A hydraulic winch system

Abstract

The present invention provides a hydraulic winch system, including an oil tank, a load-sensitive variable pump assembly, an electromagnetic proportional reversing valve, a balancing valve, a metering pump, a first hydraulically controlled reversing valve, a hydraulic motor and a system oil drain pipeline connected to the oil tank, the oil tank, the load-sensitive variable pump assembly, the electromagnetic proportional reversing valve and the high-pressure chamber of the hydraulic motor are connected, the balancing valve is connected to the high-pressure chamber and the electromagnetic proportional reversing valve; the oil tank, the metering pump and the first hydraulically controlled reversing valve are connected, the first hydraulically controlled reversing valve is connected to the high-pressure chamber and the low-pressure chamber; the pipeline between the first hydraulically controlled reversing valve and the low-pressure chamber and the pipeline between the first hydraulically controlled reversing valve and the high-pressure chamber are connected to the system oil drain pipeline. The beneficial effects of the present invention: the hydraulic motor can be exhausted, replenished and exhausted to avoid the hydraulic motor from instantaneously overspeeding and then stalling, thereby avoiding damage to parts of the system.

Description

Technical Field

[0001] The present invention relates to the field of hydraulic technology, and in particular to a hydraulic winch system. Background Art

[0002] Safety, stability and reliability are essential indicators for hydraulic winch systems, such as hydraulically driven winch cranes used in ships, offshore platforms and port terminals. In daily winch control, it is common to hear cavitation sound when the crane is first started after being placed for a long time, and the hydraulic motor may lose speed and be damaged when lowering due to air suction.

[0003] In order to enable the system to be lowered normally, a single oil pressure-controlled reverse balancing valve is usually used to achieve this. This oil pressure control has a prerequisite. When the system is stationary for a long time or stagnates during lowering, the pressure in the pressure chamber between the motor and the balancing valve will disappear due to oil leakage, causing the air dissolved in the oil to precipitate and occupy a part of the closed chamber. When the winch system is lowered for the first time or again, the hydraulic motor starts by braking the drive shaft. It cannot operate on its own in the closed chamber occupied by compressed air. In order to reduce brake wear, the matching brake is generally opened before the balancing valve. When the balancing valve is driven by the control oil in the low-pressure chamber of the hydraulic motor and opens, the brake that brakes the motor drive shaft has already been opened. At this time, the motor will run in the lowering direction under the drag of the heavy object. The first thing compressed by the motor is not oil but air. Due to the high compressibility of air, the motor overspeeds instantly, and then stalls, causing instant damage to internal components. Summary of the invention

[0004] The problem solved by the present invention is how to exhaust the hydraulic motor by replenishing oil and exhausting the hydraulic motor, so as to avoid the hydraulic motor from instantaneously overspeeding and then stalling, thereby avoiding damage to parts of the system.

[0005] To solve the above problems, the present invention provides a hydraulic winch system, including an oil tank, a load-sensitive variable pump assembly, an electromagnetic proportional reversing valve, a balancing valve, a metering pump, a first hydraulically controlled reversing valve, a hydraulic motor and a system oil drain pipeline connected to the oil tank, wherein the oil tank, the load-sensitive variable pump assembly, the electromagnetic proportional reversing valve and the high-pressure chamber of the hydraulic motor are connected, and the balancing valve is connected to both the high-pressure chamber and the electromagnetic proportional reversing valve; the oil tank, the metering pump and the first hydraulically controlled reversing valve are connected, and the first hydraulically controlled reversing valve is connected to both the high-pressure chamber and the low-pressure chamber; the pipeline between the first hydraulically controlled reversing valve and the low-pressure chamber and the pipeline between the first hydraulically controlled reversing valve and the high-pressure chamber are both connected to the system oil drain pipeline.

[0006] In the present technical scheme, the high-pressure chamber and the low-pressure chamber of the hydraulic motor are replenished with oil by a metering pump, and the pipeline between the first hydraulic-controlled reversing valve and the low-pressure chamber of the hydraulic motor and the pipeline between the first hydraulic-controlled reversing valve and the high-pressure chamber are connected to the system oil drain pipeline for exhaust. The high-pressure chamber and the low-pressure chamber can be filled with oil at any time, thereby preventing the hydraulic motor from being sucked into the air or stalling due to compressed air, and further preventing the hydraulic motor from being damaged. Therefore, when the system is started for the first time after being placed for a long time, the above-mentioned oil replenishment and exhaust process can be performed, and then the hydraulic motor can be lifted and lowered to avoid air suction or stalling. The system can also be temporarily shut down to perform air replenishment and exhaust operations to ensure that there is always a certain oil replenishment pressure in the two chambers of the hydraulic motor, thereby avoiding air precipitation in the two chambers of the hydraulic motor, thereby facilitating restarting and ensuring safer operation during multiple starts.

[0007] Further, the electromagnetic proportional reversing valve is connected to the first hydraulically controlled reversing valve. When the first hydraulically controlled reversing valve is in the left position, the electromagnetic proportional reversing valve, the first hydraulically controlled reversing valve and the low-pressure chamber are connected; when the first hydraulically controlled reversing valve is in the right position, the electromagnetic proportional reversing valve, the first hydraulically controlled reversing valve and the low-pressure chamber are connected, and the electromagnetic proportional reversing valve, the first hydraulically controlled reversing valve and the high-pressure chamber are connected.

[0008] Further, the first hydraulically controlled reversing valve includes a left-position oil port and a right-position oil port. When the first hydraulically controlled reversing valve is in the left position, the electromagnetic proportional reversing valve, the left-position oil port and the low-pressure chamber are connected. When the first hydraulically controlled reversing valve is in the right position, the right-position oil port, the first hydraulically controlled reversing valve and the low-pressure chamber are connected, and the right-position oil port, the first hydraulically controlled reversing valve and the high-pressure chamber are connected. The pipeline between the balancing valve and the high-pressure chamber, the pipeline between the left-position oil port and the low-pressure chamber, the pipeline between the right-position oil port and the low-pressure chamber, and the pipeline between the right-position oil port and the high-pressure chamber are all connected to the system oil drain pipeline.

[0009] Furthermore, it also includes a shuttle valve, the electromagnetic proportional reversing valve includes a first working port and a second working port, the first working port is connected with the oil inlet of the shuttle valve, the balance valve, and the high-pressure chamber, the second working port is connected with the oil inlet of the shuttle valve, the control port of the balance valve and the first hydraulically controlled reversing valve, the oil outlet of the shuttle valve is connected with the first hydraulically controlled reversing valve, when the hydraulic oil flows into the first hydraulically controlled reversing valve from the oil outlet of the shuttle valve, the hydraulic oil makes the first hydraulically controlled reversing valve in the left position, so that the second working port, the first hydraulically controlled reversing valve and the low-pressure chamber are connected; when the hydraulic oil flows into the first hydraulically controlled reversing valve from the metering pump, the hydraulic oil makes the first hydraulically controlled reversing valve in the right position.

[0010] Furthermore, it also includes a first overflow valve and a first throttle nozzle, the oil outlet of the shuttle valve is connected to the pipeline between the first hydraulically controlled reversing valve, the first overflow valve and the system oil drain pipeline, and the oil outlet of the shuttle valve is connected to the pipeline between the first hydraulically controlled reversing valve, the first throttle nozzle and the system oil drain pipeline.

[0011] Furthermore, it also includes a pressure compensator, which is located on the pipeline between the load-sensitive variable pump assembly and the electromagnetic proportional reversing valve, and the pipeline between the oil outlet of the shuttle valve and the first hydraulically controlled reversing valve is connected to the pressure compensator.

[0012] Furthermore, it also includes a brake cylinder and a second hydraulically controlled reversing valve, wherein the brake cylinder is used to brake the hydraulic motor, and the oil outlet of the shuttle valve, the second hydraulically controlled reversing valve and the brake cylinder are connected.

[0013] Furthermore, it also includes a manual pump assembly connected to the oil tank, and the manual pump assembly is connected to the first hydraulically controlled reversing valve. When the hydraulic oil flows from the manual pump assembly into the first hydraulically controlled reversing valve, the hydraulic oil puts the first hydraulically controlled reversing valve in the right position, so that the hydraulic oil of the manual pump assembly flows into the high-pressure chamber and the low-pressure chamber through the first hydraulically controlled reversing valve.

[0014] Furthermore, it also includes a throttle valve and a switch valve, the low-pressure chamber, the throttle valve, the switch valve and the high-pressure chamber are connected, and the manual pump assembly is connected to the brake cylinder.

[0015] Furthermore, it also includes a second overflow valve and an electromagnetic reversing valve connected to the second overflow valve, the second overflow valve is connected to the metering pump, and the second overflow valve is connected to the system oil return pipeline, and the electromagnetic reversing valve is connected to the system oil drain pipeline. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is an electrical structure diagram of a hydraulic winch system in an embodiment of the present invention;

[0017] Figure 2 It is a control flow chart of the hydraulic hoisting system during the hydraulic motor lifting operation in an embodiment of the present invention;

[0018] Figure 3 It is a control flow chart of the hydraulic hoisting system during the lowering operation of the hydraulic motor in an embodiment of the present invention;

[0019] Figure 4 It is a control flow chart of the hydraulic hoisting system when the hydraulic motor is replenished with oil and exhausted by a quantitative pump in an embodiment of the present invention;

[0020] Figure 5This is a control flow chart of the hydraulic winch system when the hydraulic motor is replenished with oil and exhausted through a manual pump assembly and the hydraulic motor is urgently released in an embodiment of the present invention.

[0021] Description of reference numerals:

[0022] 1-Oil tank; 1a-First branch pipe; 1b-Second branch pipe; 2-Load-sensitive variable pump assembly; 3-Electromagnetic proportional reversing valve; 4-Balance valve; 5-Dosing pump; 6-First hydraulically controlled reversing valve; 7-System oil drain line; 8-Hydraulic motor; 9-Shuttle valve; 10-First overflow valve; 11-First throttle nozzle; 12-Pressure compensator; 13-Brake cylinder; 14-Second hydraulically controlled reversing valve; 15-Hand pump assembly; 16-Throttle valve; 17-Switch valve; 18-Second overflow valve; 19-Electromagnetic reversing valve; 20-System oil return line; 21-Cooler. DETAILED DESCRIPTION

[0023] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, specific embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0024] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the numbers used in this way can be interchanged where appropriate, so that the embodiments of the present invention described herein can be implemented in an order other than those illustrated or described herein.

[0025] Reference Figure 1-5 As shown, the present invention proposes a hydraulic winch system, including an oil tank 1, a load-sensitive variable pump assembly 2, an electromagnetic proportional reversing valve 3, a balancing valve 4, a metering pump 5, a first hydraulically controlled reversing valve 6, a hydraulic motor 8 and a system oil drain pipeline 7 connected to the oil tank 1, wherein the high-pressure chamber of the oil tank 1, the load-sensitive variable pump assembly 2, the electromagnetic proportional reversing valve 3 and the hydraulic motor 8 are connected, and the balancing valve 4 is connected to both the high-pressure chamber and the electromagnetic proportional reversing valve 3; the oil tank 1, the metering pump 5 and the first hydraulically controlled reversing valve 6 are connected, and the first hydraulically controlled reversing valve 6 is connected to both the high-pressure chamber and the low-pressure chamber; the pipeline between the first hydraulically controlled reversing valve 6 and the low-pressure chamber, the pipeline between the first hydraulically controlled reversing valve 6 and the high-pressure chamber, and the pipeline between the balancing valve 4 and the high-pressure chamber are all connected to the system oil drain pipeline 7.

[0026] In the related art, it is common that when a crane is first started after being placed for a long time, there is air cavitation sound, and when it is lowered, the hydraulic motor is instantly stalled and damaged due to air suction. In order to enable the system to be lowered normally, a single oil pressure control reverse balance valve is usually used to achieve this. This oil pressure control has a prerequisite. When the system is stationary for a long time or stagnates halfway during lowering, the pressure in the pressure chamber between the motor and the balance valve will disappear due to oil leakage, and the air dissolved in the oil will precipitate and occupy a part of the closed chamber. When the winch system is lowered for the first time or again, the hydraulic motor starts to brake the drive shaft through the brake. It cannot operate the closed chamber occupied by compressed air by itself. In order to reduce brake wear, the matching brake is generally opened first before the balance valve. When the balance valve is driven by the control oil of the low-pressure chamber of the hydraulic motor and opens, the brake that brakes the motor drive shaft has already been opened. At this time, the motor will run in the lowering direction under the drag of the heavy object. The motor first compresses air instead of oil. Due to the high compressibility of air, the motor is instantly overspeeded, and then stalled, causing internal components to be instantly damaged.

[0027] In the embodiment of the present invention, the oil tank 1 of the hydraulic hoisting system is connected to the load-sensitive variable pump assembly 2 to output the hydraulic oil for controlling the operation of the hydraulic motor 8, such as the hydraulic oil flowing into the high-pressure chamber of the hydraulic motor 8 to lift the hoisting system, and the hydraulic oil flowing into the low-pressure chamber of the hydraulic motor 8 to lower the hoisting system, refer to Figure 1 The high-pressure chamber of the hydraulic motor 8 is the motor A chamber in the figure, and the low-pressure chamber is the motor B chamber in the figure. The load-sensitive variable pump assembly 2 may include a load-sensitive variable pump P1 and a control valve that controls the load-sensitive variable pump. The load-sensitive variable pump is controlled by the control valve. The load-sensitive variable pump P1 is powered by the engine D1. In this embodiment, the hydraulic oil output by the load-sensitive variable pump assembly 2 can flow into the P port of the electromagnetic proportional reversing valve 3 through the one-way valve DX1, the a port of the pressure compensator 12, and the b port of the pressure compensator 12 in sequence. The p port of the electromagnetic proportional reversing valve 3 is the oil inlet of the electromagnetic proportional reversing valve 3, and then through the control of the electromagnetic proportional reversing valve 3, it is led out from the working oil port a or the working oil port b to supply oil to the hydraulic motor 8. The one-way valve DX1 is set to avoid hydraulic oil backflow.

[0028] Among them, a balancing valve 4 is provided, and the balancing valve 4 can be selected as a reverse balancing valve. The balancing valve 4 is connected to the electromagnetic proportional reversing valve 3 and the hydraulic motor 8 to balance the hydraulic oil pressure difference. Figure 1In an optional embodiment of the present embodiment, a one-way pipeline is included, on which a one-way valve DX2 is provided, and the electromagnetic proportional reversing valve 3 is connected to the high-pressure chamber of the hydraulic motor 8 through the one-way pipeline, so that the hydraulic oil can flow from the electromagnetic proportional reversing valve 3 through the flow path to the high-pressure chamber of the hydraulic motor 8. The balancing valve 4 is connected in parallel with the one-way pipeline and is connected to the electromagnetic proportional reversing valve 3 and the high-pressure chamber, so that the hydraulic oil flowing out of the hydraulic motor 8 can enter the b port of the balancing valve 4, and then flow out from the a port of the balancing valve 4, and then flow to the electromagnetic proportional reversing valve 3, so as to return the oil through the return oil port t of the electromagnetic proportional reversing valve 3.

[0029] The hydraulic winch system also includes a metering pump 5, which is connected to the oil tank 1. The metering pump 5 is powered by the engine D1. In this embodiment, the hydraulic oil output by the metering pump 5 flows to the first hydraulically controlled reversing valve 6 through the one-way valve DX5, the a port of the pressure reducing valve JY2, the b port of the pressure reducing valve JY2, and the one-way valve DX6 in sequence. When the hydraulic oil is introduced into the first hydraulically controlled reversing valve 6, the metering pump 5 is connected to the hydraulic motor 8, that is, the hydraulic oil flows into the high-pressure chamber and the low-pressure chamber of the hydraulic motor 8 for oil replenishment after passing through the first hydraulically controlled reversing valve 6. Specifically, Figure 1 In the embodiment, the first hydraulically controlled reversing valve 6 is connected to the high-pressure chamber and the low-pressure chamber through pipelines at the oil port d after the oil supply from the metering pump 5 is turned on, so as to form the hydraulic oil output by the first hydraulically controlled reversing valve 6 to replenish the hydraulic motor 8, wherein a one-way valve DX3 is arranged on the pipeline connected to the high-pressure chamber, and a one-way valve DX4 is arranged on the pipeline connected to the low-pressure chamber to avoid backflow.

[0030] The port c of the pressure reducing valve JY2 is connected to the system oil drain line 7 so that the oil drained from the pressure reducing valve JY2 can flow back to the oil tank 1 for processing.

[0031] Among them, the pipeline between the first hydraulically controlled reversing valve 6 and the low-pressure chamber, and the pipeline between the first hydraulically controlled reversing valve 6 and the high-pressure chamber are both connected to the system oil drain pipeline 7. Specifically, refer to Figure 1 The pipeline between the one-way valve DX4 and the low-pressure chamber is connected to the system oil drain pipeline 7 through the first branch pipe 1a provided with a throttle nozzle JZ2, and the pipeline between the one-way valve DX3 and the high-pressure chamber is connected to the system oil drain pipeline 7 through the second branch pipe 1b provided with a throttle nozzle JZ1, so as to realize the exhaust of the high-pressure chamber and the low-pressure chamber of the hydraulic motor 8, refer to the attached Figure 1 The first dotted line in the attached drawing connects the oil tank 1, which refers to the system oil drain pipeline 7, and the pipeline connecting the components in the system to the system oil drain pipeline 7 for oil drain and exhaust. Figure 1 The second dashed line frame shows the manual pump assembly 15 and the frame shows the load sensing variable displacement pump assembly 2.

[0032] In summary, the system replenishes oil and exhausts the high-pressure chamber and the low-pressure chamber of the hydraulic motor 8, so that the high-pressure chamber and the low-pressure chamber are filled with oil at any time, thereby preventing the hydraulic motor 8 from being sucked into air or stalling due to compressed air, and further preventing the hydraulic motor 8 from being damaged. Therefore, when the system is started for the first time after being placed for a long time, the above-mentioned oil replenishment and exhaust process can be performed, and then the hydraulic motor 8 can be lifted and lowered to avoid air suction or stalling. When the system is temporarily shut down and the air replenishment and exhaust operations are performed, it can be ensured that there is always a certain oil replenishment pressure in the two chambers of the hydraulic motor 8, thereby avoiding air precipitation in the two chambers of the hydraulic motor 8, thereby facilitating restarting and ensuring startup safety during multiple starts and operations.

[0033] In an optional embodiment of the present invention, the electromagnetic proportional reversing valve 3 is connected to the first hydraulically controlled reversing valve 6. When the first hydraulically controlled reversing valve 6 is in the left position, the electromagnetic proportional reversing valve 3, the first hydraulically controlled reversing valve 6 and the low-pressure chamber are connected; when the first hydraulically controlled reversing valve 6 is in the right position, the electromagnetic proportional reversing valve 3, the first hydraulically controlled reversing valve 6 and the low-pressure chamber are connected, and the electromagnetic proportional reversing valve 3, the first hydraulically controlled reversing valve 6 and the high-pressure chamber are connected.

[0034] In this embodiment, the left position and the right position of the first hydraulically controlled reversing valve 6 refer to the passage switching performed by the first hydraulically controlled reversing valve 6 when receiving hydraulic oil from different flow paths, Figure 1-4 The first hydraulically controlled reversing valve 6 includes oil ports a, b, c, d, e, f, and g, among which switching to the left position indicates that the oil ports a and c are connected, and switching to the right position indicates that the oil ports b and d are connected. When hydraulic oil is introduced into the oil port e, the hydraulic oil makes the first hydraulically controlled reversing valve 6 in the left position and connected. When hydraulic oil is introduced into the oil port f, the hydraulic oil makes the first hydraulically controlled reversing valve 6 in the right position and connected, thereby realizing the specific hydraulically controlled reversing of the first hydraulically controlled reversing valve 6. In this embodiment, the oil port f is connected with the metering pump 5 through a pipeline. When the metering pump 5 performs the oil replenishment operation, the hydraulic oil flows out from the one-way valve DX6 and is guided into the oil port f to realize the right position conduction. In this way, the hydraulic oil flowing out of the one-way valve DX6 can flow into the oil port b of the first hydraulically controlled reversing valve 6 and flow out from the oil port d. The hydraulic oil flowing out of the oil port d is connected to the high-pressure chamber and the low-pressure chamber for oil replenishment. The oil port g of the first hydraulically controlled reversing valve 6 is connected to the system oil drain pipeline 7 to drain the hydraulic oil flowing out of the first hydraulically controlled reversing valve 6.

[0035] Reference Figure 1-3, wherein, when the first hydraulically controlled reversing valve 6 is in the left position, the working port b of the electromagnetic proportional reversing valve 3, the oil port a of the first hydraulically controlled reversing valve 6, the oil port c of the first hydraulically controlled reversing valve 6 and the low-pressure chamber are connected, that is, the hydraulic oil output by the load-sensitive variable pump assembly 2 can be input into the low-pressure chamber through the regulation of the electromagnetic proportional reversing valve 3 to perform the lowering operation of the hydraulic motor 8. Correspondingly, when the electromagnetic proportional reversing valve 3 introduces the hydraulic oil into the high-pressure chamber to perform the lifting operation of the hydraulic motor 8, the hydraulic oil flowing out of the low-pressure chamber can flow back to the working port b of the electromagnetic proportional reversing valve 3 through the oil port c of the first hydraulically controlled reversing valve 6 and the oil port a of the first hydraulically controlled reversing valve 6, and flow to the system oil return pipeline 20 through the oil return port t of the electromagnetic proportional reversing valve 3, and finally flow back to the oil tank 1 to complete the hydraulic oil circulation.

[0036] In an optional embodiment of the present invention, the first hydraulically controlled reversing valve 6 includes a left-position oil port and a right-position oil port. When the first hydraulically controlled reversing valve 6 is in the left position, the electromagnetic proportional reversing valve 3, the left-position oil port and the low-pressure chamber are connected; when the first hydraulically controlled reversing valve 6 is in the right position, the right-position oil port, the first hydraulically controlled reversing valve 6 and the low-pressure chamber are connected, and the right-position oil port, the first hydraulically controlled reversing valve 6 and the high-pressure chamber are connected; the pipeline between the balancing valve 4 and the high-pressure chamber, the pipeline between the left-position oil port and the low-pressure chamber, the pipeline between the right-position oil port and the low-pressure chamber, and the pipeline between the right-position oil port and the high-pressure chamber are all connected to the system oil drain pipeline 7.

[0037] Reference Figure 1 , the left oil port is the oil port c of the first hydraulically controlled reversing valve 6, and the right oil port is the oil port d of the first hydraulically controlled reversing valve 6. When the hydraulic motor 8 is controlled to be lowered, the first hydraulically controlled reversing valve 6 is controlled to be in the left position, wherein the pipeline between the left oil port and the low-pressure chamber is connected to the system oil drain pipeline 7. In this embodiment, it is connected to the system oil drain pipeline 7 through the first branch pipe 1a and the second branch pipe 1b for exhaust. When the metering pump 5 is controlled to replenish oil, the first hydraulically controlled reversing valve 6 is in the right position. At this time, the right oil port replenishes oil in the high-pressure chamber and the low-pressure chamber, and the first branch pipe 1a and the second branch pipe 1b simultaneously exhaust the oil at this time.

[0038] The electromagnetic proportional reversing valve 3 regulates the hydraulic oil discharged from the load-sensitive variable pump assembly 2 to introduce the hydraulic oil into the high-pressure chamber to lift the hydraulic motor 8 or introduce the hydraulic oil into the first hydraulically controlled reversing valve 6 in the left position state and then into the low-pressure chamber to lower the hydraulic motor 8, such as Figure 1-3As shown, in this embodiment, the electromagnetic proportional reversing valve 3 includes an oil inlet p, an oil return port t, a working port a and a working port b. The oil inlet p is communicated with the load-sensitive variable pump assembly 2, and the oil return port t is connected to the system oil return pipeline 20 to return the oil when the system is running the hydraulic oil circulation. The working port a and the working port b are used to supply oil to the high-pressure chamber and the low-pressure chamber respectively, and, for the working port a, when the hydraulic motor 8 is lifting operation, the high-pressure chamber enters the oil and the low-pressure chamber discharges the oil, and the hydraulic oil flowing out of the low-pressure chamber flows to the working port b of the electromagnetic proportional reversing valve 3 to return the oil from the oil return port t of the electromagnetic proportional reversing valve 3 to the oil tank 1 to circulate the hydraulic oil. Corresponding to this embodiment, the low-pressure chamber discharges the oil. The oil passes through the oil port c of the first hydraulically controlled reversing valve 6, the working port b of the electromagnetic proportional reversing valve 3, the return oil port t of the electromagnetic proportional reversing valve 3, and the system return oil pipeline 20 in sequence, and then flows into the oil tank 1; for the working port b, when the hydraulic motor 8 is lowered, oil enters the low-pressure chamber and oil discharges from the high-pressure chamber, and the hydraulic oil flowing out of the high-pressure chamber flows to the working port a of the electromagnetic proportional reversing valve 3, so as to return the oil to the oil tank 1 from the working port a of the electromagnetic proportional reversing valve 3, so as to circulate the hydraulic oil. Corresponding to this embodiment, the oil out of the high-pressure chamber passes through the balance valve 4, the working port a of the electromagnetic proportional reversing valve 3, the return oil port t of the electromagnetic proportional reversing valve 3, and the system return oil pipeline 20 in sequence, and then flows into the oil tank 1.

[0039] The pipeline between the balancing valve 4 and the high-pressure chamber is connected to the system oil drain pipeline 7. Figure 1 In the embodiment, the second branch pipe 1b is also connected with the pipeline between the balancing valve 4 and the high-pressure chamber to drain oil and exhaust gas. In addition, the pipeline between the left oil port and the low-pressure chamber is connected with the first branch pipe 1a to drain oil and exhaust gas. When the corresponding hydraulic motor 8 is working, the oil entering between the balancing valve 4 and the high-pressure chamber of the hydraulic motor 8 always keeps a certain amount of exhaust gas for the high-pressure chamber of the hydraulic motor 8 through the second branch pipe 1b; the oil entering between the left oil port c of the first hydraulically controlled reversing valve 6 and the low-pressure chamber of the hydraulic motor 8 always keeps a certain amount of exhaust gas for the low-pressure chamber of the hydraulic motor 8 through the first branch pipe 1a. The two always keep the air mixed in the chambers on both sides of the hydraulic motor 8 excluded through exhaust gas, thereby realizing the smooth operation of the hydraulic motor 8 and reducing the possibility of internal cavitation.

[0040] In an optional embodiment of the present invention, a shuttle valve 9 is further included, and the electromagnetic proportional reversing valve 3 includes a first working port and a second working port, the first working port is connected to the oil inlet of the shuttle valve 9, the balance valve 4, and the high-pressure chamber, the second working port is connected to the oil inlet of the shuttle valve 9, the control port of the balance valve 4 and the first hydraulically controlled reversing valve 6, and the oil outlet of the shuttle valve 9 is connected to the first hydraulically controlled reversing valve 6; when the hydraulic oil flows from the oil outlet of the shuttle valve 9 into the first hydraulically controlled reversing valve 6, the hydraulic oil puts the first hydraulically controlled reversing valve 6 in the left position, so that the second working port, the first hydraulically controlled reversing valve 6 and the low-pressure chamber are connected, and when the hydraulic oil flows from the metering pump 5 into the first hydraulically controlled reversing valve 6, the hydraulic oil puts the first hydraulically controlled reversing valve 6 in the right position.

[0041] Reference Figure 1 In this embodiment, a shuttle valve 9 is provided to adjust the oil circuit, wherein the first working port of the electromagnetic proportional reversing valve 3 is the working port a, and the second working port is the working port b. The shuttle valve 9 generally includes a plurality of oil inlets and oil outlets, so that when the hydraulic oil is introduced into the oil inlet, the oil outlet discharges oil and the flow direction of the hydraulic oil is adjusted. In this embodiment, the shuttle valve 9 specifically includes a shuttle valve oil inlet a, a shuttle valve oil inlet b, a shuttle valve oil outlet c and a shuttle valve oil outlet d, wherein the first working port is connected with the balance valve 4 and the high-pressure chamber, that is, the electromagnetic proportional reversing valve 3 is adjusted so that when the first working port discharges oil, the hydraulic oil flows into the high-pressure chamber for lifting operation, at which time the second working port does not discharge oil and can be used for oil return of the low-pressure chamber, at which time the oil inlet a of the shuttle valve 9 is connected with the first working port, and part of the hydraulic oil flowing out of the first working port flows into the oil inlet a, and the oil outlet c of the shuttle valve 9 is connected with the oil port e of the first hydraulically controlled reversing valve 6, so that the hydraulic oil can be introduced into the oil port e so that the first hydraulically controlled reversing valve 6 is in the left position. position, so that the oil port c and the oil port a of the first hydraulically controlled reversing valve are connected, so that the hydraulic oil flowing out of the low-pressure chamber can flow to the oil port a through the oil port c, and then flow into the second working port of the electromagnetic proportional reversing valve 3 for oil return circulation; the second working port is connected with the oil inlet b of the shuttle valve 9 and the first hydraulically controlled reversing valve 6. Specifically, the second working port is connected with the oil port a of the first hydraulically controlled reversing valve 6, so that when the hydraulic motor 8 is lowered, the electromagnetic proportional reversing valve 3 is adjusted to make the second working port discharge oil. At this time, the hydraulic oil flowing out of the second working port flows into the oil inlet b of the shuttle valve 9, the oil outlet c of the shuttle valve 9, and the oil port e of the first hydraulically controlled reversing valve 6 in sequence, so that the first hydraulically controlled reversing valve 6 is in the left position, so that the oil port c and the oil port a of the first hydraulically controlled reversing valve are connected, and the hydraulic oil flowing out of the second working port can flow to the oil port c through the oil port a, and then flow into the low-pressure chamber for lowering operation, and the second working port is also connected to the control port of the balance valve 4, that is, Figure 1The C port of the middle balancing valve 4, the hydraulic oil flowing out of the second working port can control the balancing valve 4 to open the opening corresponding to the hydraulic oil pressure, realize the sequential conduction of the high-pressure chamber, the balancing valve 4, and the first working port, so as to perform the return oil circulation during the lowering operation, thereby making the control of the cylinder lifting system more reasonable and convenient, and the system structure simpler.

[0042] In an optional embodiment of the present invention, it also includes a first overflow valve 10 and a first throttle nozzle 11, the oil outlet of the shuttle valve 9 is connected to the pipeline between the first hydraulically controlled reversing valve 6, the first overflow valve 10 and the system oil drain pipeline 7, and the oil outlet of the shuttle valve 9 is connected to the pipeline between the first hydraulically controlled reversing valve 6, the first throttle nozzle 11 and the system oil drain pipeline 7.

[0043] Specifically, refer to Figure 1 In the embodiment, the pipeline between the oil outlet c of the shuttle valve 9 and the oil outlet e of the first hydraulically controlled reversing valve 6 is connected to the first relief valve 10 and the first throttle nozzle 11, and further connected to the system oil drain pipeline 7. The first relief valve 10 is also connected to the oil outlet e of the first hydraulically controlled reversing valve 6. Figure 1 In YL4, the first throttle nozzle 11 is Figure 1 In JZ3, multiple throttling nozzles can be arranged on the pipeline between the oil outlet c and the oil port e of the first hydraulically controlled reversing valve 6 and the system oil drain pipeline 7, namely JZ3 and JZ4 arranged in series in the figure, to facilitate adjustment. The oil outlet c of the shuttle valve 9 is connected with the oil port e of the first hydraulically controlled reversing valve, the first throttling nozzle 11 and the system oil drain pipeline 7, and then connected with the system oil drain pipeline 7, so that the hydraulic oil flowing out through the oil port c of the shuttle valve 9 simultaneously enters the first overflow valve 10 and performs an oil drain circulation, which is used for oil unloading when the load sensitive pressure is higher than the set value to ensure that the motor driving the load sensitive variable pump assembly 2 is not overloaded; the hydraulic oil flowing out through the oil port c of the shuttle valve 9 enters the first throttling nozzle 1 and performs a reflux circulation, realizing the oil pressure peak filtering existing during system operation, maintaining the pressure of the control oil basically stable, and realizing the basically stable flow output of the load sensitive variable pump assembly 2. The system oil drain pipeline 7 is provided with a one-way valve DX11 and a filter LQ2 in series in order to prevent the hydraulic oil from flowing in reverse and filter the hydraulic oil.

[0044] In an optional embodiment of the present invention, a pressure compensator 12 is further included, and the pressure compensator 12 is located on the pipeline between the load-sensitive variable pump assembly 2 and the electromagnetic proportional reversing valve 3, and the oil outlet of the shuttle valve 9 is connected to the pipeline between the first hydraulically controlled reversing valve 6 and the pressure compensator 12.

[0045] In this embodiment, the pressure compensator 12 is located on the pipeline between the load-sensitive variable pump assembly 2 and the electromagnetic proportional reversing valve 3, so that the hydraulic oil output by the load-sensitive variable pump assembly 2 enters the port a of the pressure compensator 12 and flows out from the port b to flow to the working port P of the electromagnetic proportional reversing valve 3. The hydraulic oil pressure is adjusted by the pressure compensator 12, and the oil flowing out of the oil outlet c of the shuttle valve 9 also enters the pressure compensator 12, specifically, flows into the port c of the pressure compensator 12, so as to ensure that the pressure difference between the outlet of the load-sensitive variable pump assembly 2 and the working port of the electromagnetic proportional reversing valve 3 is constant, thereby achieving a stable oil flow rate entering the high-pressure chamber or low-pressure chamber of the hydraulic motor 8.

[0046] In an optional embodiment of the present invention, a brake cylinder 13 and a second hydraulically controlled reversing valve 14 are further included. The brake cylinder 13 is used to brake the hydraulic motor 8, and the oil outlet of the shuttle valve 9, the second hydraulically controlled reversing valve 14 and the brake cylinder 13 are connected.

[0047] In this embodiment, when hydraulic oil flows out of the oil outlet d of the shuttle valve 9, the hydraulic oil flows to the second hydraulically controlled reversing valve 14 to turn on the second hydraulically controlled reversing valve 14, and finally the hydraulic oil flowing out of the second hydraulically controlled reversing valve 14 enters the brake cylinder 13 to open the brake cylinder 13 and apply the brake, thereby realizing a smooth lifting or lowering action of the hydraulic winch system.

[0048] Specifically, the second hydraulically controlled reversing valve 14 includes an oil port p, an oil port c, an oil port a, an oil port t, and an oil port b. Normally, the oil port a and the oil port t are connected, and the oil port t is an oil return port. The hydraulic oil flowing out of the brake cylinder 13 flows to the oil port t through the oil port a. The oil port t is connected to the system oil drain line 7 to process the hydraulic oil. The oil port b is an oil drain hole and is also connected to the system oil drain line 7 for hydraulic oil processing. Figure 1 The oil outlet d of the shuttle valve 9 passes through the pipeline pressure reducing valve JY4, and the pressure reducing valve JY4 connects the oil port p and the oil port c. After the hydraulic oil flows out of the oil outlet d, the hydraulic oil enters the pressure reducing valve JY4 through the a port of the pressure reducing valve JY4 for pressure regulation. The hydraulic oil flows out of the b port of the pressure reducing valve JY4 and is introduced into the oil port c of the second hydraulically controlled reversing valve 14, realizing the conduction between the oil port p and the oil port a in the second hydraulically controlled reversing valve 14, thereby realizing the hydraulically controlled reversing of the second hydraulically controlled reversing valve 14. The hydraulic oil flows out of the b port of the pressure reducing valve JY4 and flows into the oil port p of the second hydraulically controlled reversing valve 14 at the same time, and flows out from the oil port a. The hydraulic oil flowing out from the oil port a flows through the switch valve KG2, and then passes through the throttle nozzle JZ3 and the one-way valve DX10 connected in parallel with the throttle nozzle JZ3, and finally merges and flows to the brake cylinder 13 to drive and control the brake cylinder 13. The switch valve KG2 can control the flow of hydraulic oil from the oil port a of the second hydraulically controlled reversing valve 14 to the throttle nozzle JZ3 and the one-way valve DX10, and prevent the hydraulic oil from flowing back into the second hydraulically controlled reversing valve 14 when closed.

[0049] The port c of the pressure reducing valve JY4 is connected to the system oil drain pipeline 7, so that the oil drained from the pressure reducing valve JY4 can flow back to the oil tank 1 for treatment.

[0050] Reference Figure 1 and 5 In an optional embodiment of the present invention, it also includes a manual pump assembly 15 connected to the oil tank 1, and the manual pump assembly 15 is connected to the first hydraulically controlled reversing valve 6. When the hydraulic oil flows from the manual pump assembly 15 into the first hydraulically controlled reversing valve 6, the hydraulic oil puts the first hydraulically controlled reversing valve 6 in the right position, so that the hydraulic oil of the manual pump assembly 15 flows into the high-pressure chamber and the low-pressure chamber through the first hydraulically controlled reversing valve 6.

[0051] In the related art, when the hydraulic winch system is performing an emergency release such as in the event of a power outage, because it does not have the oil replenishment and exhaust functions for emergency lowering, the operation of the hydraulic motor causes the oil in the original cavity to gradually decrease due to leakage, eventually causing the hydraulic motor to suck air and stall, thereby damaging the hydraulic motor. Furthermore, if the hydraulic winch is lowered continuously for a long time, the housing of the hydraulic motor will heat up and may instantly suck air and stall and be damaged.

[0052] In this embodiment, the manual pump assembly 15 is connected to the oil tank 1, so that when the system needs to be urgently lowered, the manual pump assembly 15 will guide the hydraulic oil of the oil tank 1, and the hydraulic oil passes through the one-way valve DX8, the a port of the pressure reducing valve JY3, the b port of the pressure reducing valve JY3, and the one-way valve DX9 in sequence, and then flows into the first hydraulically controlled reversing valve 6, specifically, into the oil port f and the oil port b of the first hydraulically controlled reversing valve 6, so that the first hydraulically controlled reversing valve 6 is in the right position, and then, the hydraulic oil flowing out of the manual pump assembly 15 can also flow into the high-pressure chamber and the low-pressure chamber through the first hydraulically controlled reversing valve 6 to replenish oil, and in the process of replenishing oil, according to the above-mentioned exhaust pipeline, exhaust can also be performed, thereby ensuring that the high-pressure chamber and the low-pressure chamber of the hydraulic motor 8 are filled with oil, and there is no suction or stalling due to compressed air, so as to facilitate the emergency release of the system.

[0053] The pipeline between the manual pump assembly 15 and the oil tank 1 is provided with a switch valve KG4 to control the switch of the oil circuit; the manual pump assembly 15 includes a manual pump P3 to output the hydraulic oil, the manual pump P3 is connected to the overflow valve YL5, and the pressure oil is exported through the control of the overflow valve YL5, and a pressure gauge YB1 is provided to detect the pressure value of the pressure oil output by the manual pump P3, so as to facilitate the control of the system according to the pressure value.

[0054] The port c of the pressure reducing valve JY3 is connected to the system oil drain pipeline 7, so that the oil drained from the pressure reducing valve JY3 can flow back to the oil tank 1 for treatment.

[0055] Reference Figure 1and 5 In an optional embodiment of the present invention, it also includes a throttle valve 16 and a switch valve 17, the low-pressure chamber, the throttle valve 16, the switch valve 17 and the high-pressure chamber are connected, and the manual pump assembly 15 is connected to the brake cylinder 13.

[0056] In this embodiment, the manual pump assembly 15 is connected to the brake cylinder 13, so that the brake cylinder 13 can be supplied with oil to start the brake cylinder 13 to brake and ensure smooth emergency release. Specifically, the hydraulic oil discharged by the manual pump assembly 15 passes through the one-way valve DX8, the switch valve KG3, the throttle nozzle JL2 and the one-way valve DX10 connected in parallel with the throttle nozzle JL2, and the brake cylinder 13 in turn to perform the braking operation. The switch valve KG3 in the oil circuit is usually closed and is turned on during emergency release. In the above embodiment, the switch valve KG2 connected to the second hydraulically controlled reversing valve 14 can be closed during emergency release to prevent the pressure oil output by the manual pump assembly 15 from flowing back to the second hydraulically controlled reversing valve 14. The low-pressure chamber, the throttle valve 16, the switch valve 17 and the high-pressure chamber are connected, and the throttle valve 16 is Figure 1 Middle throttle valve JY1, switch valve 17 Figure 1 The middle switch valve KG1 allows the low-pressure chamber and the high-pressure chamber to be directly connected in an emergency, thereby performing emergency release. The throttle valve 16 can directly control the emergency lowering speed by controlling the conduction of the hydraulic oil between the low-pressure chamber and the high-pressure chamber. For example, during emergency release, the pressure of the pressure gauge YB1 can be observed. When the pressure of the pressure gauge YB1 is lower than a set value, the throttle valve 16 can be closed to ensure the safety and controllability of the emergency lowering process and avoid the hydraulic motor 8 from stalling due to air suction.

[0057] In an optional embodiment of the present invention, it also includes a second overflow valve 18 and an electromagnetic reversing valve 19 connected to the second overflow valve 18, the second overflow valve 18 is connected to the metering pump 5, and the second overflow valve 18 is connected to the system oil return pipeline 20, and the electromagnetic reversing valve 19 is connected to the system oil drain pipeline 7.

[0058] Reference Figure 1 As shown, in this embodiment, the second overflow valve 18 and the electromagnetic reversing valve 19 are used to control the quantitative pump 5 to output the hydraulic oil with a relatively high pressure. Figure 1In the second overflow valve YL2, under normal circumstances, the metering pump 5 is connected to the engine, and the engine needs to achieve low-power non-load starting. During non-load starting, the electromagnetic reversing valve 19 does not work, and the metering pump 5 outputs the pressure oil and flows out to the a port of the second overflow valve 18 through the one-way valve DX5. The oil flows to the system return oil pipeline 20 through the b port of the second overflow valve 18 to return the system oil, so as to ensure the completion of the non-load starting. The oil of the metering pump 5 flows at a relatively low pressure. After the non-load starting is completed, it passes through the set electromagnetic reversing valve 19 and is connected to the second overflow valve 18. Specifically, the b port of the electromagnetic reversing valve 19 is connected to the c port of the second overflow valve 18. The electromagnetic reversing valve 19 is connected to the c port of the second overflow valve 18. The t port and the a port of the valve 19 are also connected to the system oil drain pipeline 7 for oil draining. By controlling the electromagnetic reversing valve 19, the oil of the second relief valve 18 can be prevented from flowing out. Specifically, the electromagnetic control coil corresponding to the electromagnetic reversing valve 19 is energized under the control of the electrical program, and the b port of the electromagnetic reversing valve 19 is disconnected from its a port and t port, and the oil of the c port of the second relief valve 18 cannot flow out, thereby realizing the loading of the second relief valve 18. At this time, the second relief valve 18 can enable the metering pump 5 to output pressure oil with a relatively high pressure. Therefore, through the second relief valve 18 and the electromagnetic reversing valve 19, the metering pump 5 can be reasonably started and controlled, so that the starting oil output of the metering pump 5 is smoother.

[0059] The system return oil pipeline 20 is connected to the oil tank 1 to connect the oil ports of various components in the system for oil return. The system return oil pipeline 20 can be sequentially provided with a one-way valve DX7 to prevent oil reverse reflux, a filter LQ1 to filter the hydraulic oil, and a cooler 21 to cool the hydraulic oil, so as to avoid excessive temperature rise during the hydraulic oil circulation, thereby avoiding situations such as deterioration of the hydraulic oil, and facilitating long-term use of the system.

[0060] In this embodiment, the hydraulic oil flowing out of the return oil port t of the electromagnetic proportional reversing valve 3, the hydraulic oil output by the metering pump 5 when starting the oil replenishment, and the hydraulic oil output by the manual pump assembly 15 when emergency release and replenishment are performed, etc., can all be returned to the oil tank 1 through the system return oil pipeline 20 for oil return, thereby increasing the oil flowing into the cooler 21, and finally achieving a better exchange of hot and cold oils, which is beneficial to the long-term use of the system. Among them, an overflow valve YL3 can be set on the corresponding pipeline for oil return to facilitate oil return. Specifically, refer to Figure 1The one-way valve DX7 of the system oil return pipeline 20 is connected to the oil return port t of the electromagnetic proportional reversing valve 3 through a pipeline to return oil during the lifting or lowering operation of the hydraulic motor 8; the one-way valve DX7 of the system oil return pipeline 20 is connected to the overflow valve YL3 through a pipeline, and the overflow valve YL3 is connected to the pipeline between the one-way valve DX6 and the first hydraulically controlled reversing valve 6 through a pipeline to communicate with the metering pump 5, thereby returning oil from the metering pump 5; the overflow valve YL3 is connected to the one-way valve DX9 through a pipeline to communicate with the manual pump assembly 15, thereby returning oil from the manual pump assembly 15.

[0061] The load-sensitive variable pump assembly 2 includes a pilot control oil port x, and a pipeline between the oil outlet c of the shuttle valve 9 and the oil port e of the first hydraulically controlled reversing valve 6 is connected to the pilot control oil port x. When the hydraulic winch system needs to be shut down, the electromagnetic proportional reversing valve 3 can be powered off by controlling the electromagnetic proportional reversing valve 3, and the electromagnetic proportional reversing valve 3 returns to the middle position. At this time, no oil flows out of the working port of the electromagnetic proportional reversing valve 3, but can only flow out from the return oil port t after the oil enters. At this time, the pressure control oil flowing out of the oil outlet c of the shuttle valve 9 in the system disappears, and the pilot pressure control oil entering the pilot control oil port x of the load-sensitive variable pump assembly 2 disappears, and the displacement swing angle of the load-sensitive variable pump assembly 2 becomes zero, causing the system to stop supplying pressure oil, thereby facilitating the control of the system stop.

[0062] In an optional embodiment of the present invention, it also includes a liquid level sensor YW, a heater HT, a liquid level gauge YB, an air filter TQ and an oil drain switch KG5, wherein the liquid level sensor YW is used to detect the liquid level of the hydraulic oil in the oil tank 1 and send a corresponding liquid level signal, the heater HT is used to heat the hydraulic oil in the oil tank 1, the air filter TQ is used to filter the air entering the oil tank 1, the oil drain switch KG5 is used to export the hydraulic oil in the oil tank 1, and the liquid level gauge YB is used to indicate the liquid level of the hydraulic oil in the oil tank 1, so as to facilitate the control of the hydraulic oil in the oil tank 1.

[0063] Although the disclosure is disclosed as above, the protection scope of the disclosure is not limited thereto. Those skilled in the art may make various changes and modifications without departing from the spirit and scope of the disclosure, and these changes and modifications will fall within the protection scope of the present invention.

Claims

1. A hydraulic winch system, characterized in that: The invention comprises an oil tank (1), a load-sensitive variable pump assembly (2), an electromagnetic proportional reversing valve (3), a balancing valve (4), a metering pump (5), a first hydraulically controlled reversing valve (6), a hydraulic motor (8) and a system oil drain pipeline (7) connected to the oil tank (1); the oil tank (1), the load-sensitive variable pump assembly (2), the electromagnetic proportional reversing valve (3) and a high-pressure chamber of the hydraulic motor (8) are connected; the balancing valve (4) is connected to both the high-pressure chamber and the electromagnetic proportional reversing valve (3); the oil tank (1), the metering pump (5) and the first hydraulically controlled reversing valve (6) are connected; the first hydraulically controlled reversing valve (6) is connected to both the high-pressure chamber and the low-pressure chamber; the pipeline between the first hydraulically controlled reversing valve (6) and the low-pressure chamber and the pipeline between the first hydraulically controlled reversing valve (6) and the high-pressure chamber are both connected to the system oil drain pipeline (7); The electromagnetic proportional reversing valve (3) is connected to the first hydraulically controlled reversing valve (6); when the first hydraulically controlled reversing valve (6) is in the left position, the electromagnetic proportional reversing valve (3), the first hydraulically controlled reversing valve (6) and the low-pressure chamber are connected; when the first hydraulically controlled reversing valve (6) is in the right position, the electromagnetic proportional reversing valve (3), the first hydraulically controlled reversing valve (6) and the low-pressure chamber are connected, and the electromagnetic proportional reversing valve (3), the first hydraulically controlled reversing valve (6) and the high-pressure chamber are connected; It also includes a shuttle valve (9), the electromagnetic proportional reversing valve (3) including a first working port and a second working port, the first working port being in communication with the oil inlet of the shuttle valve (9), the balancing valve (4), and the high-pressure chamber, and the second working port being in communication with the oil inlet of the shuttle valve (9), the control port of the balancing valve (4), and the first hydraulically controlled reversing valve (6); the oil outlet of the shuttle valve (9) being in communication with the first hydraulically controlled reversing valve (6), when hydraulic oil flows from the oil outlet of the shuttle valve (9) into the first hydraulically controlled reversing valve (6), the hydraulic oil causes the first hydraulically controlled reversing valve (6) to be in the left position, so that the second working port, the first hydraulically controlled reversing valve (6), and the low-pressure chamber are in communication, and when hydraulic oil flows from the metering pump (5) into the first hydraulically controlled reversing valve (6), the hydraulic oil causes the first hydraulically controlled reversing valve (6) to be in the right position; It also includes a first overflow valve (10) and a first throttling nozzle (11), the oil outlet of the shuttle valve (9) is connected to the pipeline between the first hydraulically controlled reversing valve (6), the first overflow valve (10) and the system oil drain pipeline (7), and the oil outlet of the shuttle valve (9) is connected to the pipeline between the first hydraulically controlled reversing valve (6), the first throttling nozzle (11) and the system oil drain pipeline (7).

2. The hydraulic winch system according to claim 1, characterized in that: The first hydraulically controlled reversing valve (6) comprises a left-position oil port and a right-position oil port. When the first hydraulically controlled reversing valve (6) is in the left position, the electromagnetic proportional reversing valve (3), the left-position oil port and the low-pressure chamber are in communication; when the first hydraulically controlled reversing valve (6) is in the right position, the right-position oil port, the first hydraulically controlled reversing valve (6) and the low-pressure chamber are in communication, and the right-position oil port, the first hydraulically controlled reversing valve (6) and the high-pressure chamber are in communication; the pipeline between the balancing valve (4) and the high-pressure chamber, the pipeline between the left-position oil port and the low-pressure chamber, the pipeline between the right-position oil port and the low-pressure chamber, and the pipeline between the right-position oil port and the high-pressure chamber are all in communication with the system oil drain pipeline (7).

3. The hydraulic winch system according to claim 1, characterized in that: It also includes a pressure compensator (12), which is located on the pipeline between the load-sensitive variable pump assembly (2) and the electromagnetic proportional reversing valve (3), and the pipeline between the oil outlet of the shuttle valve (9) and the first hydraulically controlled reversing valve (6) is connected to the pressure compensator (12).

4. The hydraulic winch system according to claim 1, characterized in that: It also includes a brake oil cylinder (13) and a second hydraulically controlled reversing valve (14), wherein the brake oil cylinder (13) is used to brake the hydraulic motor (8), and the oil outlet of the shuttle valve (9), the second hydraulically controlled reversing valve (14) and the brake oil cylinder (13) are connected.

5. The hydraulic winch system according to claim 4, characterized in that: It also includes a manual pump assembly (15) connected to the oil tank (1), and the manual pump assembly (15) is connected to the first hydraulically controlled reversing valve (6). When the hydraulic oil flows from the manual pump assembly (15) into the first hydraulically controlled reversing valve (6), the hydraulic oil causes the first hydraulically controlled reversing valve (6) to be in the right position, so that the hydraulic oil of the manual pump assembly (15) flows into the high-pressure chamber and the low-pressure chamber through the first hydraulically controlled reversing valve (6).

6. The hydraulic winch system according to claim 5, characterized in that: It also includes a throttle valve (16) and a switch valve (17); the low-pressure chamber, the throttle valve (16), the switch valve (17) and the high-pressure chamber are in communication; and the manual pump assembly (15) is in communication with the brake oil cylinder (13).

7. The hydraulic winch system according to any one of claims 1 to 6, characterized in that: The system further comprises a second overflow valve (18) and an electromagnetic reversing valve (19) connected to the second overflow valve (18), wherein the second overflow valve (18) is connected to the metering pump (5), and the second overflow valve (18) is connected to a system oil return pipeline (20), and the electromagnetic reversing valve (19) is connected to the system oil drain pipeline (7).

Images