CN218708784U

CN218708784U - Double-motor structure wave compensation hydraulic winch control system

Info

Publication number: CN218708784U
Application number: CN202222138159.2U
Authority: CN
Inventors: 钱冬林; 印俊; 魏金辉
Original assignee: Cssc Luzhou Zhenjiang Marine Auxiliary Machinery Co ltd
Current assignee: Cssc Luzhou Zhenjiang Marine Auxiliary Machinery Co ltd
Priority date: 2022-08-15
Filing date: 2022-08-15
Publication date: 2023-03-24
Anticipated expiration: 2032-08-15

Abstract

The utility model discloses a double motor structure wave compensation hydraulic winch control system, including hydraulic winch, main motor and main motor valve unit, vice motor and vice motor valve unit, hydraulic winch include frame, pivot, reel, planetary reducer, hydraulic disc brake, hydraulic disc clutch, encoder. The winding drum is installed on the frame through a rotating shaft, the rotating shaft is connected with an output shaft of the main motor, a planetary reducer is arranged between the rotating shaft and the main motor, the planetary reducer reduces the rotating speed and increases the torque of the output shaft of the main motor, and a hydraulic disc brake is arranged on the output shaft of the main motor; the winding drum is provided with a main gear, two sides of the main gear are respectively provided with a pinion which is meshed with the main gear, one pinion is connected with the encoder, and the other pinion is connected with an output shaft of the slave motor; a hydraulic disc type clutch is arranged in a winding drum of the hydraulic winch.

Description

Double-motor structure wave compensation hydraulic winch control system

Technical Field

The utility model relates to a double motor structure wave compensation hydraulic winch control system.

Background

With the development of global economy, the ocean transportation and the ocean resource development are increasing, and the lifeboat is used as an important escape device in case of danger at sea and is a legal safety device which is necessary for each ship. The lifeboat is complex in folding and unfolding sea conditions, the influence of waves on the folding and unfolding of the lifeboat is obvious, the folding and unfolding difficulty is increased, the danger is increased, and therefore higher requirements are put forward on a device for folding and unfolding the lifeboat, namely, the wave compensation function is increased.

The realization of the heave compensation needs to ensure that the rope for hoisting the lifeboat is kept tensioned, and can be realized by setting the constant tension on the rope. The tension on the rope is fed back to a hydraulic system, namely the pressure, the overflow pressure of an overflow valve between an oil inlet and an oil outlet of a winch for retracting the lifeboat can be set, the constant tension of the rope wound on the winch under the working condition of wave compensation is set, and the lifeboat is guaranteed to sink and float along with waves. When the waves upwelling, the lifeboat is lifted up by the waves, the rope is loosened, the stress of the winch is smaller than the set wave compensation tension, the hydraulic oil pushes the winch to rotate forwards, the rope is tightened, and the lifeboat is tensioned. When the wave sinks, the lifeboat breaks away from the water surface, the whole gravity action of the lifeboat is on the winch, the stress of the winch is larger than the set wave compensation tension, hydraulic oil overflows through the overflow valve, and the winch rotates reversely under the action of the gravity of the lifeboat to transfer the lifeboat.

Common wave compensation hydraulic winch is mostly single motor structure, and the motor turns into the torque and the rotational speed of output shaft with hydraulic energy, through planet reduction gear with torque increase and rotational speed reduction, finally transmits for the reel, realizes the big moment of torsion operating mode of low-speed, is applicable to full-load take-off and land. During the wave compensation operating mode, reduce the motor discharge capacity through motor variable mechanism, the small discharge capacity of variable motor generally is 30% of full discharge capacity on the market, so, the tension of rope is 30% under the full load take-off and landing operating mode on the winch under the wave compensation operating mode, the speed of rope is 333% under the full load take-off and landing operating mode on the winch under the wave compensation operating mode, just also make the tension of rope when the heavy load lifeboat wave compensation too big, propose the surface of water with the lifeboat very easily, the wave is followed the effect and is not obvious, there is certain limitation.

The displacement of the main motor and the auxiliary motor of the double-motor structure wave compensation hydraulic winch has no special proportion constraint, theoretically, the displacement can reach any proportion, and the defects are overcome.

SUMMERY OF THE UTILITY MODEL

The utility model aims at solving the defects of the prior art, and providing a double-motor structure wave compensation hydraulic winch control system.

The utility model provides a double motor structure wave compensation hydraulic winch control system, includes hydraulic winch, main motor and main motor valve unit, vice motor and vice motor valve unit, hydraulic winch include frame, pivot, reel, planetary reducer, hydraulic disc brake, hydraulic disc clutch, encoder. The winding drum is arranged on the frame through a rotating shaft, the rotating shaft is connected with an output shaft of the main motor, a planetary reducer is arranged between the rotating shaft and the main motor, the planetary reducer reduces the rotating speed and increases the torque of the output shaft of the main motor, and a hydraulic disc brake is arranged on the output shaft of the main motor;

the winding drum is provided with a main gear, two sides of the main gear are respectively provided with a pinion which is meshed with the main gear, one pinion is connected with the encoder, and the other pinion is connected with an output shaft of the slave motor;

a hydraulic disc type clutch is arranged in a winding drum of the hydraulic winch, when no hydraulic oil enters a control port LH at the tail end of the hydraulic winch, the clutch holds an output shaft of the planetary reducer tightly under the action of spring force, and the motion of the main motor is transmitted to the clutch through the planetary reducer and finally transmitted to the winding drum; when oil enters a winch tail end control opening LH, the clutch is disengaged from an output shaft of the planetary reducer, the motion of the main motor is transmitted to the output shaft of the planetary reducer but cannot be transmitted to the winding drum, and the motion of the winding drum is not driven by the main motor and is only driven by the auxiliary motor;

the main motor converts hydraulic energy into torque and rotating speed of an output shaft of the main motor, then the mechanical energy is subjected to rotating speed reduction and torque increase through the planetary reducer, and finally the mechanical energy is transmitted to the winding drum through the normally closed clutch, so that the low-speed large-torque take-off and landing working condition is realized. Meanwhile, the main gear on the winding drum is meshed with the pinion gear on the output shaft of the slave motor to drive the output shaft of the slave motor to move along with the winding drum.

The main motor converts hydraulic energy into torque and rotating speed of an output shaft of the main motor, and then the mechanical energy is transmitted to the winding drum through gear engagement, so that the working condition of high-speed small-torque wave compensation is realized. At the same time, the normally closed clutch in the drum is opened, and the rotation of the drum is disengaged from the movement of the main motor and is driven only by the auxiliary motor.

As a further improvement, the hydraulic disc clutch is arranged in a winding drum, and the winding drum is used as a shell of the clutch.

As a further improvement, the main motor control valve group comprises a first electromagnetic valve, a second balance valve, a third shuttle valve, a fourth hydraulic reversing valve, a fifth pressure reducing valve, a sixth shuttle valve, a tenth one-way valve, an eleventh electromagnetic valve and a twelfth one-way valve, under the full-load lifting working condition, hydraulic oil enters the main motor control valve group from a winch lifting port, sequentially passes through the first electromagnetic valve, the third shuttle valve, the fourth hydraulic reversing valve, the fifth pressure reducing valve and the sixth shuttle valve, enters a brake ZD port, and opens a main motor brake to enable the main motor to be in a brake releasing state; meanwhile, hydraulic oil enters the port A of the main motor through the second balance valve to drive the output shaft of the main motor to rotate, and the working hydraulic oil flows out of the descending port of the winch through the port B of the main motor and the main motor control valve group.

As a further improvement, the auxiliary motor control valve group comprises a seventh reducing valve, an eighth check valve, a ninth electromagnetic valve, a thirteenth balance valve, a fourteenth shuttle valve, a fifteenth hydraulic reversing valve, a sixteenth reducing valve, a seventeenth check valve and an eighteenth overflow valve, under a full-load lifting working condition, hydraulic oil enters the auxiliary motor control valve group through an X port of the main motor control valve group, and then enters an auxiliary motor A, B port through the seventh reducing valve, the eighth check valve and the ninth electromagnetic valve in sequence, and the auxiliary motor control valve group is an oil supplementing way for the auxiliary motor to move along. When the winding drum rotates, the main gear on the winding drum is meshed with the pinion gear on the output shaft of the slave motor to drive the output shaft of the slave motor to rotate; and a ninth electromagnetic valve is arranged between the oil inlet and the oil outlet AB of the auxiliary motor, and the electromagnetic valve is normally open, namely, when the auxiliary motor is fully loaded in the lifting working condition, the oil inlet and the oil outlet AB of the auxiliary motor are communicated, so that the requirement of following the movement of the winding drum can be met. Meanwhile, the auxiliary motor has leakage, the oil quantity between the oil inlet and the oil outlet AB of the auxiliary motor is less and less after long-term use, the auxiliary motor is damaged by air suction, and therefore an oil supplementing way is needed for supplementing oil to the auxiliary motor.

As a further improvement, when hydraulic oil is stopped being input to a winch lifting opening or a winch descending opening, pressure oil in the brake flows out of a leakage opening L1 of a main motor control valve group through a sixth shuttle valve, a tenth one-way valve and a fourth hydraulic reversing valve in sequence, finally flows back to an oil tank, the brake is closed, and the winch brakes. When no hydraulic oil is input, the second balance valve can stop the load at any position, so that the dual guarantee that the parking load does not slide is realized.

As a further improvement, when the pressure of hydraulic oil entering the brake is lower than the set spring force of the fourth hydraulic reversing valve, the fourth hydraulic reversing valve does not act, at the moment, the hydraulic oil cannot enter the brake, and the brake is closed; when the hydraulic oil pressure entering the brake is higher than the spring force set by the fourth hydraulic reversing valve, the fourth hydraulic reversing valve reverses, the hydraulic oil enters the brake, and the brake is opened. The starting pressure of the brake is improved, and the phenomenon that the winch shakes as the brake is opened and closed intermittently due to oil pressure fluctuation is avoided.

As a further improvement, under the wave compensation working condition, the overflow pressure of an eighteenth overflow valve is set, and the constant tension of the winch under the wave compensation working condition is set; when the wave compensation working condition is automatically started, the first electromagnetic valve, the ninth electromagnetic valve and the eleventh electromagnetic valve are electrified, and oil is fed into a lifting opening of the winch; hydraulic oil flows into a VA port of the auxiliary motor control valve group through an eleventh electromagnetic valve, sequentially passes through a fourteenth shuttle valve, a fifteenth hydraulic reversing valve and a sixteenth pressure reducing valve, enters a clutch LH port and a Z port of the main motor control valve group, opens a clutch in the winding drum, enables the main motor and the winding drum to be separated, opens a brake of the main motor, and enables the main motor to be in a brake releasing state; meanwhile, hydraulic oil enters an auxiliary motor A port and an eighteenth overflow valve oil inlet through a thirteenth balance valve;

if the waves sink at the moment, the whole gravity of the load acts on the rope wound on the winding drum, the rope is tensioned, the winch is stressed to be larger than the set tension, the load falls under the action of the dead weight to drive the winch to rotate reversely, hydraulic oil flows out through the eighteenth overflow valve to supplement oil for the port B of the auxiliary motor, and redundant hydraulic oil directly flows out of the 'winch descending port' through the port VB of the auxiliary motor control valve group and the twelfth check valve and does not work on the auxiliary motor;

if the waves upwelling at the moment, the load is lifted by the waves, the rope wound on the winding drum becomes loose, the force of the winch is smaller than the set tension, the hydraulic oil flows into the port A of the auxiliary motor to drive the output shaft of the auxiliary motor to rotate positively, the winding drum is driven to rotate through gear engagement to tighten the rope and tighten the load, and the hydraulic oil after working flows out of the 'winch descending port' through the port B of the auxiliary motor, the port VB of the auxiliary motor control valve group and the twelfth one-way valve;

when the wave compensation is cancelled, the first electromagnetic valve, the ninth electromagnetic valve and the eleventh electromagnetic valve are powered off, and no hydraulic oil enters a winch lifting port; hydraulic oil in the clutch flows out of a leakage port L2 of the auxiliary motor control valve group through a seventeenth one-way valve and a fifteenth hydraulic reversing valve in sequence and finally flows back to an oil tank, and the clutch is closed; the pressure oil in the brake flows out of a leakage opening L1 of the main motor control valve group through a sixth shuttle valve, a tenth one-way valve and a fourth hydraulic reversing valve in sequence, finally flows back to an oil tank, the brake is closed, and the winch brakes; and then the full-load lifting working condition is recovered.

The utility model discloses there is following beneficial effect:

1. the brake in the winch is normally closed, the pressure is lost for braking, the drum stops rotating, and the load can be braked at any position.

2. The winding drum is directly used as a shell of the clutch, so the winch is compact in structure.

3. The brake and the second balance valve in the winch can stop the load at any position, so that the dual guarantee that the parking load does not slide is realized.

4. The fourth hydraulic reversing valve improves the oil pressure for opening the brake, and avoids the phenomenon that the winch shakes as the brake is opened and closed intermittently due to oil pressure fluctuation.

5. The double-motor structure has the advantages that the main motor and the planetary speed reducer are used for the full-load lifting working condition, the auxiliary motor and the pair of gears are meshed for the wave compensation working condition, the pair of gears are meshed for replacing the complex planetary speed reducer, the transmission efficiency is improved, the two working conditions are not related, and the requirement of light wave compensation of the large lifeboat can be met.

Drawings

FIG. 1 is a schematic diagram of the general configuration of a wave compensating hydraulic winch control system in a dual motor configuration;

FIG. 2 is a front view of a wave compensating hydraulic winch control system in a dual motor configuration;

FIG. 3 is a side view of a wave compensating hydraulic winch control system in a dual motor configuration;

FIG. 4 is a top view of a double motor configuration heave compensation hydraulic winch control system;

FIG. 5 is a hydraulic schematic of a double motor configuration heave compensation hydraulic winch control system;

1. the hydraulic control system comprises a first electromagnetic valve 2, a second balance valve 3, a third shuttle valve 4, a fourth hydraulic reversing valve 5, a fifth reducing valve 6, a sixth shuttle valve 7, a seventh reducing valve 8, an eighth one-way valve 9, a ninth electromagnetic valve 10, a tenth one-way valve 11, an eleventh electromagnetic valve 12, a twelfth one-way valve 13, a thirteenth balance valve 14, a fourteenth shuttle valve 15, a fifteenth hydraulic reversing valve 16, a sixteenth reducing valve 17, a seventeenth one-way valve 18, a eighteenth overflow valve 19, a winch lifting port 20, a winch descending port 21, a total leakage port 22, a main motor 23, a hydraulic disc brake 24, a planetary reducer 25, a rack 26, a winding drum 27, a hydraulic disc clutch 28, an encoder 29, an auxiliary motor control valve bank 31, a main motor control valve bank 32, an auxiliary gear 33 and a main gear.

Detailed Description

In order to deepen the understanding of the present invention, the present invention will be further described in detail with reference to the following embodiments and the attached drawings, and the embodiments are only used for explaining the present invention, and do not constitute the limitation to the protection scope of the present invention.

As shown in fig. 1 to 5, a double-motor structure wave compensation hydraulic winch control system includes a first electromagnetic valve 1, a second balance valve 2, a third shuttle valve 3, a fourth hydraulic directional valve 4, a fifth pressure reducing valve 5, a sixth shuttle valve 6, a seventh pressure reducing valve 7, an eighth check valve 8, a ninth electromagnetic valve 9, a tenth check valve 10, an eleventh electromagnetic valve 11, a twelfth check valve 12, a thirteenth balance valve 13, a fourteenth shuttle valve 14, a fifteenth hydraulic directional valve 15, a sixteenth pressure reducing valve 16, a seventeenth check valve 17, an eighteenth overflow valve 18, a winch lifting port 19, a winch descending port 20, a total leakage port 21, a main motor 22, a hydraulic disc brake 23, a planetary reducer 24, a frame 25, a winding drum 26, a hydraulic disc clutch 27, an encoder 28, an auxiliary motor 29, an auxiliary motor control valve bank 30, a main motor control valve bank 31, an auxiliary gear 32 and a main gear 33.

A double-motor structure wave compensation hydraulic winch control system comprises a hydraulic winch, a main motor control valve group, an auxiliary motor and an auxiliary motor control valve group; the hydraulic winch comprises a rack, a rotating shaft, a winding drum, a planetary reducer, a hydraulic disc brake, a hydraulic disc clutch and an encoder. The winding drum is arranged on the frame through a rotating shaft, and the rotating shaft is connected with an output shaft of the main motor; a planetary reducer is arranged between the rotating shaft and the main motor, and reduces the rotating speed and increases the torque of an output shaft of the main motor so as to meet the requirement of lifting or lowering the lifeboat under the full-load condition; a hydraulic disc brake is arranged on an output shaft of the main motor, the hydraulic disc brake is normally closed, when no hydraulic oil enters a front end control port ZD of the hydraulic winch, the brake tightly holds the output shaft of the main motor under the action of spring force, and the main motor cannot move, so that the purpose of braking is achieved; when oil enters a front end control opening ZD of the winch, the brake is separated from an output shaft of the main motor, the main motor is in a brake releasing state, and the motion of the main motor is transmitted to an output shaft of the planetary reducer;

the winding drum is provided with a main gear, two sides of the main gear are respectively provided with a pinion which is meshed with the main gear, one pinion is connected with an encoder, the encoder calculates the number of turns of the winding drum, further calculates the length of a rope wound on the winch for withdrawing (or lowering), further judges the height of the load lifted by the winch from the water surface, and finally feeds back the height to the control system for automatically activating the wave compensation working condition; the other pinion is connected with an output shaft of the pinion motor;

the hydraulic disc type clutch is arranged in the winding drum of the hydraulic winch and is installed in the winding drum, and the winding drum is directly used as a shell of the clutch, so that the hydraulic winch is compact in structure and small in size. When no hydraulic oil enters the hydraulic winch tail end control port LH, the clutch tightly holds the output shaft of the planetary reducer under the action of the spring force, and the motion of the main motor is transmitted to the clutch through the planetary reducer and finally transmitted to the winding drum; when oil enters a winch tail end control opening LH, the clutch is disengaged from an output shaft of the planetary reducer, the motion of the main motor is transmitted to the output shaft of the planetary reducer but cannot be transmitted to the winding drum, and the motion of the winding drum is not driven by the main motor and is only driven by the auxiliary motor;

the auxiliary motor and the rotating shaft are in gear engagement transmission, when the clutch is opened without pressure oil, the rotation of the winding drum is controlled by the main motor through the planetary reducer, and the winch is in a low-speed large-torque working condition and is suitable for full-load lifting. And the gear on the winding drum is always meshed with the gear of the output shaft of the auxiliary motor, so that the winding drum rotates to drive the auxiliary motor to move along. When the clutch is opened by pressure oil, the rotation of the winding drum is disengaged from the movement of the main motor, and at the moment, the rotation of the winding drum is only driven by the auxiliary motor through gear engagement without participation of other components, so that the transmission efficiency is high, the working condition of high speed and small torque can be realized, and the wave compensation device is suitable for wave compensation;

the main motor control valve group comprises a first electromagnetic valve, a second balance valve, a third shuttle valve, a fourth hydraulic reversing valve, a fifth pressure reducing valve, a sixth shuttle valve, a tenth check valve, an eleventh electromagnetic valve and a twelfth check valve, and the auxiliary motor control valve group comprises a seventh pressure reducing valve, an eighth check valve, a ninth electromagnetic valve, a thirteenth balance valve, a fourteenth shuttle valve, a fifteenth hydraulic reversing valve, a sixteenth pressure reducing valve, a seventeenth check valve and an eighteenth overflow valve;

under the working condition of full-load lifting, hydraulic oil enters a main motor control valve group from a winch lifting port, sequentially passes through a first electromagnetic valve, a third shuttle valve, a fourth hydraulic reversing valve, a fifth reducing valve and a sixth shuttle valve, enters a brake ZD port, and opens a main motor brake to enable the main motor to be in a brake releasing state; meanwhile, hydraulic oil enters the port A of the main motor through the second balance valve to drive the output shaft of the main motor to rotate, and the working hydraulic oil flows out of the 'winch descending port' through the port B of the main motor and the main motor control valve group; the main motor converts hydraulic energy into torque and rotating speed of an output shaft of the main motor, then the mechanical energy is subjected to rotating speed reduction and torque increase through the planetary reducer, and finally the mechanical energy is transmitted to the winding drum through the normally closed clutch, so that the low-speed large-torque lifting working condition is realized. Meanwhile, hydraulic oil enters an X port of the auxiliary motor control valve group, and then enters a A, B port of the auxiliary motor through a seventh reducing valve, an eighth check valve and a ninth electromagnetic valve in sequence, and the oil supplementing way is an oil supplementing way for the auxiliary motor to move along. When the winding drum rotates, a gear on the winding drum is meshed with an output shaft gear of the auxiliary motor to drive the auxiliary motor to rotate; and a ninth electromagnetic valve is arranged between the oil inlet and the oil outlet AB of the auxiliary motor, is normally open, namely is communicated with the oil inlet and the oil outlet AB of the auxiliary motor under the full-load lifting working condition, and can meet the requirement of following the movement of the winding drum. However, the auxiliary motor is leaked, the oil quantity between the oil inlet and the oil outlet AB of the auxiliary motor is less and less after long-term use, and the auxiliary motor is damaged by air suction, so that an oil supplementing way is needed for supplementing oil to the auxiliary motor.

The full-load descending working condition is similar to the full-load lifting working condition, and the description is omitted here.

When hydraulic oil is stopped being input into a lifting opening (or a descending opening) of the winch, the pressure oil in the brake flows out of a leakage opening L1 of a main motor control valve group through a sixth shuttle valve, a tenth one-way valve and a fourth hydraulic reversing valve in sequence, finally flows back to an oil tank, the brake is closed, and the winch brakes. When no hydraulic oil is input, the second balance valve can stop the load at any position, so that the dual guarantee that the parking load does not slide is realized.

The fourth hydraulically operated directional control valve increases the oil pressure at which the brake is opened. When the pressure of the hydraulic oil entering the brake is lower than the spring force set by the hydraulic reversing valve, the hydraulic reversing valve does not act, at the moment, the hydraulic oil cannot enter the brake, and the brake is closed. When the hydraulic oil pressure entering the brake is higher than the spring force set by the hydraulic reversing valve, the hydraulic reversing valve reverses, the hydraulic oil enters the brake, and the brake is opened. The starting pressure of the brake is improved, and the phenomenon that the winch shakes as the brake is opened and closed intermittently due to oil pressure fluctuation is avoided.

And under the wave compensation working condition, the overflow pressure of the eighteenth overflow valve is set, and the constant tension of the winch under the wave compensation working condition is set. When the wave compensation working condition is automatically opened, the first electromagnetic valve, the ninth electromagnetic valve and the eleventh electromagnetic valve are electrified, and oil enters a winch lifting opening. Hydraulic oil flows into a VA port of the auxiliary motor control valve group through an eleventh electromagnetic valve, sequentially passes through a fourteenth shuttle valve, a fifteenth hydraulic reversing valve and a sixteenth pressure reducing valve, enters a LH port of the clutch and a Z port of the main motor control valve group, opens the clutch in the winding drum, enables the main motor and the winding drum to be separated, opens a brake of the main motor, and enables the main motor to be in a brake releasing state. Meanwhile, hydraulic oil enters the port A of the auxiliary motor and the oil inlet of the eighteenth overflow valve through the thirteenth balance valve.

If the wave sinks at the moment, the whole gravity of the load acts on the rope wound on the winding drum, the rope is tensioned, the force of the winch is greater than the set tension, the load falls under the action of the dead weight to drive the winch to rotate reversely, hydraulic oil flows out through the eighteenth overflow valve to supplement oil for the port B of the auxiliary motor, and redundant hydraulic oil directly flows out of the 'winch descending port' through the port VB of the auxiliary motor control valve group and the twelfth check valve and does not work on the auxiliary motor.

If the waves upwelle at the moment, the load is lifted by the waves, the rope wound on the winding drum becomes loose, the force of the winch is smaller than the set tension at the moment, the hydraulic oil flows into the port A of the auxiliary motor, the output shaft of the auxiliary motor is driven to rotate, the winding drum is driven to rotate through gear engagement, the rope is tightened, the load is tensioned, and the hydraulic oil after working flows out of the descending port of the winch through the port B of the auxiliary motor, the port VB of the auxiliary motor control valve group and the twelfth one-way valve.

When the wave compensation is cancelled, the first electromagnetic valve, the ninth electromagnetic valve and the eleventh electromagnetic valve are powered off, and no hydraulic oil enters the winch lifting port. Hydraulic oil in the clutch flows out of a leakage port L2 of the auxiliary motor control valve group through a seventeenth one-way valve and a fifteenth hydraulic reversing valve in sequence and finally flows back to an oil tank, and the clutch is closed. And pressure oil in the brake flows out of a leakage port L1 of the main motor control valve group through a sixth shuttle valve, a tenth one-way valve and a fourth hydraulic reversing valve in sequence, finally flows back to an oil tank, the brake is closed, and the winch brakes. And then the full-load lifting working condition is recovered.

The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A double-motor structure wave compensation hydraulic winch control system is characterized by comprising a hydraulic winch, a main motor control valve group, an auxiliary motor and an auxiliary motor control valve group, wherein the hydraulic winch comprises a rack, a rotating shaft, a winding drum, a planetary reducer, a hydraulic disc brake, a hydraulic disc clutch and an encoder, the winding drum is installed on the rack through the rotating shaft, the rotating shaft is connected with an output shaft of the main motor, the planetary reducer is arranged between the rotating shaft and the main motor, the planetary reducer reduces the rotating speed and increases the torque of the output shaft of the main motor, and the hydraulic disc brake is arranged on the output shaft of the main motor;

a hydraulic disc type clutch is arranged in a winding drum of the hydraulic winch, when no hydraulic oil enters a control port LH at the tail end of the hydraulic winch, the clutch holds an output shaft of the planetary reducer tightly under the action of spring force, and the motion of the main motor is transmitted to the clutch through the planetary reducer and finally transmitted to the winding drum; when oil enters a winch tail end control opening LH, the clutch is disengaged from an output shaft of the planetary reducer, the motion of the main motor is transmitted to the output shaft of the planetary reducer but cannot be transmitted to the winding drum, and the motion of the winding drum is not driven by the main motor and is only driven by the auxiliary motor.

2. The double motor structural heave compensation hydraulic winch control system according to claim 1, wherein the hydraulic disc clutch is mounted inside a drum, and the drum serves as a housing for the clutch.

3. The double-motor structure wave compensation hydraulic winch control system according to claim 1, wherein the main motor control valve group comprises a first electromagnetic valve, a second balance valve, a third shuttle valve, a fourth hydraulic reversing valve, a fifth pressure reducing valve, a sixth shuttle valve, a tenth check valve, an eleventh electromagnetic valve and a twelfth check valve, under a full-load lifting condition, hydraulic oil enters the main motor control valve group from a winch lifting port, sequentially passes through the first electromagnetic valve, the third shuttle valve, the fourth hydraulic reversing valve, the fifth pressure reducing valve and the sixth shuttle valve, enters a brake ZD port, and opens a main motor brake to enable the main motor to be in a brake releasing state; meanwhile, hydraulic oil enters the port A of the main motor through the second balance valve to drive the output shaft of the main motor to rotate, and the working hydraulic oil flows out of the descending port of the winch through the port B of the main motor and the main motor control valve group.

4. The double-motor structural wave compensation hydraulic winch control system according to claim 1, wherein the auxiliary motor control valve group comprises a seventh reducing valve, an eighth check valve, a ninth electromagnetic valve, a thirteenth balance valve, a fourteenth shuttle valve, a fifteenth hydraulic reversing valve, a sixteenth reducing valve, a seventeenth check valve and an eighteenth overflow valve, under a full-load lifting working condition, hydraulic oil enters the auxiliary motor control valve group through an X port of the main motor control valve group and then enters a A, B port of the auxiliary motor through the seventh reducing valve, the eighth check valve and the ninth electromagnetic valve in sequence, the oil supplementing way is an oil supplementing way for the auxiliary motor to follow motion, and when the winding drum rotates, a main gear on the winding drum is meshed with an auxiliary gear on an output shaft of the auxiliary motor to drive the output shaft of the auxiliary motor to rotate; and a ninth electromagnetic valve is arranged between the oil inlet and the oil outlet AB of the auxiliary motor, and the electromagnetic valve is normally open, namely, when the auxiliary motor is fully loaded in the lifting working condition, the oil inlet and the oil outlet AB of the auxiliary motor are communicated, so that the requirement of following the movement of the winding drum can be met.

5. The system as claimed in claim 3, wherein when the hydraulic oil is stopped being supplied to the winch lifting port or the winch lowering port, the pressure oil in the brake sequentially flows out of the leakage port L1 of the main motor control valve set through the sixth shuttle valve, the tenth check valve and the fourth hydraulic directional control valve, and finally flows back to the oil tank, the brake is closed, the winch is braked, and when no hydraulic oil is supplied, the second balance valve can stop the load at any position.

6. The double-motor structural heave compensation hydraulic winch control system according to claim 5, wherein when the pressure of hydraulic oil entering the brake is lower than the spring force set by the fourth hydraulic directional valve, the fourth hydraulic directional valve does not act, at this time, hydraulic oil cannot enter the brake, and the brake is closed; when the hydraulic oil pressure entering the brake is higher than the spring force set by the fourth hydraulic reversing valve, the fourth hydraulic reversing valve reverses, the hydraulic oil enters the brake, and the brake is opened.

7. The double-motor structural heave compensation hydraulic winch control system according to claim 3 or 4, wherein under the heave compensation working condition, the overflow pressure of an eighteenth overflow valve is set, and the constant tension of the winch under the heave compensation working condition is set; when the wave compensation working condition is automatically opened, the first electromagnetic valve, the ninth electromagnetic valve and the eleventh electromagnetic valve are electrified, and oil is fed into a lifting opening of the winch; hydraulic oil flows into a VA port of the auxiliary motor control valve group through an eleventh electromagnetic valve, sequentially passes through a fourteenth shuttle valve, a fifteenth hydraulic reversing valve and a sixteenth pressure reducing valve, enters a clutch LH port and a Z port of the main motor control valve group, opens a clutch in the winding drum, enables the main motor and the winding drum to be separated, opens a brake of the main motor, and enables the main motor to be in a brake releasing state; meanwhile, hydraulic oil enters the port A of the auxiliary motor and the oil inlet of the eighteenth overflow valve through the thirteenth balance valve;