Hydraulic control system of stern anchor machine

Abstract

The invention relates to the technical field of stern anchor gears, in particular to a hydraulic control system of a stern anchor gear. The hydraulic control system comprises a stern anchor machine, a brake hydraulic cylinder, a clutch hydraulic cylinder, a main control valve group, a brake clutch control valve group and a hydraulic pump station, and the main control valve group comprises a hydraulic proportional reversing valve, a balance valve and an electric control assembly. The electric control assembly comprises a first electric control proportional reversing valve and a second electric control proportional reversing valve which are connected to the two sides of the hydraulic proportional reversing valve in series. The hydraulic pump station generates high-pressure oil to drive the main control valve group and the brake clutch valve group to act, and the shuttle valve at the main control valve group feeds back a load signal to the hydraulic pump station, so that the rotating speed, the steering direction and the displacement of the hydraulic motor can be controlled, and the working efficiency of the stern anchor machine can be better improved in cooperation with actions of a brake and a clutch; therefore, the working condition requirements of high-speed cable take-up and pay-off, light-load cable take-up and pay-off and heavy-load anchor pulling and dropping of the stern anchor machine are met.

Description

Technical Field

[0001] The invention relates to the technical field of stern windlasses, and in particular to a stern windlass hydraulic control system. Background Art

[0002] In ship operation, the stern windlass is an important equipment, mainly used to control the lowering and recovery of anchors during the process of mooring, anchoring or towing. Since the deck at the stern is an important working area, it is difficult to set up an anchor chain locker, and steel ropes are generally used instead of anchor chains to release and retract the anchor.

[0003] Since the stern anchor windlass is arranged at the stern of the ship, it is required to have a faster speed when retrieving and releasing the anchor to prevent the anchor from drifting in the water, causing the steel rope or anchor to collide with the propeller at the stern of the ship, causing damage to the propeller. In the prior art, the ratio of the rated speed to the light load speed of the conventional anchor windlass is generally 1:2 or 1:3, while the ratio of the rated speed to the light load speed required by the stern anchor windlass is generally above 1:10. Therefore, it is difficult to achieve the requirement of using the steel rope to retract and release the anchor by using the conventional anchor windlass drive. Summary of the invention

[0004] The invention provides a stern windlass hydraulic control system, which can overcome certain defects of the prior art.

[0005] The stern anchor winch hydraulic control system according to the present invention comprises a stern anchor winch, a brake hydraulic cylinder and a clutch hydraulic cylinder, and a main control valve group, which has a hydraulic motor, and the hydraulic motor is used to drive the stern anchor winch; a brake clutch control valve group, which is connected to the brake hydraulic cylinder and the clutch hydraulic cylinder; a hydraulic pump station, which has a first oil supply end, a second oil supply end and an oil return end, the first oil supply end is used to connect the main control valve group, the second oil supply end is used to connect the brake clutch control valve group, and the oil return end is connected to both the main control valve group and the brake clutch control valve group; wherein the main control valve group comprises a hydraulic proportional reversing valve , a balancing valve and an electronically controlled component, the electronically controlled component comprising a first electronically controlled proportional reversing valve and a second electronically controlled proportional reversing valve connected in series on both sides of the hydraulic proportional reversing valve; the hydraulic proportional reversing valve has a first state and a second state, in the first state, the first electronically controlled proportional reversing valve, the hydraulic proportional reversing valve, the balancing valve and the hydraulic motor jointly define a lifting circuit, in the second state, the second electronically controlled proportional reversing valve, the hydraulic proportional reversing valve and the hydraulic motor jointly define a lowering circuit; a shuttle valve is connected between the lifting circuit and the lowering circuit, and the shuttle valve is connected to the hydraulic pump station.

[0006] Furthermore, the hydraulic proportional reversing valve has a first port, which is used to connect to the first oil supply end; a second port, which is used to connect to the oil return end; a first working port, which is used to connect to the balancing valve, the balancing valve has a first connection port and a second connection port, the first connection port is connected to the first working port; the second working port, which is used to connect to the hydraulic motor, the hydraulic motor has a lifting port and a lowering port, and the second connection port is connected to the lowering port.

[0007] Furthermore, the shuttle valve is connected to the lifting port and the lowering port respectively; the shuttle valve has a side branch, which is used to connect the hydraulic oil at the lifting port or the lowering port. A displacement control valve is correspondingly provided at the hydraulic motor, and the side branch is connected to the displacement control valve. The shuttle valve is sequentially provided with a first pressure reducing valve and a first solenoid reversing valve along the side branch. The first solenoid reversing valve is used to transport the hydraulic oil at the first pressure reducing valve to the displacement control valve.

[0008] Furthermore, a first safety valve is connected between the first connecting port and the lifting port, and the first safety valve is connected to the oil return end.

[0009] Furthermore, the main control valve group also includes a second pressure reducing valve, which has a first access point and a second access point at both ends. The first access point is used to connect to the first oil supply end, and the second access point is used to connect to the first electrically controlled proportional reversing valve and the second electrically controlled proportional reversing valve.

[0010] Furthermore, the hydraulic proportional reversing valve also has a lifting side control port and a lowering side control port. The lifting side control port is used to be connected to the first electrically controlled proportional reversing valve, and the first electrically controlled proportional reversing valve is used to provide the lifting side control hydraulic oil pressure to the lifting side control port. The lowering side control port is used to be connected to the second electrically controlled proportional reversing valve, and the second electrically controlled proportional reversing valve is used to provide the lowering side control hydraulic oil pressure to the lowering side control port.

[0011] Furthermore, the brake clutch valve group includes a brake valve group and a clutch valve group, the brake valve group is used to connect to the brake hydraulic cylinder, and the clutch valve group is used to connect to the clutch hydraulic cylinder; the brake valve group includes a third pressure reducing valve and a second electromagnetic reversing valve connected in sequence, there are multiple third pressure reducing valves and they are connected in parallel, one end of the third pressure reducing valve is connected to the second oil supply end, and the other end is connected to the second electromagnetic reversing valve, and a first oil inlet is provided at the brake hydraulic cylinder, and the first oil inlet is connected to the second electromagnetic reversing valve; the clutch valve group includes a fourth pressure reducing valve, a third electromagnetic reversing valve and a fuel-saving valve connected in sequence, there are multiple fourth pressure reducing valves and they are connected in parallel, one end of the fourth pressure reducing valve is connected to the second oil supply end, and the other end is connected to the third electromagnetic reversing valve, and a second oil inlet is provided at the clutch hydraulic cylinder, one end of the fuel-saving valve is connected to the second oil inlet valve, and the other end is connected to the third electromagnetic reversing valve.

[0012] Furthermore, the brake valve group also includes a second safety valve arranged between the second electromagnetic reversing valve and the first oil inlet; the clutch valve group also includes a third safety valve arranged between the throttling valve and the second oil inlet.

[0013] Furthermore, the hydraulic pump station includes an oil tank, a motor pump group is provided on one side of the oil tank, a pump control valve group is provided at the motor pump group, the motor pump group is used to generate high-pressure oil, the motor pump group has an oil supply port, a one-way valve is connected to the oil supply port, the one-way valve is connected to the first oil supply end and the second oil supply end respectively, a feedback port is provided at the pump control valve group, the feedback port is used to connect to the hydraulic motor and the shuttle valve, and the pump control valve group is electrically connected to the main control valve group.

[0014] Furthermore, an oil return port is provided at the oil tank, an oil return filter is provided at the oil return port, and the oil return filter is connected to the oil return end; a liquid temperature sensor is provided on the top of the oil tank, and the liquid temperature sensor is used to measure the temperature of the hydraulic oil in the oil tank; a liquid level display is provided on the side wall of the oil tank, and the liquid level display is connected to the oil tank; an air filter is also provided on the top of the oil tank, and the air filter is connected to the oil tank. Beneficial Effects

[0015] The hydraulic pump station generates high-pressure oil to drive the main control valve group and the brake clutch valve group. The shuttle valve at the main control valve group feeds back the load signal to the hydraulic pump station, thereby controlling the speed, steering and displacement of the hydraulic motor. In coordination with the action of the brake and clutch, the working efficiency of the stern anchor winch can be improved to a greater extent, thereby achieving the working requirements of the stern anchor winch for high-speed cable collection and release, light-load cable collection and release, and heavy-load anchoring.

[0016] Furthermore, by setting a balancing valve at the main control valve group, the mid-position slip protection during the anchoring process is better achieved, thereby making the anchoring process smoother. By setting the first safety valve, the second safety valve and the third safety valve, the working pressure at each execution unit is better not to exceed the set value, thereby eliminating some safety hazards.

[0017] Furthermore, an oil return filter, a liquid temperature sensor, a liquid level display and an air filter are provided at the hydraulic pump station, so as to better ensure the supply quality of the hydraulic oil. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 A schematic diagram of a stern windlass hydraulic control system provided in at least one embodiment of the present application; Figure 2 A schematic diagram of a main control valve group provided in at least one embodiment of the present application; Figure 3 A schematic diagram of a brake clutch control valve assembly provided in at least one embodiment of the present application; Figure 4 A schematic diagram of a hydraulic pump station provided in at least one embodiment of the present application. DETAILED DESCRIPTION

[0019] In order to further understand the content of the present invention, the present invention is described in detail in conjunction with the embodiments. It should be understood that the embodiments are only for explaining the present invention and are not intended to limit it.

[0020] See Figure 1-2 The present embodiment provides a hydraulic control system for a stern windlass 1, comprising a stern windlass 1, a brake hydraulic cylinder 2 and a clutch hydraulic cylinder 3. The stern windlass 1 is used for retracting and releasing the anchor chain, the brake hydraulic cylinder 2 can realize the braking action of the stern windlass 1, and the clutch hydraulic cylinder 3 can realize the separation and connection of the clutch.

[0021] It can be understood that the brake and the clutch are both arranged at the stern windlass 1 .

[0022] Furthermore, the hydraulic control system of the stern windlass 1 also includes a main control valve group 4 having a hydraulic motor 5, and the hydraulic motor 5 is used to drive the stern windlass 1, so as to realize the retraction and extension of the anchor chain.

[0023] Furthermore, the hydraulic control system of the stern windlass 1 also includes a brake clutch control valve group 6, which is connected to the brake hydraulic cylinder 2 and the clutch hydraulic cylinder 3. The brake clutch control valve group 6 is used to control the opening and closing of the brake, and the separation and connection of the clutch, so as to better control the working state of the stern windlass 1.

[0024] Furthermore, the hydraulic control system of the stern anchor winch 1 also includes a hydraulic pump station 7, having a first oil supply end 701, a second oil supply end 702 and an oil return end 703, the first oil supply end 701 is used to connect the main control valve group 4, the second oil supply end 702 is used to connect the brake clutch control valve group 6, the return oil end 703 is connected to both the main control valve group 4 and the brake clutch control valve group 6, the hydraulic pump station 7 can generate high-pressure oil, supply oil to the main control valve group 4 through the first oil supply end 701, thereby realizing the action of the main control valve group 4 to control the hydraulic motor 5, and supply oil to the brake clutch valve group 62 through the second oil supply end 702, thereby realizing the action of the brake or clutch, and the return oil end 703 can realize the high-pressure oil reflux to the hydraulic pump station 7, thereby realizing the reuse of hydraulic oil.

[0025] Through the above structure, the hydraulic pump station 7 generates high-pressure oil to drive the main control valve group 4 and the brake clutch valve group 62 to operate. The main control valve group 4 can control the speed, steering and displacement of the hydraulic motor 5. In coordination with the actions of the brake and the clutch, the working efficiency of the stern anchor winch 1 can be improved to a better extent, thereby achieving the working conditions of the stern anchor winch 1 for high-speed cable collection and release, light-load cable collection and release, and heavy-load anchoring.

[0026] Among them, the main control valve group 4 includes a hydraulic proportional reversing valve 401, a balancing valve 402 and an electronic control component, and the electronic control component includes a first electronically controlled proportional reversing valve 403 and a second electronically controlled proportional reversing valve 404 connected in series on both sides of the hydraulic proportional reversing valve 401; the hydraulic proportional reversing valve 401 has a first state and a second state.

[0027] Specifically, in the first state, the first proportional electronically controlled reversing valve, the hydraulic proportional reversing valve 401, the balancing valve 402 and the hydraulic motor 5 jointly define a lifting circuit, and the lifting circuit is used for the stern anchor machine 1 to lift the anchor chain. Since lifting the anchor chain requires achieving the effects of large-load anchoring and high-speed anchor retraction, the balancing valve 402 is provided to better achieve the mid-position slip protection function during the anchoring process, so that the working pressure when the anchor chain is lifted does not exceed the rated working pressure of the hydraulic motor 5.

[0028] Specifically, in the second state, the second electrically controlled proportional reversing valve 404, the hydraulic proportional reversing valve 401 and the hydraulic motor 5 jointly define a lowering circuit.

[0029] Among them, the first electrically controlled proportional reversing valve 403 can provide the lifting side control hydraulic oil pressure to the hydraulic proportional reversing valve 401 in proportion according to the electrical signal, and the second electrically controlled proportional reversing valve 404 can provide the lower side control hydraulic oil pressure to the hydraulic proportional reversing valve 401 in proportion according to the electrical signal, thereby better adjusting the hydraulic oil pressure at the hydraulic motor 5 to meet the load conditions.

[0030] Furthermore, a shuttle valve 405 is connected between the lifting circuit and the lowering circuit. The shuttle valve 405 is connected to the hydraulic pump station 7. The shuttle valve 405 can feed back the load in the lifting circuit or the lowering circuit to the hydraulic pump station 7, thereby controlling the hydraulic pump station 7 to change the output hydraulic oil flow rate to improve the work efficiency of the lifting operation and the lowering operation.

[0031] Through the above structure, the flow of the hydraulic pump station 7 can be controlled by the feedback load signal, and the hydraulic oil pressure on the lifting side and the lower side can be adjusted by the first proportional electronically controlled reversing valve and the second proportional electronically controlled reversing valve, so that the working efficiency of the hydraulic motor 5 can be further improved. Under the premise of meeting the rated working pressure of the hydraulic motor 5, the ratio of the rated speed of the hydraulic motor 5 to the light load speed can be further reduced, thereby better meeting the use conditions of the stern anchor winch 1, not only protecting the stern anchor winch 1 and the hydraulic motor 5, but also better extending the service life and maintenance time of the stern anchor winch 1 and the hydraulic motor 5.

[0032] Specifically, the hydraulic proportional reversing valve 401 is a three-position four-way proportional reversing valve, which has a first port 4011, and the first port 4011 is used to connect with the first oil supply end 701; the second port 4012 is used to connect with the oil return end 703; the first working port 4013 is used to connect with the balance valve 402, and the balance valve 402 adopts a plate-type two-position two-way proportional reversing valve, and has a first connection port 4021 and a second connection port 4014, and the first connection port 4021 is connected to the first working port 4013; the second working port 4022 is used to connect with the hydraulic motor 5, and the hydraulic motor 5 has a lifting port 51 and a lowering port 52, and the second connection port 4014 is connected to the lowering port 52. The hydraulic proportional reversing valve 401 can deliver driving hydraulic oil to the hydraulic motor 5, thereby controlling the direction and speed of the hydraulic motor 5.

[0033] The main control valve group 4 also includes a second pressure reducing valve 410, which has a first access point 411 and a second access point 412 at both ends. The first access point 411 is used to connect to the first oil supply end 701, and the second access point 412 is used to connect to the first electrically controlled proportional reversing valve 403 and the second electrically controlled proportional reversing valve 404. The second pressure reducing valve 410 can reduce the pressure at the first oil supply end 701 of the hydraulic pump station 7 to the control pressure of the first electrically controlled proportional reversing valve 403 and the second proportional reversing valve, so that the first electrically controlled proportional reversing valve 403 and the second proportional reversing valve can work normally.

[0034] It can be understood that the shuttle valve 405 has a side branch 406, which is used to connect the hydraulic oil at the lifting port 51 or the lowering port 52. A displacement control valve is correspondingly provided at the hydraulic motor 5. The side branch 406 is connected to the displacement control valve. The shuttle valve 405 is provided with a first pressure reducing valve 407 and a first electromagnetic reversing valve 408 in sequence along the side branch 406. The first electromagnetic reversing valve 408 is used to transport the hydraulic oil at the first pressure reducing valve 407 to the displacement control valve. The first pressure reducing valve 407 can reduce the pressure of the hydraulic oil at the lifting port 51 or the lowering port 52 to the working pressure of the first electromagnetic reversing valve 408. The first electromagnetic reversing valve 408 is a two-position three-way reversing valve. The first electromagnetic reversing valve 408 can provide pressure to control the displacement control valve, thereby changing the displacement of the hydraulic motor 5 according to the working load at the lifting port 51 or the lowering port 52, thereby improving the adjustment ability of the hydraulic motor 5 to cope with load changes.

[0035] In some specific embodiments, a first safety valve 409 is connected between the first connecting port 4021 and the lifting port 51. The first safety valve 409 is connected to the return oil end 703. The first safety valve 409 can overflow when the pressure at the lifting port 51 is too high, thereby keeping the oil pressure at the hydraulic motor 5 not exceeding the set value.

[0036] Furthermore, the hydraulic proportional reversing valve 401 also has a lifting side control port 4015 and a lowering side control port 4016. The lifting side control port 4015 is used to connect with the first electrically controlled proportional reversing valve 403, and the first electrically controlled proportional reversing valve 403 is used to provide the lifting side control hydraulic oil pressure to the lifting side control port 4015. The lowering side control port 4016 is used to connect with the second electrically controlled proportional reversing valve 404, and the second electrically controlled proportional reversing valve 404 is used to provide the lowering side control hydraulic oil pressure to the lowering side control port 4016.

[0037] See Figure 3 In some specific embodiments, the brake clutch valve group 62 includes a brake valve group 61 and a clutch valve group 62. The brake valve group 61 is used to connect with the brake hydraulic cylinder 2, and the clutch valve group 62 is used to connect with the clutch hydraulic cylinder 3. The brake valve group 61 is used to control the brake hydraulic cylinder 2, and the clutch valve group 62 is used to control the clutch hydraulic cylinder 3. When the hydraulic oil enters the brake hydraulic cylinder 2, the brake is opened, and when the hydraulic oil leaves the brake hydraulic cylinder 2, the brake is closed. When the hydraulic oil enters the clutch hydraulic cylinder 3, the clutch is closed, and when the hydraulic oil leaves the clutch hydraulic cylinder 3, the clutch is separated.

[0038] Furthermore, the brake valve group 61 includes a third pressure reducing valve 611 and a second electromagnetic reversing valve 612 connected in sequence. There are multiple third pressure reducing valves 611 and they are connected in parallel. One end of the third pressure reducing valve 611 is connected to the second oil supply end 702, and the other end is connected to the second electromagnetic reversing valve 612. The third pressure reducing valve 611 is used to reduce the oil pressure of the second oil supply end 702 to the working pressure of the second electromagnetic reversing valve 612 and the brake hydraulic cylinder 2. A first oil inlet 21 is provided at the brake hydraulic cylinder 2, and the first oil inlet 21 is connected to the second electromagnetic reversing valve 612. The second electromagnetic reversing valve 612 is a two-position four-way reversing valve. When power is not supplied, oil is not supplied to the brake hydraulic cylinder 2. When power is supplied, high-pressure oil is supplied to the brake hydraulic cylinder 2 to open the brake.

[0039] Furthermore, the clutch valve group 62 includes a fourth pressure reducing valve 621, a third electromagnetic reversing valve 622 and a throttling valve 623 connected in sequence. There are multiple fourth pressure reducing valves 621 and they are connected in parallel. One end of the fourth pressure reducing valve 621 is connected to the second oil supply end 702, and the other end is connected to the third electromagnetic reversing valve 622. The fourth pressure reducing valve 621 is used to reduce the pressure at the second oil supply end 702 to the working pressure of the third electromagnetic reversing valve 622 and the clutch hydraulic cylinder 3. The clutch hydraulic cylinder 3 is provided with a second oil inlet 31. One end of the throttling valve 623 is connected to the second oil inlet valve, and the other end is connected to the third electromagnetic reversing valve 622. The third electromagnetic reversing valve 622 is a two-position four-way reversing valve. When power is not supplied, oil is not supplied to the clutch hydraulic cylinder 3, and the clutch is in a disengaged state. When power is supplied, high-pressure oil is led to the clutch to close the clutch.

[0040] It is worth noting that the brake valve group 61 also includes a second safety valve 613 arranged between the second solenoid reversing valve 612 and the first oil inlet 21; the clutch valve group 62 also includes a third safety valve 624 arranged between the throttle valve 623 and the second oil inlet 31. The second safety valve 613 can overflow when the oil pressure at the brake hydraulic cylinder 2 is too high, and the third safety valve 624 can overflow when the oil pressure at the clutch hydraulic cylinder 3 is too high, thereby better ensuring that the oil pressure at the brake hydraulic cylinder 2 and the clutch hydraulic cylinder 3 does not exceed the set value.

[0041] See Figure 4 , illustratively, the hydraulic pump station 7 in the present application includes an oil tank 704, a motor pump group 705 is provided on one side of the oil tank 704, a pump control valve group 706 is provided at the motor pump group 705, the motor pump group 705 is used to generate high-pressure oil, the motor pump group 705 has an oil supply port 707, a one-way valve 708 is connected to the oil supply port 707, the one-way valve 708 is respectively connected to the first oil supply end 701 and the second oil supply end 702, a feedback port 709 is provided at the pump control valve group 706, the feedback port 709 is used to connect to the hydraulic motor 5 and the shuttle valve 405, and the pump control valve group 706 is electrically connected to the main control valve group 4.

[0042] Specifically, the pump-controlled valve group 706 is electrically connected to the first electrically-controlled proportional reversing valve 403 and the second electrically-controlled proportional reversing valve 404 at the main control valve group 4. When the pressure changes at the hydraulic motor 5 and the shuttle valve 405 are obtained at the feedback port 709, the pump-controlled valve group 706 generates an electrical signal to control the operation of the first electrically-controlled proportional reversing valve 403 and the second electrically-controlled proportional reversing valve 404, and at the same time controls the motor pump group 705 to change the output flow.

[0043] It can be understood that the motor pump group 705 includes a hydraulic pump, and a swash plate is provided at the hydraulic pump to change the flow of the hydraulic pump through the swash plate.

[0044] Furthermore, an oil return port 710 is provided at the oil tank 704, and an oil return filter 711 is provided at the oil return port 710, and the oil return filter 711 is connected to the oil return end 703; a liquid temperature sensor 712 is provided on the top of the oil tank 704, and the liquid temperature sensor 712 is used to measure the temperature of the hydraulic oil in the oil tank 704; a liquid level display 713 is provided on the side wall of the oil tank 704, and the liquid level display 713 is connected to the oil tank 704; an air filter 714 is also provided on the top of the oil tank 704, and the air filter 714 is connected to the oil tank 704.

[0045] That is, in actual use, the state of the hydraulic oil is first checked through the liquid level display 713 and the liquid temperature sensor 712 at the oil tank 704. After confirming that there is no abnormality, the motor pump group 705 is started to enter the ready working state.

[0046] When a heavy load anchoring operation is required, after the feedback port 709 senses the load, the third electromagnetic reversing valve 622 is controlled to be energized to reverse the direction of its valve core, control the hydraulic oil to enter the clutch hydraulic cylinder 3, and close the clutch. At the same time, the second electromagnetic reversing valve 612 is controlled to be energized to reverse the direction of its valve core, control the hydraulic oil to enter the brake hydraulic cylinder 2, and open the brake. The first electronically controlled proportional reversing valve 403 is controlled to obtain an analog electrical signal to reverse the direction of its valve core in proportion, and control the hydraulic oil to the lifting side control port 4015 of the hydraulic proportional reversing valve 401. After the hydraulic proportional reversing valve 401 obtains the hydraulic oil, its valve core is reversed in proportion, and the hydraulic oil is transported to the lifting port 51 of the hydraulic motor 5 through the lifting oil circuit, so that the hydraulic motor 5 starts to work and anchor. During the anchoring process, the situation fed back to the feedback port 709 through the shuttle valve 405 enables the displacement control valve to adjust the displacement of the hydraulic motor 5 according to different loads, thereby improving the working efficiency of the hydraulic motor 5.

[0047] Furthermore, when a heavy-load anchoring operation is required, the second electrically controlled proportional reversing valve 404 is controlled to obtain an analog electrical signal, causing its valve core to switch proportionally, thereby controlling the hydraulic oil to flow to the lower side control port 4016 of the hydraulic proportional reversing valve 401. After the hydraulic proportional reversing valve 401 obtains the hydraulic oil, its valve core switches proportionally, allowing the hydraulic oil to flow through the lower oil circuit to the lower port 52 of the hydraulic motor 5.

[0048] After the heavy-load anchoring operation is completed, the third electromagnetic reversing valve 622 is controlled to lose power, so that its valve core is reversed, and the hydraulic oil is controlled not to enter the clutch hydraulic cylinder 3, so that the clutch is disengaged; the second electromagnetic reversing valve 612 is controlled to lose power, so that its valve core is reversed, and the hydraulic oil is controlled not to enter the brake hydraulic cylinder 2, so that the brake is closed, ending the heavy-load anchoring operation.

[0049] In an optional embodiment, when a light-load cable-collecting operation is required, after the feedback port 709 senses the load, it controls the second electromagnetic reversing valve 612 to be energized, so that its valve core is reversed, and the hydraulic oil is controlled to enter the brake hydraulic cylinder 2 to open the brake, and the first electronically controlled proportional reversing valve 403 is controlled to obtain an analog electrical signal, so that its valve core is reversed proportionally, and the hydraulic oil is controlled to reach the lifting side control port 4015 of the hydraulic proportional reversing valve 401. After the hydraulic proportional reversing valve 401 obtains the hydraulic oil, its valve core is reversed proportionally, and the hydraulic oil is transported to the lifting port 51 of the hydraulic motor 5 through the lifting oil circuit, so that the hydraulic motor 5 starts working to perform the light-load cable-collecting operation.

[0050] Furthermore, when it is necessary to perform a light-load cable-laying operation, the second electrically-controlled proportional reversing valve 404 is controlled to obtain an analog electrical signal, so that its valve core is reversed proportionally, and the hydraulic oil is controlled to reach the lowering side control port 4016 of the hydraulic proportional reversing valve 401. After the hydraulic proportional reversing valve 401 obtains the hydraulic oil, its valve core is reversed proportionally, so that the hydraulic oil is retained in the lowering port 52 of the hydraulic motor 5 through the lowering oil circuit. When the light-load cable-laying operation is completed, the second electromagnetic reversing valve 612 is controlled to lose power, so that its valve core is reversed, and the hydraulic oil is controlled not to enter the brake hydraulic cylinder 2, so that the brake is closed, thereby ending the light-load cable-laying operation.

[0051] In an optional embodiment, when rapid cable retraction and release operations are required, the first solenoid reversing valve 408 is energized to reverse the direction of its valve core and control the displacement of the displacement control valve to decrease. At the same time, the second solenoid reversing valve 612 is energized to reverse the direction of its valve core and control the hydraulic oil to enter the brake hydraulic cylinder 2 to open the brake and enter the rapid cable retraction and release operating condition.

[0052] When rapid cable reeling is required, the second electromagnetic reversing valve 612 is energized to reverse the direction of its valve core, control the hydraulic oil to enter the brake hydraulic cylinder 2 to open the brake, control the first electrically controlled proportional reversing valve 403 to obtain an analog electrical signal to reverse the direction of its valve core proportionally, control the hydraulic oil to the lifting side control port 4015 of the hydraulic proportional reversing valve 401, and complete the rapid cable reeling operation.

[0053] When it is necessary to perform fast cable release, the second electrically controlled proportional reversing valve 404 is controlled to obtain an analog electrical signal, so that its valve core is switched proportionally, and the hydraulic oil is controlled to flow to the lower control port 4016 of the hydraulic proportional reversing valve 401. After the hydraulic proportional reversing valve 401 obtains the hydraulic oil, its valve core is switched proportionally, so that the hydraulic oil flows through the lower oil circuit to the lower port 52 of the hydraulic motor 5, thereby completing the fast cable release operation.

[0054] When the rapid cable retracting and releasing operation is completed, the first solenoid reversing valve 408 is de-energized to reverse the direction of its valve core and control the displacement of the displacement control valve to the default maximum. At the same time, the second solenoid reversing valve 612 is de-energized to reverse the direction of its valve core and control the hydraulic oil not to enter the brake hydraulic cylinder 2, so that the brake is closed, ending the rapid cable retracting and releasing operation.

[0055] It is easy to understand that those skilled in the art can combine, split, reorganize, etc. the embodiments of the present application to obtain other embodiments based on one or several embodiments provided in the present application, and these embodiments do not exceed the protection scope of the present application.

[0056] The present invention and its implementation methods are described schematically above, and the description is not restrictive. The embodiments shown in the embodiments are only part of the implementation methods of the present invention, and the actual structure is not limited thereto. Therefore, if a person skilled in the art is inspired by the embodiments and designs a structure and an implementation method similar to the technical solution without creativity without departing from the purpose of the invention, they should all fall within the protection scope of the present invention.

Claims

1. A stern windlass (1) hydraulic control system, comprising a stern windlass (1), a brake hydraulic cylinder (2) and a clutch hydraulic cylinder (3), characterized in that: Also includes: A main control valve group (4) having a hydraulic motor (5), wherein the hydraulic motor (5) is used to drive the stern anchor winch (1); A brake clutch control valve group (6) is connected to the brake hydraulic cylinder (2) and the clutch hydraulic cylinder (3); A hydraulic pump station (7) having a first oil supply end (701), a second oil supply end (702) and an oil return end (703), wherein the first oil supply end (701) is used to connect to a main control valve group (4), the second oil supply end (702) is used to connect to a brake clutch control valve group (6), and the oil return end (703) is connected to both the main control valve group (4) and the brake clutch control valve group (6); The main control valve group (4) comprises a hydraulic proportional reversing valve (401), a balancing valve (402) and an electric control component, wherein the electric control component comprises a first electric control proportional reversing valve (403) and a second electric control proportional reversing valve (404) connected in series on both sides of the hydraulic proportional reversing valve (401); The hydraulic proportional reversing valve (401) has a first state and a second state. In the first state, the first proportional electrically controlled reversing valve, the hydraulic proportional reversing valve (401), the balance valve (402) and the hydraulic motor (5) jointly define a lifting circuit. In the second state, the second electrically controlled proportional reversing valve (404), the hydraulic proportional reversing valve (401) and the hydraulic motor (5) jointly define a lowering circuit. A shuttle valve (405) is connected between the lifting circuit and the lowering circuit, and the shuttle valve (405) is connected to the hydraulic pump station (7).

2. The hydraulic control system of the stern windlass (1) according to claim 1, characterized in that: The hydraulic proportional reversing valve (401) has a first port (4011), and the first port (4011) is used to be connected to the first oil supply end (701); The second port (4012) is used to connect to the oil return end (703); A first working port (4013) is used to be connected to the balancing valve (402); the balancing valve (402) has a first connecting port (4021) and a second connecting port (4014); the first connecting port (4021) is connected to the first working port (4013); The second working port (4022) is used to be connected to a hydraulic motor (5); the hydraulic motor (5) has a lifting port (51) and a lowering port (52); the second connecting port (4014) is connected to the lowering port (52).

3. The hydraulic control system of the stern windlass (1) according to claim 2, characterized in that: The shuttle valve (405) is connected to the lifting port (51) and the lowering port (52) respectively; The shuttle valve (405) has a side branch (406), and the side branch (406) is used to receive the hydraulic oil at the lifting port (51) or the lowering port (52). A displacement control valve is correspondingly provided at the hydraulic motor (5), and the side branch (406) is connected to the displacement control valve. The shuttle valve (405) is provided with a first pressure reducing valve (407) and a first electromagnetic reversing valve (408) in sequence along the side branch (406). The first electromagnetic reversing valve (408) is used to transport the hydraulic oil at the first pressure reducing valve (407) to the displacement control valve.

4. The hydraulic control system of the stern windlass (1) according to claim 2, characterized in that: A first safety valve (409) is connected between the first connecting port (4021) and the lifting port (51), and the first safety valve (409) is connected to the oil return end (703).

5. The hydraulic control system of the stern windlass (1) according to claim 1, characterized in that: The main control valve group (4) further comprises a second pressure reducing valve (410), and the second pressure reducing valve (410) has a first access point (411) and a second access point (412) at both ends, the first access point (411) being used to connect to the first oil supply end (701), and the second access point (412) being used to connect to the first electrically controlled proportional reversing valve (403) and the second electrically controlled proportional reversing valve (404).

6. The hydraulic control system of the stern windlass (1) according to claim 1, characterized in that: The hydraulic proportional reversing valve (401) further comprises a lifting side control port (4015) and a lowering side control port (4016); the lifting side control port (4015) is used to be connected to the first electrically controlled proportional reversing valve (403); the first electrically controlled proportional reversing valve (403) is used to provide the lifting side control hydraulic oil pressure to the lifting side control port (4015); the lowering side control port (4016) is used to be connected to the second electrically controlled proportional reversing valve (404); the second electrically controlled proportional reversing valve (404) is used to provide the lowering side control hydraulic oil pressure to the lowering side control port (4016).

7. The hydraulic control system of the stern windlass (1) according to claim 1, characterized in that: The brake clutch valve group (62) comprises a brake valve group (61) and a clutch valve group (62), wherein the brake valve group (61) is used to be connected to the brake hydraulic cylinder (2), and the clutch valve group (62) is used to be connected to the clutch hydraulic cylinder (3); The brake valve group (61) comprises a third pressure reducing valve (611) and a second electromagnetic reversing valve (612) which are connected in sequence. There are multiple third pressure reducing valves (611) which are connected in parallel. One end of the third pressure reducing valve (611) is connected to the second oil supply end (702), and the other end is connected to the second electromagnetic reversing valve (612). The brake hydraulic cylinder (2) is provided with a first oil inlet (21), and the first oil inlet (21) is connected to the second electromagnetic reversing valve (612). The clutch valve group (62) comprises a fourth pressure reducing valve (621), a third electromagnetic reversing valve (622) and an oil saving valve (623) which are connected in sequence. There are a plurality of fourth pressure reducing valves (621) which are connected in parallel. One end of the fourth pressure reducing valve (621) is connected to the second oil supply end (702), and the other end is connected to the third electromagnetic reversing valve (622). A second oil inlet (31) is provided at the clutch hydraulic cylinder (3). One end of the oil saving valve (623) is connected to the second oil inlet valve, and the other end is connected to the third electromagnetic reversing valve (622).

8. The hydraulic control system of the stern windlass (1) according to claim 7, characterized in that: The brake valve assembly (61) further comprises a second safety valve (613) arranged between the second electromagnetic reversing valve (612) and the first oil inlet (21); the clutch valve assembly (62) further comprises a third safety valve (624) arranged between the oil-saving valve (623) and the second oil inlet (31).

9. The hydraulic control system of the stern windlass (1) according to claim 1, characterized in that: The hydraulic pump station (7) comprises an oil tank (704), a motor pump group (705) is provided on one side of the oil tank (704), a pump control valve group (706) is provided at the motor pump group (705), the motor pump group (705) is used to generate high-pressure oil, the motor pump group (705) has an oil supply port (707), a one-way valve (708) is connected to the oil supply port (707), the one-way valve (708) is connected to the first oil supply end (701) and the second oil supply end (702), respectively, a feedback port (709) is provided at the pump control valve group (706), the feedback port (709) is used to connect to the hydraulic motor (5) and the shuttle valve (405), and the pump control valve group (706) is electrically connected to the main control valve group (4).

10. The hydraulic control system of the stern windlass (1) according to claim 9, characterized in that: An oil return port (710) is provided at the oil tank (704), and an oil return filter (711) is provided at the oil return port (710), and the oil return filter (711) is connected to the oil return end (703); a liquid temperature sensor (712) is provided at the top of the oil tank (704), and the liquid temperature sensor (712) is used to measure the temperature of the hydraulic oil in the oil tank (704); a liquid level display (713) is provided on the side wall of the oil tank (704), and the liquid level display (713) is connected to the oil tank (704); an air filter (714) is also provided at the top of the oil tank (704), and the air filter (714) is connected to the oil tank (704).

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