Winch hydraulic control system and winch mechanism
By introducing a flow-type balance valve and a proportional relief valve into the hoist hydraulic system, the problems of high energy consumption and unstable lowering of heavy objects were solved, resulting in reduced system energy consumption and improved stability of lowering heavy objects, while ensuring the speed control accuracy during the floating phase.
Patent Information
- Application Number
- CN202520154567.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-01-22
- Publication Date
- 2025-12-23
- Estimated Expiration
- 2035-01-22
AI Technical Summary
The existing hydraulic winch systems in construction machinery have high energy consumption, unstable lowering of heavy objects, and unstable speed control during the floating phase.
The winch hydraulic control system includes a first oil circuit, a second oil circuit, a hydraulic motor, a balance valve, a sequence valve, and a proportional relief valve. Energy consumption is reduced through the flow-type design of the balance valve, the hydraulic oil flow is controlled by the proportional relief valve during the floating phase, and the sequence valve maintains oil pressure stability.
It reduces system energy consumption, improves the stability of lowering heavy objects and the speed control accuracy during the floating phase, and avoids wire rope slack.
Smart Images
Figure CN223708113U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of hydraulic control technology, and in particular to a winch hydraulic control system and a winch mechanism. Background Technology
[0002] In the field of construction machinery, cranes and rotary drilling rigs are important pieces of equipment. When cranes lift goods or rotary drilling rigs are drilling, winch mechanisms are needed to lift heavy objects or drill buckets. Generally, the working principle of a winch mechanism is that a hydraulic motor outputs torque through the winch mechanism to control the rotation of the wire rope drum, thereby lifting and lowering the drilling tools or other heavy objects.
[0003] However, in the existing technology, the winch hydraulic system in construction machinery still has some problems such as high energy consumption, unstable lowering of heavy objects, and unstable speed control during the floating phase. Utility Model Content
[0004] The technical problem solved by this utility model is to provide a winch hydraulic control system and winch mechanism, which is beneficial to reduce system energy consumption, improve the stability of lowering heavy objects and the stability of speed control during the floating phase.
[0005] To solve the above-mentioned technical problems, this utility model provides a hoist hydraulic control system, including: a first oil circuit, the first oil circuit being connected to a first hydraulic oil inlet and a first hydraulic oil outlet; a second oil circuit, the second oil circuit being connected to a second hydraulic oil inlet and a second hydraulic oil outlet; a hydraulic motor, the hydraulic motor including a first working port and a second working port, the first working port being connected to the first hydraulic oil outlet and the second working port being connected to the second hydraulic oil outlet; a balance valve, the balance valve being disposed on the first oil circuit, the balance valve including a balance valve 1 port, a balance valve 2 port and a balance valve pilot port, the balance valve 1 port being connected to the first hydraulic oil outlet; and a balance valve balancing valve, the balance valve being disposed on the first oil circuit, the balance valve including a balance valve 1 port, a balance valve 2 port and a balance valve pilot port. A hydraulic oil outlet connection is provided, the balance valve port 2 is connected to the first hydraulic oil inlet, and the balance valve pilot port is connected to the second oil circuit; a third oil circuit is provided, connecting the first oil circuit and the second oil circuit; a sequence valve is provided on the third oil circuit, the sequence valve includes a sequence valve inlet and a sequence valve outlet, the sequence valve inlet is connected to the first oil circuit; a proportional relief valve is provided on the third oil circuit, the proportional relief valve includes a proportional relief valve inlet and a proportional relief valve outlet, the proportional relief valve inlet is connected to the sequence valve outlet, and the proportional relief valve outlet is connected to the second oil circuit.
[0006] Optionally, it also includes a first shuttle valve, which includes a first shuttle valve 1 port, a first shuttle valve 2 port and a first shuttle valve 3 port. The first shuttle valve 1 port is connected to the first oil circuit and the first shuttle valve 2 port is connected to the second oil circuit.
[0007] Optionally, it also includes a hydraulically controlled directional valve, which includes a control port 1, a directional valve port 2, a directional valve port 3, and a directional valve port 4. The control port 1 is connected to the first shuttle valve port 3, the directional valve port 2 is connected to the pilot pressure port, the directional valve port 4 is connected to the oil tank, and the directional valve port 3 is connected to the brake port.
[0008] Optionally, when the oil pressure at the control port 1 of the hydraulic directional valve is greater than the set working pressure of the hydraulic directional valve, the hydraulic directional valve switches from the first working position to the second working position. The first working position is configured such that the directional valve port 4 is connected to the directional valve port 3, and the second working position is configured such that the directional valve port 2 is connected to the directional valve port 3.
[0009] Optionally, it also includes a solenoid valve directional valve, which includes a solenoid valve port 1, a solenoid valve port 2, and a solenoid valve port 3. The solenoid valve port 1 is connected to the pilot pressure port, the solenoid valve port 2 is connected to the brake port, and the solenoid valve port 3 is connected to the oil tank. When the solenoid valve directional valve is de-energized, the solenoid valve port 3 is connected to the solenoid valve port 2; when the solenoid valve is energized, the solenoid valve port 1 is connected to the solenoid valve port 2.
[0010] Optionally, a second shuttle valve is also included, which includes a second shuttle valve 1 port, a second shuttle valve 2 port, and a second shuttle valve 3 port. The first shuttle valve 1 port is connected to the reversing valve 3 port, the second shuttle valve 2 port is connected to the solenoid valve 2 port, and the second shuttle valve 3 port is connected to the brake port.
[0011] Optionally, a one-way throttle valve is also included, which is disposed on the connecting oil line between the shuttle valve port 3 and the brake port.
[0012] Optionally, it also includes a first check valve, which includes a first inlet and a first outlet. The first inlet is connected to a first oil replenishment port, and the first outlet is connected to a first hydraulic oil outlet and the inlet of the sequence valve.
[0013] Optionally, a second check valve is also included, which includes a second inlet and a second outlet. The second inlet is connected to a second oil replenishment port, and the second outlet is connected to a second hydraulic oil outlet.
[0014] Optionally, an overflow valve may also be included, which is connected between the first oil passage and the second oil passage.
[0015] Optionally, a first damper is also included, which is disposed between the second oil passage and the pilot port of the balance valve.
[0016] Optionally, a second damper is also included, which is disposed between the first damper and the oil tank.
[0017] Accordingly, this utility model embodiment also provides a hoisting mechanism that adopts the above-mentioned hoisting hydraulic control system.
[0018] Compared with the prior art, the technical solution of this utility model embodiment has the following beneficial effects:
[0019] The winch hydraulic control system provided in this technical solution allows hydraulic oil to enter the hydraulic motor through ports 2 and 1 of the balance valve during the hoisting phase, and then return through the second oil circuit. During the hoisting lowering phase, hydraulic oil enters the hydraulic motor through the second oil circuit, while a portion of the hydraulic oil enters the pilot port of the balance valve to open it. The hydraulic oil then returns through the open balance valve. The opening pressure of the balance valve is independent of the load; the oil pressure provided by the second hydraulic oil inlet during the lowering phase only needs to meet the opening pressure of the balance valve, thus helping to reduce system energy consumption. During the hoisting floating phase, the flow rate of hydraulic oil through the third circuit is controlled by a proportional relief valve, and the pressure at the outlet of the first hydraulic oil is kept above the set pressure of the sequence valve during the floating process by a sequence valve, improving the stability of the load lowering and the control of the load lowering speed. Attached Figure Description
[0020] Figure 1 This is a hydraulic schematic diagram of the winch hydraulic control system in one embodiment of this utility model. Detailed Implementation
[0021] As described in the background section, current winch hydraulic control systems still suffer from problems such as high energy consumption, unstable lowering of heavy objects, and unstable speed control during the floating phase.
[0022] To address the aforementioned problems, this utility model provides a winch hydraulic control system and a winch mechanism. The winch hydraulic control system includes a first oil circuit, a second oil circuit, a third oil circuit, a hydraulic motor, a balance valve, a sequence valve, and a proportional relief valve. The balance valve is located on the first oil circuit, and its pilot valve port is connected to the second oil circuit. The sequence valve and the proportional flow valve are located on the third oil circuit. During the winch's ascending phase, hydraulic oil enters the hydraulic motor through the first oil circuit and then returns through the second oil circuit. During the winch's lowering phase, hydraulic oil enters the hydraulic motor through the second oil circuit, and a portion of the hydraulic oil enters the pilot valve port to open the balance valve, allowing the hydraulic oil to return through the first oil circuit. The balance valve used in this utility model embodiment is a flow-type balance valve, whose opening pressure is unaffected by the load. During the lowering phase, the hydraulic oil supplied by the second oil circuit is used to open the balance valve, which reduces system energy consumption and improves the stability of lowering heavy objects. During the floating phase of the hoist, the hydraulic oil forms a floating circuit through the first working port of the hydraulic motor, the first hydraulic oil outlet, the third oil circuit, the second hydraulic oil outlet, and the second working port of the hydraulic motor. The proportional relief valve can control the opening pressure according to the current, so that the lowering speed during the floating phase is controllable. The set pressure of the sequence valve can ensure that the oil pressure at the first hydraulic oil outlet is kept above the set pressure of the sequence valve, so as to prevent the wire rope of the hoisting mechanism from slackening after the heavy object touches the ground.
[0023] To make the above-mentioned objectives, features and beneficial effects of this utility model more apparent and understandable, the specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings.
[0024] Figure 1 This is a hydraulic schematic diagram of the winch hydraulic control system in one embodiment of this utility model.
[0025] refer to Figure 1The hoist hydraulic control system 1 includes: a first oil circuit Z1, which connects a first hydraulic oil inlet V1 and a first hydraulic oil outlet C1; a second oil circuit Z2, which connects a second hydraulic oil inlet V2 and a second hydraulic oil outlet C2; a hydraulic motor (not shown), which includes a first working port and a second working port, the first working port being connected to the first hydraulic oil outlet C1 and the second working port being connected to the second hydraulic oil outlet C2; and a balance valve CT5, which is disposed on the first oil circuit Z1 and includes a balance valve 1 port 51, a balance valve 2 port 52, and a balance valve pilot port 53. The balance valve 1 port 51 is connected to the first hydraulic oil outlet C1, the balance valve 2 port 53 ... 52 is connected to the first hydraulic oil inlet V1, and the pilot port 53 of the balance valve is connected to the second oil circuit Z2; the third oil circuit Z3 is connected to the first oil circuit Z1 and the second oil circuit Z2; the sequence valve CT2 is disposed on the third oil circuit Z3, and the sequence valve Z3 includes a sequence valve inlet 21 and a sequence valve outlet 22, and the sequence valve inlet 21 is connected to the first oil circuit Z1; the proportional relief valve CT3 is disposed on the third oil circuit Z3, and the proportional relief valve CT3 includes a proportional relief valve inlet 31 and a proportional relief valve outlet 32, the proportional relief valve inlet 31 is connected to the sequence valve outlet 22, and the proportional relief valve outlet 32 is connected to the second oil circuit Z2.
[0026] In this embodiment, during the hoisting upward phase, oil enters through the first hydraulic oil inlet V1, and the oil passage from the balance valve 2 port 52 to the balance valve 1 port is connected. The hydraulic oil passes through the balance valve CT5 in the first oil passage Z1 to the first hydraulic oil outlet C1, and then enters the first working port of the hydraulic motor, driving the hydraulic motor to work. The oil then flows out from the second working port of the hydraulic motor and returns through the second oil passage Z2. During the hoisting downward phase, oil enters through the second hydraulic oil inlet V2, and the hydraulic oil enters the second working port B of the hydraulic motor through the second oil passage Z2. A portion of the hydraulic oil also enters the balance valve pilot port 53 of the balance valve CT5 to open the balance valve CT5, allowing the hydraulic oil to flow out of the first working port of the hydraulic motor and then return through the first oil passage Z2. In the floating phase of the hoisting circuit, neither the first hydraulic oil inlet V1 nor the second hydraulic oil inlet V2 receives oil. The load is lowered by its own weight, while the hoisting wire rope is tensioned. A floating circuit is formed between the hydraulic motor and the third oil circuit Z3. The hydraulic oil flows out from the first working port of the hydraulic motor, passes through the first hydraulic oil outlet C1, the sequence valve CT2, the proportional relief valve CT3, and the second hydraulic oil outlet C2, and enters the second working port of the hydraulic motor. The proportional relief valve CT3 controls the lowering speed of the load during the floating phase. The sequence valve CT2 has a set pressure to ensure that the oil pressure at the first hydraulic oil outlet C1 is maintained above the set pressure of the sequence valve CT2, thereby ensuring the tension of the wire rope and preventing the wire rope from slackening when the load hits the ground.
[0027] In this embodiment, the balance valve CT5 is a flow-type balance valve. The opening pressure of the balance valve CT5 is not affected by the load, making it easier to control the stability when lowering heavy objects. Moreover, compared with using a pressure-type balance valve to control the first and second oil circuits, in this embodiment, the balance valve CT5 only needs to be opened with lower pressure oil during the hoisting lowering stage, which can reduce system energy consumption.
[0028] Continue to refer to Figure 1 The hoist hydraulic control system 1 further includes a first shuttle valve CT7, which includes a first shuttle valve 1 port 71, a first shuttle valve 2 port 72 and a first shuttle valve 3 port 73. The first shuttle valve 1 port 71 is connected to the first oil circuit Z1, and the first shuttle valve 2 port 72 is connected to the second oil circuit Z2.
[0029] Continue to refer to Figure 1 The hoist hydraulic control system 1 further includes a hydraulically controlled directional valve CT11, which includes a control port 111, a directional valve port 212, a directional valve port 313, and a directional valve port 414. The control port 111 is connected to the first shuttle valve port 373, the directional valve port 212 is connected to the pilot pressure port P1, the directional valve port 414 is connected to the oil tank T, and the directional valve port 313 is connected to the brake port PG.
[0030] In this embodiment, when the oil pressure at the control port 111 of the hydraulic directional valve CT11 is greater than the set working pressure of the hydraulic directional valve CT11, the hydraulic directional valve CT11 switches from the first working position to the second working position. The first working position is configured such that the directional valve port 4 114 is connected to the directional valve port 3 113, and the second working position is configured such that the directional valve port 2 112 is connected to the directional valve port 3 113.
[0031] In this embodiment, hydraulic oil is stored at the pilot pressure port P1, and the brake port PG is connected to the winch braking system. The hydraulic oil enters the brake port PG to release the brake of the winch mechanism.
[0032] During the hoisting ascent phase, hydraulic oil enters through the first hydraulic oil inlet V1. Part of the hydraulic oil enters the control port 111 of the hydraulic directional valve CT11 through the first shuttle valve 1 port 71 and the first shuttle valve 3 port 73. When the oil pressure at the control port 111 is greater than the set working pressure of the hydraulic directional valve CT11, the hydraulic directional valve CT11 switches from the first working position to the second working position. The hydraulic oil at the pilot pressure port P1 can enter the brake port PG through the hydraulic directional valve CT11 to release the brake of the hoisting mechanism.
[0033] In this embodiment, a second shuttle valve CT10 and a one-way throttle valve CT8 are also provided between the reversing valve 3 port 113 and the brake port PG.
[0034] Specifically, the second shuttle valve CT10 includes a second shuttle valve port 101, a second shuttle valve port 2 102, and a second shuttle valve port 3 103. The first shuttle valve port 101 is connected to the reversing valve port 3 113, and the second shuttle valve port 3 103 is connected to the brake port PG. The one-way throttle valve CT8 is disposed on the connecting oil line between the shuttle valve port 3 103 and the brake port PG.
[0035] In this embodiment, the hydraulic oil at the pilot pressure port P1 passes through the hydraulic control directional valve CT11, and then through the second shuttle valve 1 port 101, the second shuttle valve 3 port 103, and the one-way throttle valve CT8 to enter the brake port PG to release the brake.
[0036] During the hoisting lowering phase, hydraulic oil enters through the second hydraulic oil inlet V2. A portion of the hydraulic oil passes through port 72 of the second shuttle valve and port 73 of the first shuttle valve, entering control port 111 of the hydraulic directional valve CT11. When the oil pressure at control port 111 exceeds the set working pressure of the hydraulic directional valve CT11, the hydraulic directional valve CT11 switches from its first working position to its second working position. Hydraulic oil at the pilot pressure port P1 can then enter the brake port PG through the hydraulic directional valve CT11, releasing the hoisting mechanism's brake. The path of the hydraulic oil from the pilot pressure port P1 to the brake port PG is the same as during the hoisting ascending phase and will not be described further here.
[0037] In this embodiment, a first damper D1 and a second damper D2 are also included. The first damper D1 is disposed between the second oil passage Z2 and the pilot oil port 53 of the balance valve, and the second damper D2 is disposed between the first damper D1 and the oil tank T.
[0038] In this embodiment, during the hoist lowering stage, some hydraulic oil enters the pilot port 53 of the balance valve to open the balance valve CT5, and some hydraulic oil enters the brake port PG to release the brake. The first damper D1 can control the flow rate of hydraulic oil entering the pilot port 53 of the balance valve, so that the opening time of the balance valve CT5 is later than the brake release time, thereby avoiding abnormal wear of the friction pads of the brake mechanism.
[0039] In this embodiment, the first damper D1 and the second damper D2 form a liquid bridge function to adjust the ratio of the opening pressure of the balance valve to the actual opening pressure in the system during the lowering stage, i.e., the control ratio. The relationship between the control ratio and the damping diameter is as follows: .
[0040] Continue to refer to Figure 1 The hoist hydraulic control system 1 further includes a solenoid valve directional control valve CT9. The solenoid valve directional control valve CT9 includes a solenoid valve 1 port 91, a solenoid valve 2 port 92, and a solenoid valve 3 port 93. The solenoid valve 1 port 91 is connected to the pilot pressure port P1, the solenoid valve 2 port 92 is connected to the brake port PG, and the solenoid valve 3 port 93 is connected to the oil tank T. When the solenoid valve CT9 is de-energized, the solenoid valve 3 port 93 is connected to the solenoid valve 2 port 92; when the solenoid valve CT9 is energized, the solenoid valve 1 port 91 is connected to the solenoid valve 2 port 92.
[0041] In this embodiment, the solenoid valve 2 port 92 and the brake port PG are provided with a second shuttle valve CT10 and a one-way throttle valve CT8, and the second shuttle valve 2 port 102 is connected to the solenoid valve 2 port.
[0042] In this embodiment, during the hoisting floating stage, the control solenoid directional valve CT9 is energized, and the solenoid valve 1 port 91 is connected to the solenoid valve 2 port 92. The hydraulic oil at the pilot pressure port P1 enters the brake port PG through the solenoid directional valve CT9, the second shuttle valve 2 port 102, the second shuttle valve 3 port 103, and the one-way throttle valve CT8, thereby releasing the brake of the hoisting mechanism.
[0043] Continue to refer to Figure 1 The hoist hydraulic control system 1 further includes a first check valve CT4, which includes a first inlet 41 and a first outlet 42. The first inlet 41 is connected to the first oil replenishment port S1, and the first outlet 42 is connected to the first hydraulic oil outlet C1 and the sequence valve inlet 21.
[0044] In this embodiment, the first oil replenishment port S1 can be connected to a pressure oil pipe. When needed, hydraulic oil is input through the first one-way valve CT4 into the first working port of the hydraulic motor, which can realize the motor reversal. For example, in the hoisting floating stage, after the heavy object touches the ground, if the wire rope is long at this time, hydraulic oil can be input into the first oil replenishment port S1 to make the motor reverse and retract the excess wire rope.
[0045] Continue to refer to Figure 1 The hoist hydraulic control system 1 further includes a second check valve CT6, which includes a second inlet 61 and a second outlet 62. The second inlet 61 is connected to the second oil replenishment port S2, and the second outlet 62 is connected to the second hydraulic oil outlet C2.
[0046] In this embodiment, during the lowering stage of the winch, hydraulic oil is input through the second oil replenishment port S2 to quickly replenish oil when the hydraulic motor sucks in air, thus avoiding the hydraulic motor sucking in air during operation and affecting its lifespan.
[0047] Continue to refer to Figure 1 The hoist hydraulic control system 1 also includes an overflow valve CT1, which is connected between the first oil circuit Z1 and the second oil circuit Z2.
[0048] In this embodiment, the set pressure of the relief valve CT1 is lower than the safe operating pressure of the hydraulic motor. When the oil pressure at the first hydraulic oil outlet C1 is too high, the relief valve CT1 can be opened to ensure system safety.
[0049] Accordingly, this utility model embodiment also provides a hoisting mechanism that adopts the above-mentioned hoisting hydraulic control system.
[0050] The hoisting mechanism adopts the aforementioned hoisting hydraulic control system, which has advantages such as lower energy consumption, more stable lowering of heavy objects, and easier speed control during the floating phase.
[0051] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the present invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.
Claims
1. A hoist hydraulic control system, characterized by, Comprising: a first oil path connecting a first hydraulic oil inlet and a first hydraulic oil outlet; a second oil path connecting a second hydraulic oil inlet and a second hydraulic oil outlet; a hydraulic motor comprising a first working port and a second working port, the first working port being connected with the first hydraulic oil outlet, the second working port being connected with the second hydraulic oil outlet; a balance valve provided on the first oil path, the balance valve comprising a balance valve 1 port, a balance valve 2 port and a balance valve pilot oil port, the balance valve 1 port being connected with the first hydraulic oil outlet, the balance valve 2 port being connected with the first hydraulic oil inlet, the balance valve pilot oil port being connected with the second oil path; a third oil path connecting the first oil path and the second oil path; a sequence valve provided on the third oil path, the sequence valve comprising a sequence valve inlet and a sequence valve outlet, the sequence valve inlet being connected with the first oil path; a proportional overflow valve provided on the third oil path, the proportional overflow valve comprising a proportional overflow valve inlet and a proportional overflow valve outlet, the proportional overflow valve inlet being connected with the sequence valve outlet, the proportional overflow valve outlet being connected with the second oil path.
2. The hydraulic control system for a hoist according to claim 1, wherein Further comprising a first shuttle valve, the first shuttle valve comprising a first shuttle valve 1 port, a first shuttle valve 2 port and a first shuttle valve 3 port, the first shuttle valve 1 port being connected with the first oil path, the first shuttle valve 2 port being connected with the second oil path.
3. The hydraulic control system for a hoist according to claim 2, wherein Further comprising a hydraulic control reversing valve, the hydraulic control reversing valve comprising a control 1 port, a reversing valve 2 port, a reversing valve 3 port and a reversing valve 4 port, the control 1 port being connected with the first shuttle valve 3 port, the reversing valve 2 port being connected with a pilot pressure port, the reversing valve 4 port being connected with an oil tank, the reversing valve 3 port being connected with a brake port.
4. The hydraulic control system for a hoist according to claim 3, wherein When the oil pressure at the control 1 port of the hydraulic control reversing valve is greater than the set working pressure of the hydraulic control reversing valve, the hydraulic control reversing valve is switched from a first working position of the hydraulic control reversing valve to a second working position of the hydraulic control reversing valve, the first working position being configured such that the reversing valve 4 port is in communication with the reversing valve 3 port, the second working position being configured such that the reversing valve 2 port is in communication with the reversing valve 3 port.
5. The hydraulic control system for a hoist according to claim 4, wherein Further comprising an electromagnetic reversing valve, the electromagnetic reversing valve comprising an electromagnetic valve 1 port, an electromagnetic valve 2 port and an electromagnetic valve 3 port, the electromagnetic valve 1 port being connected with the pilot pressure port, the electromagnetic valve 2 port being connected with the brake port, the electromagnetic valve 3 port being connected with the oil tank, when the electromagnetic reversing valve loses power, the electromagnetic valve 3 port is in communication with the electromagnetic valve 2 port; when the electromagnetic valve is powered, the electromagnetic valve 1 port is in communication with the electromagnetic valve 2 port.
6. The hydraulic control system for a hoist according to claim 5, wherein Further comprising a second shuttle valve, the second shuttle valve comprising a second shuttle valve 1 port, a second shuttle valve 2 port and a second shuttle valve 3 port, the first shuttle valve 1 port being connected with the reversing valve 3 port, the second shuttle valve 2 port being connected with the electromagnetic valve 2 port, the second shuttle valve 3 port being connected with the brake port.
7. The hydraulic control system for a hoist according to claim 6, wherein Further comprising a one-way throttle valve provided on a connecting oil path between the shuttle valve 3 port and the brake port.
8. The hydraulic control system for a hoist according to claim 1, wherein A first one-way valve is further included, which comprises a first inlet and a first outlet, the first inlet is connected with the first oil supplement port, and the first outlet is connected with the first hydraulic oil outlet and the sequence valve inlet.
9. The hydraulic control system for a hoist according to claim 1, wherein, A second one-way valve is further included, which comprises a second inlet and a second outlet, the second inlet is connected with the second oil supplement port, and the second outlet is connected with the second hydraulic oil outlet.
10. The hydraulic control system for a hoist according to claim 1, wherein An overflow valve is further included, which is connected between the first oil path and the second oil path.
11. The hydraulic control system for a hoist according to claim 3, wherein A first damper is further included, which is arranged between the second oil path and the balance valve pilot oil port.
12. The hydraulic control system for a hoist according to claim 11, wherein A second damper is further included, which is arranged between the first damper and the oil tank.
13. A winding mechanism characterized by, The winding mechanism adopts the winding hydraulic control system according to any one of claims 1 to 12.