 43L so that the brakes 36R and 36L of each of the hydraulic motors 31R and 31L are released. With such a configuration, in the driving slewing mode, the hydraulic mechanism 26 rotates the boom 13 with the rotation directions of the driven gear 29 driven by the two driving gears 32R and 32L being the same.

[0047] (2. Configuration for executing a free slewing mode in which the boom 13 and the slewing platform 21 are freely slewed) The free rotation mode is the first example of the "rotation - allowing mode that allows the boom to rotate around the rotation axis with respect to the hull" of the present invention. For example, in a state where the waves are small, such as in a calm state, when the landing wheels 20 are supported by the on - shore hopper 100, or when the tip 13d floats from the hopper 100, and the bulk goods 200 are being unloaded from the boom 13 to the on - shore hopper 100, the boom 13 may be set to the free rotation mode. In this case, the hydraulic oil between the hydraulic mechanism 26 and the first and second ports 41R, 41L, 42R, 42L of each hydraulic motor 31R, 31L is not pressurized. And the hydraulic mechanism 26 allows the free entry and exit of the hydraulic oil to and from the first and second ports 41R, 41L, 42R, 42L of each hydraulic motor 31R, 31L. As a result, the output shafts 33R, 33L and the drive gears 32R, 32L of each hydraulic motor 31R, 31L are in a freely rotatable state, and the boom 13 can be freely rotated around the rotation axis S. At this time, the hydraulic mechanism 26 supplies and discharges the hydraulic oil to and from each third port 43R, 43L so that the brakes 36R, 36L of each hydraulic motor 31R, 31L are released.

[0048] (3. Configuration for executing a soft - brake mode that applies a certain brake to the turning operation of the boom 13 while allowing the boom 13 and the slewing platform 21 to rotate freely due to an external force from outside the ship unloader 10) The slow braking mode is the second example of the "rotation allowance mode that allows the boom to rotate around the turning axis with respect to the hull" of the present invention. For example, when unloading the cargo 200 from the boom 13 to the onshore hopper 100 with the landing wheels 20 supported by the onshore hopper 100 at a quay facing the open sea, the hull 2 may be shaken greatly by waves. In such a case, while the tip 13d of the boom 13 is received by the hopper 100, the base end 13e of the boom 13 is supported by the hull 2, so that the boom 13 swings around the turning axis S with the tip 13d as a fulcrum. In order to suppress this swinging, the slow braking mode may be executed. In this case, the turning mechanism 15 operates to apply a certain brake to the turning of the driven gear 29, the turntable 21, and the boom 13 by the cooperation of the drive gears 32R and 32L. Specifically, the hydraulic mechanism 26 supplies, for example, hydraulic oil of a first hydraulic pressure lower than the hydraulic pressure in the driving turning mode (the force to turn the boom 13 to the right) to the starboard first port 41R of the starboard hydraulic motor 31R, and at the same time, supplies the hydraulic oil of the first hydraulic pressure (the force to turn the boom 13 to the left) to the port second port 42L of the port hydraulic motor 31L. As a result, the backlash between each drive gear 32R, 32L and the driven gear 29 is filled and they mesh in a state without a gap, suppressing the driven gear 29 from both directions in the circumferential direction C. Thereby, when the boom 13 turns to the right, a brake is applied to the right turn by the force from the port hydraulic motor 31L, and when the boom 13 turns to the left, a brake is applied to the left turn by the force from the starboard hydraulic motor 31R. That is, a predetermined rotational resistance is imparted to the rotation of each drive gear 32R, 32L.

[0049] When executing the slow braking mode, the hydraulic mechanism 26 may supply the hydraulic oil of the first hydraulic pressure (the force to turn the boom 13 to the left) to the starboard second port 42R of the starboard hydraulic motor 31R, and at the same time, supply the hydraulic oil of the first hydraulic pressure (the force to turn the boom 13 to the right) to the port first port 41L of the port hydraulic motor 31L.

[0050] Also, when executing the creep brake mode, the hydraulic mechanism 26 may apply a predetermined rotational resistance to the output shafts 33R and 33L (drive gears 32R and 32L) by narrowing the hydraulic oil passage area between the first ports 41R and 41L and the second ports 42R and 42L for at least one of the hydraulic motors 31R and 31L using a variable orifice or the like.

[0051] (4. Configuration for Executing a Lock Mode to Restrict the Swiveling of the Boom 13 and the Slewing Platform 21) The slewing platform 21 and the boom 13 are fixed by being set in the lock mode so as not to move at the center in the left - right direction of the ship 1 during the navigation of the ship 1. When the lock mode is executed, the hydraulic mechanism 26 first closes the backlash between each drive gear 32R, 32L and the driven gear 29. Specifically, the hydraulic mechanism 26 supplies hydraulic oil (force to turn the boom 13 clockwise) to the first port 41R or 41L of either one of the hydraulic motors 31R, 31L, and at the same time, supplies hydraulic oil (force to turn the boom 13 counterclockwise) to the second port 42R, 42L of the other hydraulic motor 31R, 31L. Thereby, each drive gear 32R, 32L (upper intermediate gears 33cR, 33cL) meshes with the driven gear 29 without a gap and presses the driven gear 29 from both directions in the circumferential direction C to prevent the driven gear 29 from vibrating due to the sway during navigation. In this way, the drive gears 32R, 32L lock the swiveling operation of the driven gear 29 and the boom 13. Next, the hydraulic mechanism 26 turns on the brakes of each hydraulic motor 31R, 31L by controlling the supply of hydraulic oil to the third ports 43R, 43L of each hydraulic motor 31R, 31L. That is, the rotation of the output shafts 33R, 33L of each hydraulic motor 31R, 31L is locked. Next, the hydraulic mechanism 26 stops the hydraulic oil supply to the first ports 41R, 41L and the second ports 42R, 42L of each hydraulic motor 31R, 31L. In this way, in the lock mode, the hydraulic mechanism 26 locks the two drive gears 32R, 32L after making the rotational directions of the driven gear 29 driven by the two drive gears 32R, 32L opposite to each other.

[0052] The operation of the hydraulic mechanism 26 in each of the above four modes is set, for example, by an operator operating an operation panel (not shown). Note that since various configurations can be applied from known configurations for the specific configuration of the hydraulic mechanism 26, a more detailed description than the above-described configuration is omitted.

[0053] Referring to FIGS. 2, 4, 6, and 7, the first hose 27 is a flexible member. The first hose 27 is provided for power supply to electric devices such as a conveyor motor 14c installed on the boom 13 and a winch motor 66 (to be described later), and is also provided for supply and discharge of hydraulic oil (lubricating oil) to and from an oil supply pipe or the like installed on the boom 13. As the first hose 27, for example, hydraulic hoses 271 and 272 that form part of the hydraulic oil passage, and a wire hose 273 including a wire and a coating covering the wire are provided. When these hoses 271, 272, and 273 are collectively referred to, they are simply called the first hose 27. In this embodiment, three first hoses 27 are shown as an example. However, the number of the first hoses 27 may be two or less or four or more. One end of each first hose 27 is connected to a connector or joint (not shown) installed on the pedestal 5. The other end of each first hose 27 is connected to a connector or joint (not shown) installed on the slewing platform 21.

[0054] Since the first hose 27 is held by a swivel-movable cable bear (registered trademark) 28, the first hose 27 can move along the circumferential direction C around the swivel axis S as the slewing platform 21 slews.

[0055] The cable carrier (registered trademark) 28 is provided to guide the movement of the longitudinal middle part and the turntable 21 side part of the first hose 27 as the turntable 21 rotates. The cable carrier (registered trademark) 28 of the present embodiment is of a swivel type and can move along the circumferential direction C as the turntable 21 rotates. The cable carrier (registered trademark) 28 includes a link unit configured such that adjacent link plates 51 are relatively rotatable about the pin using the pin, and a plurality of link plates 51 are arranged side by side, and has a configuration in which a pair of link units 50A and 50B are provided at a distance in the radial direction of the axis of rotation S. Further, a block-shaped supporter 52 that can be divided vertically is attached to the pair of link units 50A and 50B. A plurality of supporters 52 are provided at intervals along the longitudinal direction of the cable carrier (registered trademark) 28. A plurality of through holes through which the first hose 27 passes are formed in the supporter 52, and the corresponding first hose 27 is passed through any of these through holes.

[0056] The cable carrier (registered trademark) 28 is disposed below the turntable 21, and the space below the turntable 21 is effectively utilized. The cable carrier (registered trademark) 28 extends along the circumferential direction C, and the longitudinal middle part of the cable carrier (registered trademark) 28 is folded back. The cable carrier (registered trademark) 28 is arranged in an arc shape in plan view.

[0057] The cable carrier (registered trademark) 28 includes an upper region 53 disposed around the axis of rotation S, a lower region 54 disposed below the upper region 53, and an intermediate region 55 disposed between the upper region 53 and the lower region 54, and the position of the intermediate region 55 around the axis of rotation S moves according to the position of the boom 13 around the axis of rotation S.

[0058] The lower region 54 is supported by a lower pedestal 61 fixed to the pedestal 5. The upper surface of the lower pedestal 61 is arranged to receive the lower surface of the lower region 54. The upper surface of the lower pedestal 61 is inclined so as to descend as it proceeds radially outward of the turning axis S. One end of each link unit 50A, 50B of the cable bear (registered trademark) 28, that is, the end of the lower region 54, is fixed to the lower pedestal 61 or the like by a fixed terminal fitting (not shown).

[0059] One end of each link unit 50A, 50B of the cable bear (registered trademark) 28, that is, the end of the upper region 53, is fixed to a bracket 62 extending downward from the swivel base 21 by a fixed terminal fitting (not shown). Thereby, the other end of the cable bear (registered trademark) 28 moves integrally around the swivel base 2 and the turning axis S. Further, when the length of the upper region 53 increases as the swivel base 21 turns, a part of the upper region 53 is supported by an upper pedestal 63 attached to the pedestal 5. The upper pedestal 63 has rollers 64 and supports the upper region 53 while rotating as the upper region 53 moves along the circumferential direction C. In the present embodiment, two rollers 64 are arranged along the radial direction of the turning axis S and receive the lower surface of the upper region 53. The rollers 64 of the upper pedestal 63 are inclined so as to ascend as they proceed radially outward of the turning axis S.

[0060] With the above configuration, the upper region 53 and the lower region 54 are arranged such that the distance between them increases as they proceed radially outward of the turning axis S. Further, in the present embodiment, the upper region 53 and the lower region 54 are arranged symmetrically (vertically symmetric) with respect to the turning axis direction.

[0061] Each first hose 27 is connected to a second hose 30 via a connector or joint (not shown) on the slewing platform 21 side. The second hose 30 is a flexible member. The number of second hoses 30 is the same as the number of first hoses 27 (in this embodiment, three). In the drawing, one second hose 30 is shown, and a plurality of second hoses 30 are arranged in a direction perpendicular to the plane of the paper. One end of each second hose 30 is connected to the corresponding hoses 271, 272, 273. Note that each second hose 30 may be connected to the first hose 27 via a metal pipe provided on the slewing platform 21. The other end of each second hose 30 is connected to the corresponding electrical equipment and oil supply pipe on the boom 13. Among the second hoses 30, the portion on the slewing platform 21 side is received by a guide 23 fixed to the slewing platform 21. Also, among the second hoses 30, the portion on the boom 13 side is received by a guide 24 fixed to the boom 13. Each of the guides 23, 24 has, for example, an arcuate hose receiving surface in side view. The middle portion of each second hose 30 is suspended between the guide slewing platform 21 and the boom 13 (between the guides 23, 24). With this configuration, the second hose 30 can follow the pitching motion of the boom 13 around the pitching pivot 12. That is, as the boom 13 pitches, the portion of the second hose 30 between the boom 13 and the slewing platform 21 flexes and deforms, and the second hose 30 can follow the pitching motion of the boom 13.

[0062] Next, the configuration of the pitching mechanism 16 will be described.

[0063] Referring to FIG. 2, the pitching mechanism 16 includes a wire 65, a winch motor 66 to which the wire 65 is attached, a fixed pulley 67 installed on the upper chute 22 of the hull 2 around which the wire 65 is wound, and a movable pulley 68 installed on the boom 13 around which the wire 65 is wound.

[0064] The winch motor 66 is supplied with power from the electric wire hose 273. When the winch motor 66 rotates and the wire 65 is wound around the winch motor 66, the boom 13 is lifted by the wire 65 at the position of the movable pulley 68, and the tip 13d of the boom 13 moves upward. On the other hand, when the winch motor 66 rotates and the wire 65 is unwound from the winch motor 66, the length of the wire 65 being unwound from the winch motor 66 increases. As a result, the tip 13d of the boom 13 moves downward.

[0065] As described above, according to the present embodiment, each of the drive gears 32R and 32L of the slewing mechanism 15 is a rotating gear attached to the hull 2 and arranged in the circumferential direction C of the driven gear 29. According to this configuration, the drive gears 32R and 32L are compactly arranged around the driven gear 29. For example, if the drive gear is a rack gear (linear gear), the long rack teeth will protrude significantly around the slewing platform 21, increasing the space substantially occupied by the drive gear. On the other hand, since the drive gears 32R and 32L are rotating gears, they do not protrude significantly from the slewing platform 21, enabling a more compact configuration of the slewing mechanism 15 for slewing the boom 13. Furthermore, the hydraulic mechanism 26 can execute the drive slewing mode described above in (1.) and the lock mode described above in (4.). With this configuration, the hydraulic mechanism 26 can perform the slewing operation of the boom 13 during the landing of the bulk cargo 200 and the fixing of the boom 13 during the navigation of the ship 1.

[0066] Also, according to the present embodiment, in the free slewing mode described above in (2.), the free rotation of each of the drive gears 32R and 32L is permitted. Also, in the slow brake mode described above in (3.), a predetermined rotational resistance is applied to the rotation of at least one of the drive gears 32R and 32L. According to this configuration, during the landing of the bulk cargo 200, for example, the free slewing mode can be selected when the waves are small, and the slow brake mode can be selected when the waves are large. Therefore, even when the waves are large, the landing of the bulk cargo 200 can be performed with the posture of the boom 13 being stable.

[0067] Further, according to the present embodiment, by making the cable bear (registered trademark) 28 a swivel type (rotary traveling type) arranged around the swivel axis S, the cable bear (registered trademark) 28 and the plurality of first hoses 27 can be compactly arranged around the swivel base 21, achieving a significant space saving. Further, the upper region 53 and the lower region 54 of the cable bear (registered trademark) 28 are arranged such that the distance between them increases as they proceed radially outward from the swivel axis S. According to this configuration, when the swivel base 21 and the boom 13 swivel, the cable bear (registered trademark) 28 follows the movement of the swivel base 21 while changing the positions of the upper region 53 and the intermediate region 55 in the circumferential direction C. At this time, the movement distance of the radially outer link unit 50B among the pair of link units 50A, 50B is larger than the movement distance of the radially inner link unit 50A. Therefore, by making the distance between the upper region 53 and the lower region 54 of the cable bear (registered trademark) 28 increase as they proceed radially outward from the swivel axis S, the movement amount of the radially outer link unit 50 can be increased. Thereby, smooth deformation movement of the cable bear (registered trademark) 28 accompanying the swivel of the boom 13 can be realized. That is, the cable bear (registered trademark) 28 and the first hose 27 held by the cable bear (registered trademark) 28 can be moved smoothly. In this way, a compact layout can be realized for the cable bear (registered trademark) 28 and the first hose 27, and they can smoothly follow the swivel operation of the swivel base 21.

[0068] Further, according to the present embodiment, the upper region 53 and the lower region 54 of the cable bear (registered trademark) 28 are arranged symmetrically with respect to the swivel axis direction (vertically symmetric arrangement). According to this configuration, smooth relative rotation between adjacent link plates 51, 51 can be realized in each of the radially outer link unit 50 and the radially inner link unit 50. Therefore, the cable bear (registered trademark) 28 can be moved more smoothly along with the swivel operation of the swivel base 21.

[0069] The embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments. The present invention can be variously modified as long as it is within the scope described in the claims.

[0070] In the above-described embodiment, the form in which two drive gears 32R and 32L are used has been described as an example. However, it does not have to be like this. The driven gear 29 may be rotationally driven by three or more drive gears.

[0071] Also, in the above-described embodiment, the form in which the hydraulic mechanism 26 is used as a drive source has been described as an example. However, it does not have to be like this. The drive gears 32R and 32L may be driven using electric motors instead of the hydraulic motors 31R and 31L. In this case, the electric motor and the control unit that controls the drive of this electric motor serve as the drive source.

Industrial Applicability

[0072] The present invention can be widely applied as a ship unloader.

Explanation of Reference Numerals

[0073] 2 Hull 10 Ship unloader 13 Boom 14a Conveyor belt 15 Swivel mechanism 26 Hydraulic mechanism (drive source) 27 First hose (hose) 28 Cable Bear (registered trademark) 29 Driven gear 32R, 32L Drive gears 51 Link plate 53 Upper region 54 Intermediate region 55 Lower region 200 Bulk goods (objects to be conveyed) S Swivel axis

Claims

1. A conveyor belt for conveying an object to be conveyed from the hull to the outside of the hull, a boom for supporting the conveyor belt, a turning mechanism for turning the boom around a turning axis that is an axis extending vertically on the hull with respect to the hull, comprising: The turning mechanism includes a drive source, at least two drive gears powered by the drive source, and a driven gear driven by each drive gear. The driven gear is a rotating gear connected to the boom so as to be capable of interlocking rotation around the turning axis, and each drive gear is a rotating gear attached to the hull and arranged in the circumferential direction of the driven gear. The drive source is configured to be capable of executing a drive turning mode in which the boom is turned with the rotation directions of the driven gears being the same due to the driving of each drive gear, and a lock mode in which the two drive gears are locked after the rotation directions of the two drive gears are made opposite. a hose extending from the hull side to the boom side, a CableBear (registered trademark) having a plurality of link plates and holding the hose, further comprising: The CableBear (registered trademark) includes an upper region arranged around the turning axis, a lower region arranged below the upper region, and an intermediate region arranged between the upper region and the lower region, and the position of the intermediate region around the turning axis is configured to move according to the position of the boom around the turning axis. The upper region and the lower region are arranged such that the distance between them increases as they proceed radially outward from the turning axis. A ship unloader.

2. The turning mechanism is configured to be capable of executing a rotation allowance mode that allows the boom to rotate freely around the turning axis with respect to the hull. In the rotation allowance mode, free rotation of each drive gear is allowed, or a predetermined rotational resistance is applied to the rotation of at least one drive gear. The ship unloader according to Claim 1.

3. The upper region and the lower region are arranged symmetrically with respect to the turning axis direction. The ship unloader according to Claim 1 or Claim 2.

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