KR20160123063A - hydraulic winch driving device - Google Patents

hydraulic winch driving device Download PDF

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Publication number
KR20160123063A
KR20160123063A KR1020150053110A KR20150053110A KR20160123063A KR 20160123063 A KR20160123063 A KR 20160123063A KR 1020150053110 A KR1020150053110 A KR 1020150053110A KR 20150053110 A KR20150053110 A KR 20150053110A KR 20160123063 A KR20160123063 A KR 20160123063A
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KR
South Korea
Prior art keywords
hydraulic
pressure fluid
flow path
supplied
passage
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KR1020150053110A
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Korean (ko)
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KR101721645B1 (en
Inventor
노기태
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훌루테크 주식회사
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Priority to KR1020150053110A priority Critical patent/KR101721645B1/en
Publication of KR20160123063A publication Critical patent/KR20160123063A/en
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Publication of KR101721645B1 publication Critical patent/KR101721645B1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B21/00—Tying-up; Shifting, towing, or pushing equipment; Anchoring
    • B63B21/16—Tying-up; Shifting, towing, or pushing equipment; Anchoring using winches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • B63B2708/02—

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The present invention relates to a hydraulic winch driving device for a ship, enabling to manually control an eccentric of the hydraulic motor in accordance with a loading condition to reduce a deflection even in a neutral state of a control valve, and to maintain a low lifting speed of an anchor. The hydraulic winch driving device comprises: a supply flow path to guide inflow of a hydraulic fluid and a discharge flow path to guide outflow of the hydraulic fluid; a hydraulic motor driven by the hydraulic fluid received from the supply flow path to drive a winch, and operated in a small eccentric or a large eccentric state in accordance with a motion of the hydraulic operation unit; a control valve to control supplying of the hydraulic fluid introduced from the supply flow path to the hydraulic motor; a regulator to change a supplying direction of the hydraulic fluid received in the hydraulic operation unit of the hydraulic motor; a detour flow path to guide a portion of the hydraulic fluid supplied from the supply flow path directly to the hydraulic operation unit through the regulator without passing the control valve, and to the portion to operate the regulator; and an opening and closing lever installed on the detour flowing path to open and close the detour flow path by a manual control.

Description

[0001] The present invention relates to a hydraulic winch driving device for a ship,

[0001] The present invention relates to an apparatus for driving a hydraulic winch used in a ship, and more particularly, to an eccentric adjustment of a hydraulic motor manually according to a load condition, thereby reducing an amount of deflection of an anchor And an elevating speed of the anchor can be maintained at a low speed.

In general, the ship is provided with an anchor for mooring at a specific point in the sea, and the anchor is lifted or pulled down by the operation of the winch with its anchor chain lifted.

A hydraulic motor 10 is provided in the driving device for driving the winch. The hydraulic motor 10 is operated in the large eccentric state or in the large eccentric state by the operation of the marine regulator 30 by controlling the operation of the control valve 20, The eccentricity is controlled such that the eccentric state of the small eccentric state is maintained and the speed of lifting the anchor (not shown) is kept slow or maintained fast.

1 schematically shows a hydraulic circuit for a conventional hydraulic winch.

As shown in the figure, in the conventional hydraulic type winch, the eccentricity of the hydraulic motor 10 is adjusted while the regulator 30 is operated by the pressure fluid that has passed through the shuttle valve 71, and the anchor is lifted The speed is adjusted to be fast or slow.

However, in the hydraulic winch drive apparatus according to the related art, when the winch is used, the load caused by the anchor chain is reduced and the speed at which the anchor is lifted increases as the anchor is used. Thus, the anchor is moved to the ball mouse There is a problem that shock noise is generated and the damage is caused due to an increase in impact impact.

That is, when considering the load at the time of the first rise of the anchor, the hydraulic motor 10 is kept in the eccentric state at the time of the first rise of the anchor. However, when the rise of the anchor is made more than a certain level and qnk is reduced, The rising speed of the anchor is excessively increased with time due to the small eccentric state of the hydraulic motor 10, although the diameter of the winding portion due to the winding of the anchor chain is increased.

Further, when the control valve 20 is placed in the neutral state, the supply of the pressure fluid to the hydraulic motor 10 is interrupted, so that sagging due to the weight of the anchor is generated. Particularly, So that the amount of deflection due to the weight of the anchor is further increased and the reliability of the product is inevitably lowered.

SUMMARY OF THE INVENTION It is an object of the present invention to reduce the amount of deflection even when the control valve is in the neutral state by enabling the eccentric adjustment of the hydraulic motor manually according to the load condition. And to provide a hydraulic type winch drive apparatus for a ship according to a new form in which an elevator speed of an anchor can be maintained at a low speed.

According to an aspect of the present invention, there is provided an apparatus for driving a hydraulic winch according to the present invention, comprising: a feed channel for guiding an inflow flow of a pressurized fluid and an outflow channel for guiding an outflow flow of the pressurized fluid; A hydraulic motor that operates the winch while being driven by the pressure fluid supplied through the supply passage and operates in a small eccentric or eccentric state by the operation of the hydraulic operation portion; A control valve for controlling that the pressure fluid flowing through the supply passage is supplied to the hydraulic motor; A regulator for changing a providing direction of the pressure fluid provided to the hydraulic operation portion of the hydraulic motor; A bypass channel for guiding a portion of the pressure fluid supplied through the supply channel to be supplied to the hydraulic operation unit through the regulator directly without passing through the control valve and guiding the portion to be supplied to a portion for operation of the regulator; And an opening / closing lever that is installed on the bypass flow path and opens / closes the bypass flow path by manual operation.

Here, the supply passage further includes a pressure compensator, and the bypass passage is connected to receive the pressure fluid from the hydraulic inlet side of the pressure compensator in the supply passage.

The hydraulic motor is configured to receive the pressure fluid from the supply passage through two flow paths through which the pressure fluid is supplied or recovered. In the two flow paths connected to the hydraulic motor, the first branch flow passage and the second branch flow passage are connected A portion of the pressure fluid is supplied to the regulator through the branched flow paths and the direction of the pressure fluid supplied to the hydraulic operation portion is changed according to a load of the pressure fluid supplied through the branch flow paths. .

The first branch passage and the second branch passage are connected to each other by a first coupling passage, and a second coupling passage communicating with the bypass passage is connected to the first coupling passage, To the regulator.

In addition, a first shuttle valve for controlling the flow direction of the pressure fluid is further provided at a connection portion between the first connection passage and each branch passage, and a flow of the pressure fluid is provided at a connection portion between the second connection passage and the bypass passage. And a second shuttle valve for controlling the direction of the second shuttle valve.

The hydraulic hydraulic winch drive apparatus of the present invention as described above has the following features: (1) an open / close lever for manual operation; (2) a bypass flow path for supplying pressure fluid to the regulator by the operation of the open / close lever; So that it is possible to prevent the impact of the ball mouse due to an increase in the excessive lifting speed during lifting of the anchor.

Furthermore, even when the control valve is positioned in the neutral state, the hydraulic motor can maintain the large eccentric state, thereby preventing the occurrence of deflection due to the weight of the anchor.

FIG. 1 is a schematic view of a conventional hydraulic hydraulic winch driving apparatus,
FIG. 2 is a schematic view of a hydraulic circuit diagram schematically shown for explaining a hydraulic power winch drive system for a ship according to an embodiment of the present invention.
3 to 8 are views showing a hydraulic circuit diagram for explaining an operation state of a hydraulic winch drive apparatus for a ship according to an embodiment of the present invention.

Hereinafter, a preferred embodiment of a hydraulic winch drive apparatus for a ship according to the present invention will be described with reference to FIGS. 2 to 8. FIG.

Prior to the description, in the hydraulic circuit diagram shown in each drawing, the flow due to the supply flow of the pressure fluid is expressed by a thick line, and in the case of the relatively thin line, the flow due to the recovery flow of the pressure fluid or the flow It represents the part.

FIG. 2 is a hydraulic circuit diagram illustrating a hydraulic power winch drive apparatus for a ship according to an embodiment of the present invention. Referring to FIG.

The hydraulic winch drive apparatus for a ship according to an embodiment of the present invention includes a supply passage 910 and an outflow passage 920, a hydraulic motor 100, a control valve 200, a regulator 300, The control valve 200 is provided with the bypass passage 400 and the opening and closing lever 500. In particular, even if the control valve 200 is in the neutral state by the provision of the bypass passage 400 and the opening / closing lever 500, Pressure hydraulic fluid is supplied to the hydraulic motor 100 so that the hydraulic motor 100 can be maintained in a large eccentric state.

This will be described in more detail below for each configuration.

First, the supply flow path 910 is a flow path for supplying a pressure fluid to a ship's hydraulic type winch drive apparatus (hereinafter referred to as " winch drive apparatus "), Respectively.

At this time, the supply passage 910 is connected to receive a pressure fluid stored in a hydraulic tank (not shown) by driving a hydraulic pump (not shown), and the outflow passage 920 is connected to a pressure fluid Is returned to the hydraulic tank.

Next, the hydraulic motor 100 is a device that operates a winch (not shown) while being driven by a pressure fluid supplied through the supply passage 910.

The hydraulic motor 100 is operated in a small eccentric or eccentric state by the operation of the hydraulic actuator 110, thereby elevating and lowering the anchor connected to the winch.

The hydraulic actuating unit 110 has a cylinder structure that adjusts the amount of eccentricity of the hydraulic motor 100 while receiving or discharging pressure fluid through the first hydraulic line 610 and the second hydraulic line 620, The first hydraulic line 610 is connected to a first space 111 for switching the hydraulic motor 100 of the hydraulic operation unit 110 to a large eccentric state, And is connected to a second space 112 for switching the hydraulic motor 100 to a small eccentric state. Here, the large eccentric state means a state in which the winch operated by the hydraulic motor 100 is operated with a large turning radius, and the small eccentric state means that the winch operated by the hydraulic motor 100 is small Quot; means a state in which it is operated while having a turning radius.

The hydraulic motor 100 receives the pressure fluid from the supply passage 910 through the third hydraulic line 630 and the fourth hydraulic line 640 or receives the pressure fluid from the supply passage 910 Out.

Next, the control valve 200 is a valve that controls the supply of pressure fluid to the hydraulic motor 100.

The control valve 200 is located at a portion where the supply passage 910 and the outflow passage 920 are connected to the third hydraulic line 630 and the fourth hydraulic line 640, The pressure fluid flowing through the supply passage 910 is selected as a hydraulic line among the third hydraulic line 630 and the fourth hydraulic line 640 connected to the hydraulic motor 100 according to the descending operation of the anchor And a direction switching valve that is operated to supply the gas.

Particularly, the control valve 200 is supplied to the third hydraulic line 630 or the fourth hydraulic line 640 even when the pressure fluid is supplied from the supply passage 910 at a neutral position thereof .

Next, the regulator 300 is a valve for changing the direction of providing the pressure fluid provided to the hydraulic actuating portion 110 of the hydraulic motor 100.

The regulator 300 supplies a part of the pressure fluid flowing along the third hydraulic line 630 and the fourth hydraulic line 640 through the first branch passage 650 and the second branch passage 660 And is selected and provided to each of the spaces 111 and 112 of the hydraulic operation unit 110 constituting the hydraulic motor 100.

The first branch passage 650 and the second branch passage 660 are connected to each other by a first connection passage 670 and the first connection passage 670 is connected to the bypass passage 400, And a second connection passage 680 communicating with the second connection passage 680 is connected to supply the pressure fluid to the regulator 300 through the second connection passage 680.

A first shuttle valve 710 for controlling the flow direction of the pressure fluid is further provided at a connection portion between the first connection passage 670 and the branch passages 650 and 660, And a second shuttle valve 720 for controlling the flow direction of the pressure fluid is further provided at a communicating portion between the bypass passage 400 and the bypass passage 400.

Particularly, the regulator 300 is configured to change the direction of the pressure fluid supplied to the hydraulic operation portion 110 of the hydraulic motor 100 according to the load of the pressure fluid supplied through the branched flow paths 650 and 660 . That is, when the load acting on the hydraulic motor 100 is large as in the initial driving, the pressure fluid is operated to be supplied to the first hydraulic line 610 so that the hydraulic motor 100 can be in a large eccentric state, When the load applied to the motor 100 is small, the hydraulic fluid is supplied to the second hydraulic line 620 so that the hydraulic motor 100 can be in a small eccentric state.

The bypass flow path 400 is a path for guiding the pressure fluid supplied to the supply flow path 910 directly to the regulator 300 separately from the third hydraulic line 630 and the fourth hydraulic line 640, to be. That is, some of the pressure fluid supplied through the supply passage 910 by the bypass passage 400 is directly supplied to the hydraulic actuator 110 through the regulator 300 without passing through the control valve 200 .

In particular, in the embodiment of the present invention, the supply passage 910 is further provided with a pressure compensator 11, and one end of the bypass passage 400 is connected to the pressure compensator 11 To receive the pressurized fluid from the hydraulic inlet side thereof.

That is, since the hydraulic pressure inflow side of the pressure compensator 11 maintains a higher pressure state than the hydraulic pressure outflow side (the hydraulic pressure inflow side of the control valve) of the hydraulic pressure operating unit 110, So that the operation of the hydraulic operation unit 110 can be smoothly performed.

Next, the opening / closing lever 500 is a portion which is installed on the bypass passage 400 and opens / closes the bypass passage by manual operation.

That is, in the embodiment of the present invention, the hydraulic motor 100 can be maintained in the large eccentric state regardless of the load during the lifting of the anchor due to the operation of the winch, so that the speed at which the anchor is lifted is increased So that the problem that the anchor hits the ball mouse (the anchor entrance side) of the ship can be prevented, and the control valve 200 is maintained in the neutral state, so that the pressure fluid is supplied to the hydraulic motor 100 The hydraulic motor 100 can be maintained in the large eccentric state through the pressure fluid supply to the bypass passage 400 by the operation of the opening / closing lever 500 so that the sag due to the weight of the anchor can be minimized It is.

Hereinafter, the operation of the winch drive apparatus according to the embodiment of the present invention described above will be described in more detail.

2 shows a state in which the control valve 200 is in a neutral state and the opening and closing lever 500 is also in a neutral state.

In this state, since the pressure fluid is not supplied to the hydraulic motor 100, the regulator 300 is also in a neutral state, and the pressure fluid is not supplied to the hydraulic actuator 110, Eccentric state.

In such a small eccentric state of the hydraulic motor 100, the amount of deflection due to the weight of the anchor becomes larger than that in the large eccentric state.

Accordingly, in the neutral state of the control valve 200, the opening / closing lever 500 is operated as shown in FIG. 3 so that the pressure fluid can be supplied to the regulator 300.

When the operation of the on-off valve 500 is performed, the high-pressure fluid existing on the hydraulic inlet side of the pressure compensator 11 in the supply passage 910 passes through the opening / closing lever 500, 680 to the regulator 300 where some of the high pressure fluid is provided to switch the regulator 300 to a high load condition so that the pressure fluid that has passed through the regulator 300 is supplied to the first hydraulic line Is provided to the first space (111) for switching the hydraulic motor (100) out of the hydraulic actuating part (110) to the large eccentric state via the first clutch (610).

As a result, the hydraulic motor 100 is switched to the large eccentric state, thereby minimizing deflection due to the weight of the anchor.

4 shows a state in which a pressure fluid is supplied to the hydraulic motor 100 by power supply to the control valve 200. [

In this case, the pressure fluid that has passed through the pressure compensator 11 through the supply passage 910 flows to the third hydraulic line 630 by the guidance of the control valve 200 and is then supplied to the hydraulic motor 100 The hydraulic motor 100 is driven.

In addition, some of the pressure fluid flowing along the third hydraulic line 630 passes through the first branch passage 650, the first connection passage 670 and the second connection passage 680 in order The regulator 300 is provided with the influence of such a high load so that the pressure fluid is supplied to the first hydraulic line 610 because the load is sufficient at the beginning of the operation of the hydraulic motor 100. [ . As a result, the hydraulic motor 100 is in a large eccentric state and the anchor is smoothly lifted.

When the lifting operation of the anchor is proceeded, the chain of the anchor is gradually wound on the winch, thereby reducing the load for lifting the anchor.

When the load is reduced, the regulator 300 is restored by reducing the load supplied to the regulator 300, and the first branch flow channel 650 and the first connection flow channel 670, The pressure fluid, which is sequentially passed through the second connection passage 680 and provided to the regulator 300, is supplied to the second hydraulic line 620. As a result, the hydraulic motor 100 forms a small eccentric state, as shown in FIG. 5 attached hereto.

However, when the hydraulic motor 100 is continuously operated in the small eccentric state due to such a decrease in load, the speed of raising the anchor gradually increases, and there is a problem that the corresponding anchor hits the ball mouse of the ship .

Accordingly, when the load is reduced, the operator can operate the opening / closing lever 500 so that the regulator 300 can continuously maintain the large eccentric state.

6, the high-pressure fluid existing in the hydraulic oil inflow side of the pressure compensator 11 in the supply passage 910 is supplied to the bypass passage 400 via the open / close lever 500, Closing lever 500 through the bypass passage 400 and then supplied to the regulator 300. At this time, compared with the pressure fluid supplied through the second connection passage 680, the opening / closing lever 500 is rotated through the bypass passage 400 The second shuttle valve 720 blocks the flow of the pressure fluid flowing through the second connection passage 680 and the bypass passage 400 is connected to the second connection passage 680 via the bypass passage 400. [ Thereby guiding one pressure fluid to be supplied to the regulator 300.

As a result, the hydraulic hydraulic winch driving apparatus of the present invention includes an open / close lever 500 for manual operation, a bypass channel 400 for supplying pressure fluid to the regulator 300 by the operation of the open / close lever 500, By providing the shuttle valves 710 and 720 additionally, the hydraulic motor 100 can be forcibly brought into the eccentric state, thereby preventing the ball mouse from being hit by an excessive lifting speed during lifting of the anchor, Even when the control valve 200 is positioned in the neutral state, the hydraulic motor 100 can be maintained in the large eccentric state, thereby preventing the occurrence of deflection due to the weight of the anchor.

910. Supply flow 920. Run flow
11. Pressure compensator 100. Hydraulic motor
110. Hydraulic operation part 111. First space
112. Second space 200. Control valve
300. Regulator 400. Bypass Euro
500. Open / close lever 610. First hydraulic line
620. 2nd hydraulic line 630. 3rd hydraulic line
640. Fourth hydraulic line 650. First branch line
660. Second branch Euro 670. First connection channel
680. Second connection channel 710. First shuttle valve
720. Second shuttle valve

Claims (5)

An outflow channel for guiding an outflow flow of the pressurized fluid and a supply flow channel for guiding the inflow flow of the pressurized fluid;
A hydraulic motor that operates the winch while being driven by the pressure fluid supplied through the supply passage and operates in a small eccentric or eccentric state by the operation of the hydraulic operation portion;
A control valve for controlling that the pressure fluid flowing through the supply passage is supplied to the hydraulic motor;
A regulator for changing a providing direction of the pressure fluid provided to the hydraulic operation portion of the hydraulic motor;
A bypass channel for guiding a portion of the pressure fluid supplied through the supply channel to be supplied to the hydraulic operation unit through the regulator directly without passing through the control valve and guiding the portion to be supplied to a portion for operation of the regulator; And,
And an open / close lever provided on the bypass flow path for manually opening and closing the bypass flow path by manual operation. The method according to claim 1,
Wherein the supply passage further comprises a pressure compensator,
Wherein the bypass passage is connected to receive the pressure fluid from the hydraulic inflow side of the pressure compensator in the supply passage. The method according to claim 1,
Wherein the hydraulic motor is configured to receive pressure fluid from the supply passage through two flow paths through which pressure fluid is supplied or recovered,
The first branch flow path and the second branch flow path are connected to the two flow paths connected to the hydraulic motor so that a part of the pressure fluid is supplied to the regulator through the branch flow paths, Wherein the supply direction of the pressure fluid provided to the hydraulic operation unit is changed according to the load of the hydraulic winch. The method of claim 3,
Wherein the first branched flow path and the second branched flow path are configured to be connected to each other by a first connection flow path,
Wherein the first connection channel is connected to a second connection channel communicating with the bypass channel, and the pressure fluid is supplied to the regulator through the second connection channel. 5. The method of claim 4,
And a first shuttle valve for controlling the flow direction of the pressure fluid is further provided at a connection portion between the first connection passage and each branch passage,
And a second shuttle valve for controlling the flow direction of the pressure fluid is further provided at a communicating portion between the second connection passage and the bypass passage.
KR1020150053110A 2015-04-15 2015-04-15 hydraulic winch driving device KR101721645B1 (en)

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KR1020150053110A KR101721645B1 (en) 2015-04-15 2015-04-15 hydraulic winch driving device

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KR1020150053110A KR101721645B1 (en) 2015-04-15 2015-04-15 hydraulic winch driving device

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KR20160123063A true KR20160123063A (en) 2016-10-25
KR101721645B1 KR101721645B1 (en) 2017-04-10

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102377481B1 (en) * 2020-12-03 2022-03-22 훌루테크 주식회사 Hydraulic Winch Driving Device for Ship Use
KR20220132260A (en) * 2021-03-23 2022-09-30 훌루테크 주식회사 A forced low speed type regulator

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3391382B2 (en) * 2000-08-11 2003-03-31 川崎重工業株式会社 Windlass application selector
JP3731775B2 (en) * 1997-04-16 2006-01-05 日立建機株式会社 Winch equipment for work equipment
JP2014069724A (en) * 2012-09-28 2014-04-21 Fukushima Seisakusho:Kk Windlass driving device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3731775B2 (en) * 1997-04-16 2006-01-05 日立建機株式会社 Winch equipment for work equipment
JP3391382B2 (en) * 2000-08-11 2003-03-31 川崎重工業株式会社 Windlass application selector
JP2014069724A (en) * 2012-09-28 2014-04-21 Fukushima Seisakusho:Kk Windlass driving device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102377481B1 (en) * 2020-12-03 2022-03-22 훌루테크 주식회사 Hydraulic Winch Driving Device for Ship Use
KR20220132260A (en) * 2021-03-23 2022-09-30 훌루테크 주식회사 A forced low speed type regulator

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