JPS6356160B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION OBJECTS OF THE INVENTION (INDUSTRIAL APPLICATION) The present invention relates to winches, and more particularly to winches, including a control device, for the purpose of reducing and reducing peak loads that may occur in tension acting outwardly on a hawser. (or) a general vessel designed for mooring, navigation, towing, etc. purposes with a control system to ensure the desired tension of the hawser via the winch drum by adjusting the power of the motors for equalization; related to winches.

(Prior art) In various operations on ships, especially towing operations,
There are many practical problems that need to be solved. Until now, there has been a heavy reliance on hawser lines made from fibers to absorb fluctuations in the loads on the hawser due to waves, wind, currents, etc. For towing operations in increasingly strong waves, wind, and water currents, the length of the towline must be increased. Because of the length of this line and the resulting increased weight of the line in question, the tow line (rope) hangs in a large arc between the towing vessel and the towed vessel, which is actually the case in many waters. The rope will be towed along the seabed. In practice, a long towline is required in order for the vessel to be able to respond individually to the different forces encountered without fatigue of the line.

(Problem to be solved by the invention) Such a long line makes it extremely difficult to control the vessel being towed, and there is a great danger that, for example, it is difficult to visually confirm the whereabouts of the line. There is. Such long lines make mooring difficult during loading and unloading of cargo at boring platforms, loading buoys, etc.

Japanese Patent Publication No. 52-64573 discloses a hydraulic actuation system for a winch,
In this case, effective tension control of the winch line is possible, especially by limiting the controlled pressure.
This limits the effects of sudden tensile loads on the line and limits the effects of impulsive pressure build-ups during the working cycle of the hydraulically actuated system. Generally, this effect is ensured by valving the hydraulically actuated system at a predetermined maximum pressure, and once this maximum pressure is exceeded, the associated winch drum releases the rope. However, as soon as the tension in the line falls below the desired tension, the valve acts to tighten the slack in the line until the predetermined maximum pressure in the hydraulically actuated system is again established.

The aim of the invention is to make it possible to relieve and/or average out the peak loads of tension applied externally to the rope in a fully reliable and effective manner. In particular, always let out the line at the desired length and at the desired tension, but be prepared to hold the line in a condition that has the possibility of suppressing and/or averaging said peak loads on the line. The objective is to achieve combined control of rope tension control and rope payout length control.

[Structure of the invention]

(Means for Solving the Problems) According to the present invention, a winch, particularly a marine winch designed for purposes such as mooring, navigation, towing, etc., is provided with A control system for ensuring the desired tension in the rope via the winch drum by regulating the power, a control member of a control device integrated in said control system and a selection of the winch drum and its drive shaft. an adjustable transmission device disposed between the movable element and controlling the control member with a linearly adjustable operating movement simultaneously with the movement of the movable element; - It can be adjusted to an operating position where the desired tension is generated on the rope that is paid out from the drum,
The increase in the tension of the rope, which causes a corresponding movement of the movable element in the direction corresponding to the direction of the winch sag, gradually increases the power to the drive motor in an adjustable manner to the said transmission device via the control device, A reduction in the tension in the rope, which causes a corresponding movement of the movable element in a direction corresponding to the direction of tension action, causes the transmission device via a control device to gradually reduce the power of the drive motor in an adjustable manner.

In this way, a good controlled relaxation of the line is made possible, and as a result of the generation of an external force that increases the pulling force on the line, the pulling force applied to the winch on the line is reduced as the line relaxes. It will be increased accordingly.
As a result, it is possible to maintain the tension of the rope within controlled tolerance limits without the risk of the rope breaking, and at the same time the relaxation of the rope can be limited in a controlled manner. A subsequent winding of the rope is therefore also possible more quickly and in a better controlled manner. Similarly, to counter undesirable sudden tension in the rope, a reduction in the pulling force allows the rope to be reeled in as a result of the reduction in tension in the rope.

Various transmission devices can be used between the control element of the control valve and the drum of the winch, for example based on tachometers, potentiometers or associated regulating devices, or based on gear transmissions or the like. In all cases, the signal or force issued from the drum of the winch can release a control force that can directly actuate the restriction member of the control valve.

In one preferred embodiment, the transmission device has a cam member which is moved synchronously with the movable member of the winch in a direction transverse to the direction of movement of the control member and cooperates with a cam follower fixed to the control member. work

According to the present invention, it is possible to adjust the cam surface of the cam member to various positions inclined with respect to the direction of movement of the cam member by the adjusting device. In particular, the regulating device can be controlled remotely, for example from the ship's bridge;
This facilitates the adjustment of the tension load on the line according to conditions relating to wave size, wind and current strength, etc., or the action of various cooperating winches, as desired. The use of a remotely controllable adjustment device is desirable to facilitate further adjustment as conditions permit.

By adjusting the inclined position of the cam surface of the cam member by remote control, the degree of action of the control member of the control valve can be changed, for example, at a steeper inclined position of the cam surface.
Even more rapid formation of pressure in the winch motor,
Or it can be adjusted during operation to provide a steeper pressure drop in the winch motor than in a more gently sloped position of the cam surface.

In a preferred configuration, the hydraulically actuated system includes a control valve, known per se, for regulating the winch drive motor to provide a predetermined tension on the line and a winch drive motor. An outlet valve known per se for the supply of relatively large or small amounts of pressure medium from an operating valve external to the motor and, if necessary, a pressure limiting valve known per se for controlling said outlet valve. , said control valve is connected to an outlet valve and/or a pressure limiting valve.

(Operation) Thus, a hydraulic actuation system corresponding to that shown in Japanese Patent Application Publication No. 52-64573 can be used and, in addition to the advantages possessed by the present invention, the particular effects contemplated by the present invention are achieved. can get.

EXAMPLES In order that the invention may be better understood, it will be described below by way of example with reference to the accompanying drawings, in which: FIG.

In the following description, the aforementioned Japanese Unexamined Patent Publication No. 52
An embodiment of the present invention is described for use in the hydraulically actuated system shown in Figures 1-6 of No.-64573.

In the known systems referred to later in the following description, the components thereof are used as separate devices for use according to the invention. It is emphasized that this separate device can also be used in other hydraulically actuated systems where effective tension control on the rope can be ensured.

In the accompanying drawings, a limited capacity hydraulically actuated system is shown. A main supply pipe 1 extends from the irreversible pump 10 to the inlet port 12 of the operating valve 13.
1 is extending. A main return pipe 15 extends from the outlet 14 of the operating valve 13 and returns to the suction side of the pump 10. A circulation pipe 16 runs between the supply pipe 11 and the return pipe 15 and is closed by a safety valve 17 . 17a indicates a back pressure valve.

The three-way motor 18 has three paths forming a supply path for the motor when operating the motor in the hoisting direction.
It has three openings 19, 20, 21 (first passage) and one opening 22 (second passage) forming a discharge passage from the motor when operating in the hoisting direction. During operation in the relaxation direction, opening 22 forms a supply path for the motor and openings 19, 20,
21 forms a discharge passage from the motor. The operation of the motor in one or the other direction as well as the adjustment of the drive speed, the adjustment of the motor in the stop position, etc. are controlled by the slider 23 of the operating valve 13, which is known per se. This operating valve 13 is described in US Pat.
It almost corresponds to the configuration shown in No. 2736170.

In the accompanying drawings, an intermediate valve 24 is inserted between the operating valve 13 and the motor 18, and the intermediate valve 24 is configured with an opening communication portion 24a between the openings 19 and 20. 25 indicates a short circuit between openings 20 and 21.

A direct pressure medium passage is therefore formed between the openings 19, 20, 21. It is clear that this represents one preferred structure and is not a necessary means for the system according to the invention to function. Operation valve 1
Discharge ducts 26 , 27 are connected between the opening 19 of No. 3 and the discharge section 29 via the associated discharge valve 28 . One end of the duct 26 is connected to the opening 19 via the intermediate piece 24, and one end of the duct 27 is connected to the return side of the system. duct 26,
The other ends of 27 are connected to respective ports 30 and 31 of valve 28, respectively. In the position shown in FIG. 1, ports 30, 31 are separated from each other by flange 32 of slider 33. One end of the slider with a corresponding flange 34 is received in a control pressure chamber 35 and the opposite end of the slider with a corresponding flange 36 is received in an opposing chamber 37. The control pressure chamber 3 is controlled by the control line 38.
5 is connected to the opening 22, and the opposite chamber 37 is connected to the discharge duct 27 via a branch. A compression spring 40 is inserted between the slider 33 and the bottom of the chamber 37 at an opposing position.

Control line 38 extends directly via control valve 41 . The control valve 41 has a pressure control chamber 43 at one end of a control slider 42 and a corresponding flange 44.
An "opposite chamber" 45 is provided at the opposite end of the control slider. The pressure control chamber 43 communicates with the supply channel 26 of the discharge duct via a branch 46 and has the same pressure conditions as the openings 19-21 of the motor. In the opposing chamber 45, the flange 4
4 and the adjustment screw 48 at the bottom of the chamber is a compression screw 49.
is located. The force acting on the slider 42 in the opposing chamber is the force from the spring 49. The force from spring 49 can be adjusted by adjusting screw 48.

The opposing chamber 45 has a working pipe line 50 from the pressure reducing valve 51.
It is connected to the. Valve 51 receives its oil supply pressure from branch line 46 of control valve 41 via supply pressure line 52 . That is, a pressure corresponding to the pressure at the openings 19-21 is obtained. The valve 51 is connected to the discharge duct 27
It has a discharge conduit 53 associated with the discharge port 29 via. A slider 54 is shown with three flanges 55, 56, 57 forming intermediate chambers 58, 59. In the position shown, the flange 56 covers the port opening to the working line 50, while the associated chambers 58, 59 communicate with the supply pressure line 52 and discharge line 53, respectively, and the slider 54. This position corresponds to the two opposite compression springs 60,6
1 and related chambers 62, 63. One compression spring 60 is housed in a chamber 62 connected to the working line 50 via a branch line 64, and the other compression spring 61 is housed in a chamber 63 connected to the discharge line 53 via a branch line 65. be done. Compression spring 60 has a constant working pressure, while compression spring 61 has a constant working pressure.
It can be adjusted by If the force applied to the spring 61 is increased, the slider 54 can be moved downward in the figure.
The pressure in the working line 50 is increased until the pressure in the chamber 62 and the force from the spring 61 balances the force on the spring 61. By correspondingly reducing the force from spring 61, slider 54 is moved upwardly, thereby reducing the pressure in working conduit 50 to the same extent and balancing the forces on both ends of the slider. It is discharged from the working conduit 50 through the chamber 59 to the discharge conduit 53 until it is released.

In the position shown in FIG. 1, the operating valve 13 remains in the rest position and its slider 23 is set such that the input port 12 from the main supply line 11 communicates with the outlet 14 of the operating valve, and the opening 19 ~21 are flanges 23a, 23b or 23c, 23, respectively.
d and 23e from said outlet 14, thereby securing the position of the motor 18 in said stop position. At this time, oil is circulated from the pump 10 into a passage through the operating valve 13 external to the motor 18. Further, the openings 19 to 21 always form a higher oil pressure than the opening 22.

When the slider is moved toward the relaxed position, oil exits through the release valve 28. Opening 22 is inlet port 1
2, and receives pressure medium from the supply pipe 11 without restriction. This causes the motor 18
is driven by this pressure in the direction of relaxation, ie in the direction of the external force acting on the motor 18 (eg the load on the load winch). During this time, motor 18
is driven as a pump by an external force.

If the external forces are small, the motor 18 is driven by the force generated by the pressure medium in the opening 22 in addition to the external force. In this way, the rate of relaxation can be increased by the action of the pressure medium in the openings 22. When the external force is large, the external force is decisive and the problem is mainly to reduce the rate of relaxation. The rate of relaxation is determined by how much oil is introduced into the openings 22. The pressure in the opening 22 can be adjusted by allowing a pressure medium to pass through the lower flange 23f of the slider 23 to the discharge part 29. The passage passing through the flange 23f is
It can be closed by the flange 23f. In the relaxed position of the slider, this pressure is adjusted to the pressure that drives the motor in the relaxing direction, ie the pressure that opens the discharge valve 28. The pressure can be greatest when there is no load acting on the relaxation motion. The operating valve 13 has to be moved further from the starting position at a high relaxation pressure rather than at a low relaxation pressure in order to throttle the flange 23f.

If a relaxed state must occur, the slider 23
The initial position of is the stop position (Fig. 1). The opening 22 is then not subjected to pressure and the discharge 28 is closed. When the slider 23 is moved slightly upward, the flange 23f of the slider 23 narrows the passage between the opening 22 and the discharge portion 29. In that case, opening 2
2, and the pressure in control line 38 increases at the same time. When the pressure in the control line 38 exceeds the force (spring force) acting on the slider 33 from the opposing chamber 37 (via the spring 40),
The discharge valve 28 is opened and the discharge passage 2 is opened from the opening 19.
6 and 27 to form a discharge passage that reaches the discharge section 29. If an external force (load on the load winch) attempts to pull the motor in the relaxation direction at a faster rate than the presence of oil allows due to the blockage of flange 23f, the pressure in opening 22 will drop. , a corresponding pressure drop also occurs in the control line 38. The exhaust valve 28 is then completely or partially closed until the pressure in the opening 22 builds up again.

A control valve 41 is controlled by a branch 46 emerging from the discharge duct 26 in FIG. 1, so that the control valve 41, together with the discharge valve 28, can be used as a tension-limiting-pressure-limiting structure.

Thus, for example winches (mooring winches, towing winches, trawl winches and similar)
During fluctuations in the tension of the wire or during a sudden transition from the lifting position to the rest position (shipping winches), the pressure in the openings 19 to 21 increases in the opposing chamber 4.
5, the connection between the branch line 46 and the control line 38 via the pressure control chamber 43 is opened, resulting in an increase in the pressure in the control line 38.
The release valve 28 opens and drains excess pressure medium into the supply passage 26.
From there, it is discharged through the discharge valve 28 to the duct 27 and further to the discharge section 29. Therefore, the spring 49
By adjusting the force on the slider 42 via the adjusting screw 48, the pressure in the openings 19-21 can be adjusted to the maximum limit pressure. As soon as this maximum limit pressure is exceeded, the pressure in the openings 19-21 is limited to the desired pressure, i.e. to the force determined by the adjusting screw 48.
Pressure relief takes place via the relief valve 28. In this way, the winch is adjusted to the desired tension limit (tension limit) and also prevents undesirable pressure build-up due to braking, for example during operation in the unwinding direction, as well as undesirable pressure build-up remaining in the openings 19-21. Pressure build-up can be vented.

As a result, for example for mooring winches, trawl winches, tugboat winches or the like,
Depending on whether the external force increases or decreases,
The wire can be paid out or wound up.

In use, as the slider 42 of the control valve 41 moves downwards, an increase in pressure occurs in the line 50, so that the slider 54 of the valve 51 moves upwardly, causing the line 59 to flow through the table 59. A corresponding pressure discharge to 53 occurs.

On the other hand, as soon as the slider 42 is returned upwards, a pressure drop occurs in the conduit 50, so that the valve 5
1 slider 54 is moved downwardly and a corresponding pressure increase is obtained from line 52 through chamber 58 to line 50 until a balance of forces is achieved at both ends of slider 54.

A particular advantage of the remote control system according to the invention is that it is based on pressure transmission in the lines 50, 52, 53 without any pressure medium flow. Therefore, even if relatively viscous pressure oil is used in the hydraulic system and long piping, the piping 5
Precise pressure regulation within 0,52,53 is obtained.

This mode of operation corresponds to that achieved by the method according to Japanese Patent Publication No. 52-64573.

Valve 70, included in additional equipment for known hydraulically actuated systems such as those described above, is connected to branch lines 71,
72, 73 and the conduits 50, 5 via the coupling device.
2,53. This coupling device 74 allows the valve 51 (Japanese Unexamined Patent Publication No.
64573) or valve 70 (so as to obtain the mode of operation contemplated by the present invention).

Valve 70 has a similar construction to valve 51, the only difference being that manual adjustment screw 66 is now a control member 76. The control member 76 is provided with a wheel-shaped cam follower 77 actuated by a cam element 78 which is driven synchronously with the drive shaft 79 of the winch via a transmission device 80 . Further details of the additional equipment are shown in FIGS. 2 and 3.

What is emphasized in the explanation is that the cam follower 77
When actuated by cam element 78 during winch operation, valve 70 automatically acts upon a change in the desired line payout length. This length adjustment action occurs in parallel with the tension adjustment action otherwise provided by the hydraulically actuated system described above.
This action, in the illustrated embodiment, has substantially the same construction and action as compared to the valve 51, with an automatically controlled control member 76 replacing the manually controlled adjustment screw 66 of the valve 51. This is done by a valve 70 that differs only in that it is used.

In Figure 2, the drive shaft of the winch is indicated by the dotted line 7.
9. A first coupling element 82 is fixed to this drive shaft 79 and is rotatably mounted in a housing 84 via a roller bearing 83 . The second coupling element 85 is attached to the outer periphery of a slider portion 86 provided at one end of the spiral guide member 87 so as to be movable toward and away from the coupling element 82 in the axial direction. . The guide member 87 is rotatably mounted at one end within the coupling element 82 and at the other end rotatably mounted on the opposite side of the housing 84 .

The coupling element 85 is rotationally engaged with the guide member 87 and is therefore adapted to perform a co-rotation with the guide member 87 . Further, a holder 88 is rotatably mounted on the coupling element 85 via a ball bearing 89, and a holder 88 is rotatably mounted on the coupling element 85.
5 is movable in the axial direction by its holder 88 along the slider 86 of the guide member 87. A first arm 90 of the holder 88 is actuated by a remotely controlled disconnection mechanism 91 and a diametrically opposite second arm 92 is actuated by an adjustment screw 93.
and is actuated by a compression spring 94 which applies a moment towards the holder 88 around this screw. This moment, in addition to the force from the cutting/closing mechanism 91 , provides abutting action between the coupling elements 82 and 85 , causing the cutting/closing mechanism 91 to abut and support the holder via the arm portion 90 .

The nut 95 engages with the threaded portion 87a of the guide member 87. One end of this nut is connected to a disk 96 having two stoppers 97, 98,
Said stop engages feelers 99, 100 for producing visual and audible warning signals when the nut 95 is displaced to a predetermined warning position on either end of the guide member 87.

Next, the first coupling element 82 and the second coupling element 85
Let us briefly explain the effect of

Normally, an operating switch (not shown) of the cutting mechanism 91 is operated, and the cutting mechanism 91 moves the first arm 90 and the holder 88 to the left in FIG. As a result, the second coupling element 85 also moves to the left, and the first coupling element 82 and the second coupling element 8
5 come into contact and sufficient frictional transmission is achieved. This frictional transmission occurs with sufficient force to actuate valve 70.

Further, for example, when the nut 95 moves to either the left or right end in FIG. As a result, the first arm portion 90 and the holder 88 move to the right in FIG. As a result, the second coupling element 85 also moves to the right, the second coupling element 85 is separated from the first coupling element 82, and friction transmission from the drive shaft 79 to the guide member 87 is stopped.

The nut 95 is the holder 1 for the cam element 78.
01 on the opposite side, and the holder 101
is slidably mounted on the guide 102 of the slider. The holder 101 has two end stops 1.
03, 104 are provided, which stops form support seats for both sides of the housing 84 at the two outer positions of the holder, where the holder is restrained and causes slippage in the connection between the coupling elements 82, 85. Stoppers 103, 104 are adjustable in the holder. The cam element 78 has pivot 1
It is rotatably mounted in the holder around 05 and can be adjusted to various tilted positions with respect to the holder by adjusting screws 106 and 107. Alternatively, the cam element may include a remotely controllable adjustment device (not shown) such as an electric motor, hydraulically actuated cylinder, etc.
Can be connected to the holder via. as needed,
The cam element is pivotally mounted on the first adjustment device and can be connected to the sliding groove of the second adjustment device. As a result, the cam surface of the cam element is arranged in a second position relative to said first adjustment device.
The cam surface of the cam element can be displaced relative to the holder 101 by moving only the adjusting device, and by moving both adjusting devices.

By adjusting the inclination of the cam surface relative to the path of movement of the cam element along the slider guide 102, and by adjusting the distance of the cam surface from the holder 101, the degree of action on the cam follower element can be adjusted as required; As a result, the valve 70 can act on different movements of the winch drum line within precise adjustment intervals.

The mode of operation of valve 70 is as follows. It is now assumed that after the desired length of line has been let out through the winch and relaxed, normal tension control is performed using valve 51. Valve 51 is then shut off and valve 70 is activated in its place. It can be seen that the tension control 41 is set so that the winch does not perform a payout action. This is done to avoid shock to the equipment in the event of power loss, in which case the system reverts to manual control.

The end stops 103, 104 and path controls then adjust the limits as to how much line length variation can be tolerated for the desired payout length. This limit is not exceeded under normal conditions, but is set so that if it is exceeded, an audible and/or optical alarm, for example, is issued to the ship's bridge. In case of an emergency, an emergency release mechanism is actuated directly from the bridge so that the coupling elements for automatic tensioning and length adjustment effects are cut off.

In FIG. 2, valve 70 is shown in the closed position;
The required length of line is paid out and held at the desired tension.

As soon as an increase in the tension in the line occurs beyond the desired tension ensured by the winch's hydraulic actuation system, the tensioning action begins to act and the line is paid out by rotation of the winch drum in one direction. .
This rotation of the winch drum causes the guide member 8
7 displaces the cam element 78 to the right in FIG. 2, which causes the slider 70a of the valve 70 to gradually increase the pulling force on the winch and thus the tension on the line from the winch. Displaced like this. Furthermore, the more the cam element is moved to the right in FIG. 2, the greater the degree of action of the valve 70;
The tension exerted by the winch on the line increases. As a result of the gradual increase in the tension from the winch while the winch gradually releases the line, the increase in line tension is gradually suppressed, and when the increase in tension caused by the external force decreases again, the line tension reaches the desired tension. When the desired payout length is returned and the cam element is in its starting position, the valve 70 returns to its initial position.

If the tensile load or tension of the rope falls below the desired tension, the tension adjustment action is activated again, but in the opposite direction, and the rope is hoisted by the rotating action of the winch drum in the opposite direction. . Therefore, for this purpose, the cam element 78 is moved to the left in FIG. 2, which provides a less and less pulling force at the winch and therefore less and less pulling action from the winch on the line. The slider 70a of the valve 70 is thus displaced. The tensile load applied to the rope from an external source increases as a result, and the rope returns to its initial position at its desired tension and payout length;
Valve 70 is correspondingly returned to the starting position.

In the illustrated embodiment, there are three cooperating valves 28, 41 and 5 for normal tensioning action.
1, and three cooperating valves 28, 41 and 70 for the combined action of tension adjustment and length adjustment. Alternatively, instead of the three valves described above, valve 2 may have the dimensions of a combination of a discharge valve and a control valve.
1 that can be performed by combining the effects of 8 and 70
valves can be used.

In the embodiment, a transmission device between a control member of a valve 70 and a movable part of a winch consisting of a linearly movable cam member used as a cam follower element with respect to the control member of this valve is shown. ing.
However, mechanical, hydraulically actuated or electrical transmission devices,
Alternatively, it is also possible to use other mechanical, hydraulically actuated or electrical components in place of the illustrated example so that a combination of the three is obtained. For example, instead of a mechanical control of the cam member using a guide member with a corresponding nut, a tachometer with a hydraulically actuated or electrical transmission to the cam member can be used, or alternatively a hydraulically actuated control with a corresponding regulating valve. It is also possible to use a pressure-actuated slider or a potentiometer with an intensifier and a regulating valve.

It will be clear that remote control can also be implemented by various mechanical, hydraulically actuated and electrical components as desired.

In the illustrated embodiment, a limited capacity hydraulically actuated system for the pressure medium supplied from one pump is shown. As an alternative to this, two cooperating pumps, one of which can be permanently connected to the hydraulically operated system and the other of which can be normally supplied in circulation and supply pumping medium to the hydraulically operated system as soon as the need arises. can be used. In this way, it is possible to increase or decrease the number of revolutions per minute of the winch on the fly when necessary. Disconnection of the pumping medium from the other pump to the hydraulically actuated system is made possible by control from the control valve 70, which controls the control valve 70 for actual changes as a function of the action of the control valve.
A signal is issued from. For example, excess pumping medium can be supplied to the hydraulic actuation system as soon as a quick hoisting of the line on a winch is required. Therefore, at the same time as the line tension is reduced, the control valve 70
It is possible to quickly increase the hoisting speed, which is controlled in a manner that is regulated by.

Although a preferred embodiment hydraulically operated winch has been described, in place of the illustrated hydraulically operated control valve,
The present invention also encompasses other types of winches, such as steam winches or electric winches, in which separate controls for the associated media-driven or electrical control systems described above are used.

〔Effect of the invention〕

According to the present invention, it is possible to relieve and average the peak load of tension applied to the rope from the outside, and it is possible to pay out the rope to a desired length and with a desired tension.

[Brief explanation of drawings]

FIG. 1 is a partial cross-sectional diagram of a hydraulic actuation system for a winch, FIG. 2 is a partially longitudinal cross-sectional view of a control device for a winch, and FIG. 3 is the same diagram of the control device of FIG. 2. FIG. 10...irreversible pump, 12...inlet port,
13... Operation valve, 14... Outlet, 15... Return pipe, 16... Circulation pipe, 17... Safety valve, 18...
...3-way motor, 19-22...opening, 23...
Slider, 24... Intermediate piece, 25... Short circuit path, 28
...Discharge valve, 29...Discharge part, 30, 31...Port, 32...Flange, 33...Slider, 34
... Flange, 35 ... Control pressure chamber, 36 ... Flange, 37 ... Opposing chamber, 38 ... Control conduit, 3
9... Branch road, 40... Compression spring, 41...
... Control valve, 42 ... Control slider, 43 ... Pressure control chamber, 44 ... Flange, 45 ... Opposing chamber, 46
... Branch furnace, 48 ... Adjustment screw, 49 ... Compression spring, 50 ... Working pipe line, 51 ... Pressure reduction valve, 53 ... Discharge pipe line, 54 ... Slider, 55 -
57...Flange, 58, 59...Intermediate chamber, 6
0, 61... Compression spring, 64, 65... Branch path, 66... Knob, 70... Valve, 71-73
... branching path, 74 ... coupling device, 76 ... control member, 77 ... cam follower element, 78 ... cam element, 79 ... drive shaft, 80 ... transmission device.

Claims (1)

[Scope of Claims] 1. A marine winch designed for mooring, navigation, towing, etc., which has a first passage and a second passage, and the working medium is controlled by an operating valve in the opposite direction or opposite direction to an external force, respectively. a drive motor that drives the drive shaft of the winch drum in the same direction; and a discharge valve connected to a discharge duct, one end of which is connected to the first passage and the other end of which is connected to the discharge side of the operating valve, and internally facing each other. a control valve that controls the opening and closing of the discharge valve and has a slider that forms a chamber and moves toward the opposing chamber by pressure from the first passage; a pressure reducing valve that discharges the pressure in the chamber to the discharge side of the operating valve, a control member that adjusts the discharge pressure from the opposing chamber is reciprocably disposed on the pressure reducing valve, and the control member and the drive shaft. between the movable elements that move according to the rotation of the control member, a cam element that is movable synchronously with the movable element that moves in a direction transverse to the direction of movement of the control member, and a cam that moves linearly with respect to the movement of this cam element. A transmission device consisting of a follower is provided, and when the winch drum rotates in the relaxation direction, the discharge pressure from the opposing chamber is increased to increase the tension of the net, and when the winch drum rotates in the tension direction,
A ship winch configured to reduce the tension of the net by lowering the discharge pressure from the opposing chamber. 2. The winch according to claim 1, wherein the cam element has a cam surface that can be adjusted to various inclination positions with respect to the direction of movement of the cam element by an adjustment device. 3. The winch according to claim 2, wherein the adjustment device is remotely controllable.