Constant power hydraulic winch

Abstract

The application discloses a constant-power hydraulic winch and belongs to the field of hydraulic winches, and solves the problems of complex structure, response lag and low precision of the existing adjustment mode. The technical scheme for solving the problems mainly comprises a machine shell, a roller, a speed collector and a driving assembly. The driving assembly comprises a constant-displacement pump, a hydraulic oil circuit and a hydraulic motor in transmission connection with the roller. The constant-displacement pump outputs hydraulic oil to the hydraulic motor through the hydraulic oil circuit. The hydraulic oil circuit is sequentially provided with a first reversing valve, a second reversing valve, an electro-hydraulic proportional flow control valve and a third reversing valve along the hydraulic oil output direction. The reversing controller controls the second reversing valve and the third reversing valve to simultaneously switch the direction of the hydraulic oil according to the output direction of the first reversing valve. The electro-hydraulic proportional flow control valve changes the opening degree according to the detection result of the speed collector to maintain the speed of the traction rope unchanged. The application is mainly used for improving the response speed and control precision of the winch adjustment.

Description

Technical Field

[0001] This invention demonstrates a constant power hydraulic winch, belonging to the field of hydraulic winch technology. Background Technology

[0002] Hydraulic winches are essential traction devices in vehicles, ships, and construction machinery. With their powerful traction, excellent overload capacity, and high reliability in harsh environments, they play a crucial role in various rescue, self-rescue, towing, and heavy-load installation operations. They are widely used in rescue work in complex terrains such as snow, swamps, deserts, beaches, and muddy mountain roads. They are also commonly used for obstacle clearing, equipment towing, and facility installation, making them an indispensable safety and operational device for military, police, petroleum, fire, rescue, forestry, transportation, and special vehicles.

[0003] In actual use, when the traction rope is wound layer by layer on the drum, the effective winding diameter of the drum will change. If the traction speed at the end of the traction rope is to be kept constant, the speed of the hydraulic motor must be reduced accordingly as the number of winding layers increases and increased accordingly as the number of winding layers decreases. In actual traction operations, it is often necessary to keep the speed of the traction rope constant to ensure the smoothness and controllability of the traction operation.

[0004] To adapt to changes in drum diameter, existing technologies often rely on complex mechanical transmission mechanisms (such as gearboxes) or manual adjustments by operators to the engine throttle or hydraulic pump displacement to change system flow and thus adjust speed. These methods have significant drawbacks: mechanical transmission mechanisms increase system complexity, cost, and potential for failure; while manual adjustments are slow to respond and lack precision, failing to achieve real-time, accurate automatic control, especially under dynamically changing load conditions, making it difficult to guarantee a truly constant linear speed. Summary of the Invention

[0005] The purpose of this invention is to solve the problems of complex structure, slow response and low accuracy of existing adjustment methods. To this end, a constant power hydraulic winch is provided, which realizes automatic adjustment of hydraulic motor speed through electro-hydraulic proportional flow control valve, thereby improving response speed and control accuracy.

[0006] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0007] A constant power hydraulic winch, comprising:

[0008] chassis;

[0009] A roller, which is rotatably mounted on the machine housing, has a traction rope wound around it;

[0010] A speed acquisition device is used to detect the speed of the traction rope detaching from the drum in real time.

[0011] The drive assembly includes a metering pump, a hydraulic oil circuit, and a hydraulic motor connected to the roller drive, wherein the metering pump outputs hydraulic oil to the hydraulic motor through the hydraulic oil circuit;

[0012] The hydraulic oil circuit is provided with a first reversing valve, a second reversing valve, an electro-hydraulic proportional flow control valve, and a third reversing valve in sequence along the hydraulic oil output direction. The second and third reversing valves are connected to a reversing controller. The reversing controller controls the second and third reversing valves to switch directions simultaneously according to the output direction of the first reversing valve. The electro-hydraulic proportional flow control valve is electrically and / or communicatively connected to a speed acquisition device. The electro-hydraulic proportional flow control valve changes its opening degree according to the detection result of the speed acquisition device to maintain the speed of the traction rope constant.

[0013] The beneficial effects of using the present invention are:

[0014] In this invention, the speed of the traction rope is monitored in real time by a speed acquisition device, and the electro-hydraulic proportional flow control valve is linked with the speed acquisition device to dynamically adjust the valve opening. This allows for precise control of the hydraulic oil flow into the hydraulic motor based on the speed changes of the traction rope. When the number of layers of the traction rope changes, the speed acquisition device can detect the speed change in a timely manner. The electro-hydraulic proportional flow control valve adjusts its opening based on the detection result, thereby adjusting the speed of the hydraulic motor to maintain a constant speed of the traction rope, improving the stability and controllability of the winch traction operation. Through the linkage between the speed acquisition device and the electro-hydraulic proportional flow control valve, the speed of the hydraulic motor is automatically corrected according to the speed changes of the traction rope, achieving automatic and rapid adjustment. This can also replace manual adjustment of the throttle and pump displacement, eliminating the need for real-time operator intervention and improving the winch's response speed and automation level. Furthermore, this invention eliminates the need for mechanical transmission structures such as gearboxes. Relying on the hydraulic circuit and electronic control to achieve hydraulic motor speed regulation significantly simplifies the overall mechanical structure of the winch, reduces the overall size, lowers the manufacturing and assembly costs, and reduces potential mechanical jamming, wear, and other malfunctions, improving the overall operational reliability of the winch.

[0015] In addition, the hydraulic oil circuit is equipped with a first reversing valve, a second reversing valve, and a third reversing valve. When the output direction of the first reversing valve changes, the reversing control valve can simultaneously control the second and third reversing valves to switch directions. While changing the output direction of the hydraulic motor, it can also ensure that the flow direction of the hydraulic oil in the electro-hydraulic proportional flow control valve does not change. After changing the output direction of the hydraulic motor, the electro-hydraulic proportional flow control valve can still regulate the flow of hydraulic oil entering the hydraulic motor, thereby meeting the forward and reverse traction operation requirements of the winch and improving the applicability of the winch.

[0016] Preferably, the hydraulic oil circuit includes an oil supply line and a return line between the second and third directional valves. The hydraulic oil in the oil supply line flows to the hydraulic motor, and the hydraulic oil in the return line flows back to the fixed displacement pump. The electro-hydraulic proportional flow control valve is connected in series on the oil supply line and is connected to the return line. The electro-hydraulic proportional flow control valve changes its opening to regulate the flow rate to the return line.

[0017] Preferably, the electro-hydraulic proportional flow control valve includes a control valve inlet, a first control valve outlet, and a second control valve outlet. A main flow channel is formed between the control valve inlet and the first control valve outlet, and a branch flow channel is formed between the control valve inlet and the second control valve outlet. The main flow channel is connected in series on the oil delivery pipeline, and the second control valve outlet is connected to the return oil pipeline.

[0018] Preferably, the third directional valve includes a third valve port A and a third valve port B, which are respectively connected to a hydraulic motor. The hydraulic motor has a forward output state and a reverse output state. In the forward output state, the oil supply line is connected to the hydraulic motor through the third valve port A, and the hydraulic motor is connected to the return oil line through the third valve port B. In the reverse output state, the oil supply line is connected to the hydraulic motor through the third valve port B, and the hydraulic motor is connected to the return oil line through the third valve port A.

[0019] Preferably, the first directional valve includes a first valve port A and a first valve port B, and the second directional valve includes a second valve port A and a second valve port B. The second valve port A is connected to the third directional valve through an oil supply pipeline, and the second valve port B is connected to the third directional valve through a return oil pipeline. In the forward output state, the output end of the metering pump is connected to the oil supply pipeline through the first valve port A and the second valve port A; in the reverse output state, the output end of the metering pump is connected to the oil supply pipeline through the second valve port B and the second valve port A.

[0020] Preferably, the reversing controller is connected to the first valve port B, and the reversing controller simultaneously controls the second reversing valve and the third reversing valve to switch directions according to the pressure change of the first valve port B.

[0021] Preferably, the hydraulic winch also includes a controller. The electro-hydraulic proportional flow control valve is electrically and / or communicatively connected to a speed acquisition device via a sensor. The speed acquisition device includes a guide wheel and a sensor. The guide wheel maintains contact with the traction rope and rotates as the traction rope moves. The sensor detects the rotational speed of the guide wheel, and the controller calculates the speed of the traction rope based on the rotational speed of the guide wheel. Using the aforementioned technical solution, the movement of the traction rope is converted into the rotation of the guide wheel through the detection method of the guide wheel contacting the traction rope and rotating as the traction rope moves. This accurately reflects the actual movement state of the traction rope. The sensor collects the rotational speed of the guide wheel, and the controller calculates the linear velocity, providing accurate data support for subsequent constant speed control. Furthermore, the speed acquisition device, sensor, and electro-hydraulic proportional flow control valve are all connected to the controller, forming a complete electronic control closed loop. The rotational speed signal can be quickly transmitted, processed, and fed back to the flow control valve, resulting in timely speed adjustment response. This can compensate for speed deviations caused by changes in drum diameter and load fluctuations in real time, continuously maintaining the uniform speed of the traction rope.

[0022] Preferably, the metering pump is connected to an oil tank and an overflow valve. The metering pump has an oil suction port and an oil outlet. The oil suction port is connected to the oil tank, and the oil outlet is connected to the oil tank through the overflow valve.

[0023] Preferably, the hydraulic motor has a first interface and a second interface, and the hydraulic motor includes a forward output state and a reverse output state. In the forward output state, hydraulic oil enters the hydraulic motor from the first interface, and the hydraulic motor drives the drum to retract the traction rope. In the reverse output state, hydraulic oil enters the hydraulic motor from the second interface, and the hydraulic motor drives the drum to release the traction rope.

[0024] Preferably, both the first and second interfaces of the hydraulic motor are connected to a balance valve, which has a control pressure port and an oil inlet. The control pressure port of the balance valve is connected in parallel with the oil inlet of another balance valve.

[0025] Other features and advantages of the present invention will be disclosed in detail in the following detailed description and accompanying drawings. Attached Figure Description

[0026] The invention will be further described below with reference to the accompanying drawings:

[0027] Figure 1 This is a simplified diagram of a hydraulic winch according to the present invention;

[0028] Figure 2 This is a simplified diagram of a hydraulic motor in a hydraulic winch of the present invention in a positive output state;

[0029] Figure 3 This is a simplified diagram of a hydraulic winch in which the hydraulic motor is in a reverse output state.

[0030] Reference numerals: 1. Metering pump; 11. Motor; 12. Relief valve; 13. Oil tank; 2. First directional control valve; 21. First valve port P; 22. First valve port T; 23. First valve port A; 24. First valve port B; 3. Second directional control valve; 31. Second valve port P; 32. Second valve port T; 33. Second valve port A; 34. Second valve port B; 4. Electro-hydraulic proportional flow control valve; 41. First control valve inlet; 42. First control valve... 43. Second control valve outlet; 5. Third directional valve; 51. Third valve port P; 52. Third valve port T; 53. Third valve port A; 54. Third valve port B; 6. Hydraulic motor; 71. Drum; 72. Traction rope; 73. Speed ​​acquisition device; 8. Hydraulic oil circuit; 801. Oil supply line; 802. Oil return line; 811. First balance valve; 812. Second balance valve; 82. Pressure gauge; 9. Pressure relay. Detailed Implementation

[0031] The technical solutions of the embodiments of the present invention will be explained and described below with reference to the accompanying drawings. However, the following embodiments are only preferred embodiments of the present invention and not all of them. Other embodiments obtained by those skilled in the art based on the embodiments in the implementation methods without creative effort are all within the protection scope of the present invention.

[0032] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0033] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0034] like Figures 1 to 3As shown in the figure, this embodiment demonstrates a constant power hydraulic winch, including a housing, a drive assembly, and a speed acquisition device 73. A drum 71 is rotatably mounted on the housing, and a traction rope 72 is wound around the drum 71. One end of the traction rope 72 is fixed to the drum 71, and the other end extends out of the drum 71. The traction rope 72 includes a winding section wound around the drum 71 and a traction section extending out of the drum 71. The speed acquisition device 73 contacts the traction section of the traction rope 72 and is used to monitor the speed of the traction section in real time. The drive assembly includes a metering pump 1, a hydraulic oil circuit 8, and a hydraulic motor 6 that is driven by the drum 71. After the metering pump 1 is started, it outputs hydraulic oil to the hydraulic motor 6 through the hydraulic oil circuit 8. Under the action of the hydraulic oil, the hydraulic motor 6 starts and drives the drum 71 to rotate. The rotation of the drum 71 realizes the contraction and release of the traction rope 72.

[0035] In addition, in this embodiment, the hydraulic oil circuit 8 is provided with a first reversing valve 2, a second reversing valve 3, an electro-hydraulic proportional flow control valve 4, and a third reversing valve 5 in sequence along the hydraulic oil output direction. The second reversing valve 3 and the third reversing valve 5 are connected to a reversing controller. The reversing controller controls the second reversing valve 3 and the third reversing valve 5 to switch directions simultaneously according to the output direction of the first reversing valve 2. The electro-hydraulic proportional flow control valve 4 is electrically connected and / or communicatively connected to the speed acquisition device 73. The electro-hydraulic proportional flow control valve 4 changes its opening degree according to the detection result of the speed acquisition device 73 to maintain the speed of the traction rope 72 unchanged.

[0036] In this embodiment, the speed acquisition device 73 monitors the running speed of the traction rope 72 in real time, and the electro-hydraulic proportional flow control valve 4 is linked with the speed acquisition device 73 to dynamically adjust the valve opening. This allows for precise control of the hydraulic oil flow into the hydraulic motor 6 based on the speed changes of the traction rope 72. When the number of layers of the traction rope 72 changes, the speed acquisition device 73 can detect the speed change in a timely manner. The electro-hydraulic proportional flow control valve 4 adjusts its opening based on the detection result, thereby adjusting the rotational speed of the hydraulic motor 6 to maintain a constant speed for the traction rope 72, improving the stability and controllability of the winch traction operation. 3. In conjunction with the electro-hydraulic proportional flow control valve 4, the speed of the hydraulic motor 6 is automatically corrected according to the speed change of the traction rope 72, realizing automatic and rapid adjustment. It can also replace the manual adjustment of the throttle and pump displacement, without the need for real-time operator intervention, thus improving the response speed and automation level of the winch. Secondly, this embodiment does not require the addition of a gearbox or other mechanical transmission structure. The speed adjustment of the hydraulic motor 6 is achieved by relying on the hydraulic circuit and the electronic control, which greatly simplifies the overall mechanical structure of the winch, reduces the overall size of the machine, and reduces the manufacturing and assembly costs of the winch. It can also reduce potential faults such as mechanical jamming and wear, and improve the overall operational reliability of the winch.

[0037] In addition, the hydraulic oil circuit 8 is equipped with a first reversing valve 2, a second reversing valve 3, and a third reversing valve 5. When the output direction of the first reversing valve 2 changes, the reversing control valve can simultaneously control the second reversing valve 3 and the third reversing valve 5 to switch directions. While changing the output direction of the hydraulic motor 6, it can also ensure that the flow direction of the hydraulic oil in the electro-hydraulic proportional flow control valve 4 does not change. After changing the output direction of the hydraulic motor 6, the electro-hydraulic proportional flow control valve 4 can still regulate the flow of hydraulic oil entering the hydraulic motor 6, thereby meeting the forward and reverse traction operation requirements of the winch and improving the applicability of the winch.

[0038] It should be noted that in this embodiment, the drive component of the winch uses a fixed displacement pump 1 as the power source. The output flow of the fixed displacement pump 1 remains constant. Compared with traditional variable displacement pumps or constant power pumps, it has the advantages of simple structure, low manufacturing precision requirements, and low cost. In addition, the fixed displacement pump 1 has relatively relaxed requirements for oil cleanliness, resulting in lower maintenance costs. Furthermore, an electro-hydraulic proportional flow control valve 4 is used to control the flow of hydraulic oil to the hydraulic motor 6, thereby adjusting the speed of the hydraulic motor 6. Compared with complex mechanical transmission mechanisms, the electro-hydraulic proportional flow control valve 4 has fewer overall parts, fewer failure points, and higher reliability.

[0039] Specifically, in this embodiment, the drive assembly further includes a motor 11. The fixed displacement pump 1 is connected to an oil tank 13 and an overflow valve 12. The fixed displacement pump 1 has an oil suction port and an oil outlet. The oil suction port is connected to the oil tank 13, and the oil outlet is connected to the oil tank 13 through the overflow valve 12. The output end of the motor 11 is connected to the fixed displacement pump 1 for transmission. After the motor 11 starts, it drives the fixed displacement pump 1 to run. The oil suction port of the fixed displacement pump 1 draws hydraulic oil from the oil tank 13 and outputs it to the hydraulic motor 6 through the hydraulic oil circuit 8. After passing through the hydraulic motor 6, the hydraulic oil flows back to the fixed displacement pump 1 along the hydraulic oil circuit 8, and finally flows back to the oil tank 13 through the oil outlet of the fixed displacement pump 1, thereby forming a circulation of hydraulic oil.

[0040] Specifically, in this embodiment, the hydraulic oil circuit 8 sequentially includes a first reversing valve 2, a second reversing valve 3, an electro-hydraulic proportional flow control valve 4, and a third reversing valve 5 between the fixed displacement pump 1 and the hydraulic motor 6. The hydraulic oil circuit 8 includes an oil supply line 801 and a return line 802 between the second reversing valve 3 and the third reversing valve 5. The hydraulic oil in the oil supply line 801 flows towards the hydraulic motor 6, and the hydraulic oil in the return line 802 flows towards the fixed displacement pump 1. The electro-hydraulic proportional flow control valve 4 is connected in series with the oil supply line 801 and communicates with the return line 802. The electro-hydraulic proportional flow control valve 4 changes its opening to adjust the flow rate to the return line 802.

[0041] Specifically, in this embodiment, the electro-hydraulic proportional flow control valve 4 includes a control valve inlet, a first control valve outlet 42, and a second control valve outlet 43. A main flow channel is formed between the control valve inlet and the first control valve outlet 42, and a branch flow channel is formed between the control valve inlet and the second control valve outlet 43. The main flow channel is connected in series on the oil supply pipeline 801, and the second control valve outlet 43 is connected to the return oil pipeline 802. After the hydraulic oil in the oil supply pipeline 801 enters the main flow channel through the control valve inlet, part of the hydraulic oil continues to flow along the oil supply pipeline 801 to the hydraulic motor 6 through the first control valve outlet 42, while the remaining hydraulic oil flows directly from the second control valve outlet 43 to the return oil pipeline 802 along the branch flow channel. This part of the hydraulic oil does not pass through the hydraulic motor 6. Adjusting the opening of the electro-hydraulic proportional flow control valve 4 refers to changing the flow rate to the branch flow channel. Specifically, reducing the opening of the electro-hydraulic proportional flow control valve 4 increases the flow rate of hydraulic oil entering the flow divider channel and decreases the flow rate to the hydraulic motor 6, thus reducing the speed of the hydraulic motor 6. Conversely, increasing the opening of the electro-hydraulic proportional flow control valve 4 decreases the flow rate of hydraulic oil entering the flow divider channel and increases the flow rate to the hydraulic motor 6, thus increasing the speed of the hydraulic motor 6.

[0042] Specifically, in this embodiment, the hydraulic winch also includes a controller. The electro-hydraulic proportional flow control valve 4 is electrically and / or communicatively connected to the speed acquisition device 73 via a sensor. The speed acquisition device 73 includes a guide wheel and a sensor. The guide wheel maintains contact with the traction rope 72 and rotates as the traction rope 72 moves. The sensor detects the rotational speed of the guide wheel. The controller calculates the speed of the traction rope 72 based on the rotational speed of the guide wheel. By detecting the guide wheel's contact with the traction rope 72 and its rotation as the traction rope 72 moves, the movement of the traction rope 72 is converted into the rotation of the guide wheel, which can accurately reflect the actual movement state of the traction rope 72. The sensor collects the rotational speed of the guide wheel, and the controller converts it into linear velocity, providing accurate data support for subsequent constant speed control. In addition, the speed acquisition device 73, the sensor, and the electro-hydraulic proportional flow control valve 4 are all connected to the controller, forming a complete electronic control closed loop. The speed signal can be quickly transmitted, processed, and fed back to the flow control valve. The speed adjustment action is timely and can offset the speed deviation caused by changes in the diameter of the drum 71 and load fluctuations in real time, continuously maintaining the uniform speed of the traction rope 72.

[0043] Specifically, in this embodiment, the first directional valve 2 includes a first valve port A23, a first valve port B24, a first valve port P21, and a first valve port T22. The suction port of the fixed displacement pump 1 is connected to the first valve port P21, and the outlet port of the fixed displacement pump 1 is connected to the first valve port T22. The first directional valve 2 has a forward output state, a reverse output state, and an idling state. When the first directional valve 2 is in the forward output state, inside the first directional valve 2, the first valve port P21 is connected to the first valve port A23, and the first valve port T22 is connected to the first valve port A24. Port B24 is connected; when the first directional valve 2 is in the reverse output state, inside the first directional valve 2, the first valve port P21 is connected to the first valve port B24, and the first valve port T22 is connected to the first valve port A23; when the first directional valve 2 is in the idling state, the first valve port P21 is connected to the first valve port T22. At this time, the hydraulic oil output by the fixed displacement pump 1 enters the first directional valve 2 from the first valve port P21, and the hydraulic oil flows out of the first directional valve 2 from the first valve port T22 and flows back into the fixed displacement pump 1. The hydraulic oil cannot reach the hydraulic motor 6.

[0044] Specifically, in this embodiment, the second directional valve 3 includes a second valve port A33, a second valve port B34, a second valve port P31, and a second valve port T32; the third directional valve 5 includes a third valve port A53, a third valve port B54, a third valve port P51, and a third valve port T52; the hydraulic motor 6 includes a first interface and a second interface; the first valve port A23 of the first directional valve 2 is connected to the second valve port P31 of the second directional valve 3 via a pipeline; and the first valve port B24 of the first directional valve 2 is connected to the second valve port T32 of the second directional valve 3 via a pipeline. The second valve port A33 of the second directional valve 3 is connected to the inlet of the control valve through the oil supply line 801. The oil supply line 801 is connected to the third valve port P51 of the third directional valve 5 after passing through the outlet 42 of the first control valve. The second valve port B34 of the second directional valve 3 is directly connected to the third valve port T52 of the third directional valve 5 through the return oil line 802. The third valve port A53 of the third directional valve 5 is connected to the first interface of the hydraulic motor 6 through a pipeline. The third valve port B54 of the third directional valve 5 is connected to the second interface of the hydraulic motor 6 through a pipeline.

[0045] Specifically, in this embodiment, both the second reversing valve 3 and the third reversing valve 5 have a forward output state and a reverse output state. When the first reversing valve 2 is in the forward output state, both the second reversing valve 3 and the third reversing valve 5 are in the forward output state; when the first reversing valve 2 is in the reverse output state, both the second reversing valve 3 and the third reversing valve 5 are in the reverse output state. In the forward output state, inside the second reversing valve 3, the second valve port P31 is connected to the second valve port A33. T32 is connected to the second valve port B34. Inside the third directional valve 5, the third valve port P51 is connected to the third valve port A53, and the third valve port T52 is connected to the third valve port B54. In the reverse output state, inside the second directional valve 3, the second valve port P31 is connected to the second valve port B34, and the second valve port T32 is connected to the second valve port A33. Inside the third directional valve 5, the third valve port P51 is connected to the third valve port B54, and the third valve port T52 is connected to the third valve port A53.

[0046] It should be noted that in the forward output state, hydraulic oil enters the hydraulic motor 6 from the first interface, and the hydraulic motor 6 outputs in the forward direction to drive the drum 71 to retract the traction rope 72. In the reverse output state, hydraulic oil enters the hydraulic motor 6 from the second interface, and the hydraulic motor 6 outputs in the reverse direction to drive the drum 71 to release the traction rope 72.

[0047] Specifically, in this embodiment, one end of the reversing controller is connected to the first valve port B24, and the other end is connected to both the second reversing valve 3 and the third reversing valve 5. When the first reversing valve 2 is in the forward output state, the hydraulic oil pressure at the first valve port B24 is small and cannot trigger the reversing control valve. At this time, both the second reversing valve 3 and the third reversing valve 5 are in the forward output state. When the first reversing valve 2 switches to the reverse output state, the hydraulic oil leaves the first reversing valve 2 from the first valve port B24 and flows to the hydraulic motor 6. At this time, the hydraulic oil pressure at the first valve port B24 is large, which triggers the reversing control valve. The reversing control valve simultaneously controls the second reversing valve 3 and the third reversing valve 5 to switch to the reverse output state.

[0048] Specifically, in this embodiment, both the first and second interfaces of the hydraulic motor 6 are connected to a balance valve. The balance valve has a control pressure port and an oil inlet. The control pressure port of the balance valve is connected in parallel with the oil inlet of another balance valve. The hydraulic oil circuit 8 is provided with four connectors for connecting pressure gauges 82 between the third directional valve 5 and the hydraulic motor 6. When the hydraulic oil circuit 8 malfunctions, pressure gauges 82 can be connected through the connectors to detect the status of the hydraulic oil circuit 8, which facilitates troubleshooting.

[0049] Regarding the operating status of the hydraulic winch;

[0050] like Figure 2As shown, when the hydraulic winch is in the rope-reeling stage, the first reversing valve 2, the second reversing valve 3, and the third reversing valve 5 are all in the positive output state. At this time, the motor 11 drives the fixed displacement pump 1 to run. The suction port of the fixed displacement pump 1 draws hydraulic oil from the oil tank 13 and delivers the hydraulic oil to the first valve port P21 of the first reversing valve 2. After leaving the first valve port A23, the hydraulic oil passes through the second valve port P31 and enters the second reversing valve 3. Then, the hydraulic oil enters the electro-hydraulic proportional flow control valve 4 along the oil delivery pipeline. The electro-hydraulic proportional flow control valve 4 controls, according to the speed acquisition device 73, that part of the hydraulic oil flows directly to the return oil pipeline through the diversion channel, while the remaining hydraulic oil flows along the oil delivery pipeline. The hydraulic oil enters the third directional valve 5 through the third valve port P51. After leaving the third valve port A53, the hydraulic oil enters the hydraulic motor 6 through the first interface. The hydraulic oil drives the hydraulic motor 6 to output in the forward direction, so that the winch is in the rope winding stage. After leaving the hydraulic motor 6 through the second interface, the hydraulic oil returns to the third directional valve 5 through the third valve port B54. The hydraulic oil returns to the second directional valve 3 along the return oil pipe and through the second valve port B34. Then, the hydraulic oil returns to the first directional valve 2 through the second valve port T32 and the first valve port B24. Finally, the hydraulic oil returns to the fixed displacement pump 1 from the first valve port T22 and flows back to the oil tank 13 from the oil outlet, thus completing the circulation of the hydraulic oil.

[0051] like Figure 3 As shown, when the hydraulic winch is in the rope-laying stage, the first directional valve 2, the second directional valve 3, and the third directional valve 5 are all in the reverse output state. At this time, the motor 11 drives the fixed displacement pump 1 to run. The suction port of the fixed displacement pump 1 draws hydraulic oil from the oil tank 13 and delivers the hydraulic oil to the first valve port P21 of the first directional valve 2. After leaving the first valve port B24, the hydraulic oil passes through the second valve port T32 and enters the second directional valve 3. Then, the hydraulic oil enters the electro-hydraulic proportional flow control valve 4 along the oil delivery pipeline. The electro-hydraulic proportional flow control valve 4 controls, according to the speed acquisition device 73, that part of the hydraulic oil flows directly to the return oil pipeline through the diversion channel, while the remaining hydraulic oil flows along the oil delivery pipeline. The hydraulic oil enters the third directional valve 5 through the third valve port P51. After leaving the third valve port B54, the hydraulic oil enters the hydraulic motor 6 through the second interface. The hydraulic oil drives the hydraulic motor 6 to output in the reverse direction, so that the winch is in the rope-releasing stage. After leaving the hydraulic motor 6 through the first interface, the hydraulic oil returns to the third directional valve 5 through the third valve port A53. The hydraulic oil returns to the second directional valve 3 along the return oil pipe and through the second valve port B34. Then, the hydraulic oil returns to the first directional valve 2 through the second valve port P31 and the first valve port A23. Finally, the hydraulic oil returns to the fixed displacement pump 1 from the first valve port P21 and flows back to the oil tank 13 from the oil outlet, thus completing the circulation of the hydraulic oil.

[0052] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Those skilled in the art should understand that the present invention includes, but is not limited to, the contents described in the accompanying drawings and the specific embodiments above. Any modifications that do not depart from the functional and structural principles of the present invention will be included within the scope of the claims.

Claims

1. A constant power hydraulic winch characterized by, include: chassis; A roller, which is rotatably mounted on the machine housing, has a traction rope wound around it; A speed acquisition device is used to detect the speed of the traction rope detaching from the drum in real time. The drive assembly includes a metering pump, a hydraulic oil circuit, and a hydraulic motor connected to the roller drive, wherein the metering pump outputs hydraulic oil to the hydraulic motor through the hydraulic oil circuit; The hydraulic oil circuit is provided with a first reversing valve, a second reversing valve, an electro-hydraulic proportional flow control valve, and a third reversing valve in sequence along the hydraulic oil output direction. The second and third reversing valves are connected to a reversing controller. The reversing controller controls the second and third reversing valves to switch directions simultaneously according to the output direction of the first reversing valve. The electro-hydraulic proportional flow control valve is electrically and / or communicatively connected to a speed acquisition device. The electro-hydraulic proportional flow control valve changes its opening degree according to the detection result of the speed acquisition device to maintain the speed of the traction rope constant.

2. A constant power hydraulic winch according to claim 1 wherein, The hydraulic oil circuit includes an oil supply line and a return line between the second and third directional valves. The hydraulic oil in the oil supply line flows to the hydraulic motor, and the hydraulic oil in the return line flows back to the metering pump. The electro-hydraulic proportional flow control valve is connected in series on the oil supply line and is connected to the return line. The electro-hydraulic proportional flow control valve changes its opening to regulate the flow rate to the return line.

3. A constant power hydraulic winch according to claim 2, characterised in that, The electro-hydraulic proportional flow control valve includes a control valve inlet, a first control valve outlet, and a second control valve outlet. A main flow channel is formed between the control valve inlet and the first control valve outlet, and a branch flow channel is formed between the control valve inlet and the second control valve outlet. The main flow channel is connected in series on the oil delivery pipeline, and the second control valve outlet is connected to the return oil pipeline.

4. A constant power hydraulic winch according to claim 2, characterized in that, The third directional valve includes a third valve port A and a third valve port B, which are respectively connected to a hydraulic motor. The hydraulic motor has a forward output state and a reverse output state. In the forward output state, the oil supply line is connected to the hydraulic motor through the third valve port A, and the hydraulic motor is connected to the return oil line through the third valve port B. In the reverse output state, the oil supply line is connected to the hydraulic motor through the third valve port B, and the hydraulic motor is connected to the return oil line through the third valve port A.

5. A constant power hydraulic winch according to claim 4, characterized in that, The first directional valve includes a first valve port A and a first valve port B, and the second directional valve includes a second valve port A and a second valve port B. The second valve port A is connected to the third directional valve through an oil supply pipeline, and the second valve port B is connected to the third directional valve through a return oil pipeline. In the forward output state, the output end of the metering pump is connected to the oil supply pipeline through the first valve port A and the second valve port A; in the reverse output state, the output end of the metering pump is connected to the oil supply pipeline through the second valve port B and the second valve port A.

6. A constant power hydraulic winch according to claim 5, characterized in that, The reversing controller is connected to the first valve port B, and the reversing controller simultaneously controls the second reversing valve and the third reversing valve to switch directions according to the pressure change of the first valve port B.

7. A constant power hydraulic winch according to claim 1, characterized in that, The hydraulic winch also includes a controller. The electro-hydraulic proportional flow control valve is electrically and / or communicatively connected to a speed acquisition device via a sensor. The speed acquisition device includes a guide wheel and a sensor. The guide wheel maintains contact with the traction rope and rotates as the traction rope moves. The sensor detects the rotational speed of the guide wheel. The controller calculates the speed of the traction rope based on the rotational speed of the guide wheel.

8. A constant power hydraulic winch according to claim 1, characterized in that, The metering pump is connected to an oil tank and an overflow valve. The metering pump has an oil suction port and an oil outlet. The oil suction port is connected to the oil tank, and the oil outlet is connected to the oil tank through the overflow valve.

9. A constant power hydraulic winch according to claim 1, characterized in that, The hydraulic motor has a first interface and a second interface. The hydraulic motor includes a forward output state and a reverse output state. In the forward output state, hydraulic oil enters the hydraulic motor from the first interface, and the hydraulic motor drives the drum to retract the traction rope. In the reverse output state, hydraulic oil enters the hydraulic motor from the second interface, and the hydraulic motor drives the drum to release the traction rope.

10. A constant power hydraulic winch according to claim 9, characterized in that, The first and second interfaces of the hydraulic motor are each connected to a balance valve. The balance valve has a control pressure port and an oil inlet. The control pressure port of the balance valve is connected in parallel with the oil inlet of another balance valve.

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