A low-cost flexible and efficient double-motor drive stepless speed change hoist device

Abstract

The utility model relates to a kind of low-cost flexible efficient double-motor drive stepless speed change hoist device.It solves the technical problems such as high cost of existing heavy lifting,uncontrollable lifting speed or small lifting speed adjustment range etc..Including rack,both ends of rack upper side are respectively equipped with driving support,one side of two driving supports adjacent is equipped with built-in speed reducer,driving support side away from built-in speed reducer is equipped with hydraulic motor,hydraulic motor is connected with hydraulic system,hydraulic system has logic valve group and motor forward and reverse control group,logic valve group is connected with oil tank by valve control system,SK pressure reducing overflow valve is connected with brake inside built-in speed reducer,And one of hydraulic motor is variable motor,another hydraulic motor is fixed quantity motor.Advantage lies in: the combination form of fixed quantity motor and variable motor is more flexible,use two motors simultaneously to lift when heavy load,use one variable motor to lift when empty or light load,so as to improve work efficiency.

Description

Technical Field

[0001] This utility model belongs to the field of hoisting equipment technology, specifically relating to a low-cost, flexible and efficient dual-motor driven continuously variable speed hoisting device. Background Technology

[0002] Currently, with the continuous development of the hoisting field, the use of winches for hoisting has become increasingly mature. Winches have thus differentiated into those primarily driven by electric-mechanical mechanisms and those driven by hydraulic motors and reducers. In small, light-duty hoisting applications, a single motor with a reducer is often used. In heavy-duty hoisting applications, hydraulic reducers, with their higher power density, have become the mainstream hoisting solution. However, heavy-duty hoisting often requires controlling and matching the hoisting speed for objects of different weights, resulting in higher overall costs. Summary of the Invention

[0003] The purpose of this invention is to address the above-mentioned problems by providing a low-cost, flexible, and efficient dual-motor driven continuously variable speed winch.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: a low-cost, flexible, and efficient dual-motor driven continuously variable speed winch device, comprising a frame, drive supports at both ends of the upper side of the frame, an internal reducer on one side adjacent to the two drive supports, a winch drum between the two internal reducers, a hydraulic motor on the side of the drive support away from the internal reducer, the hydraulic motor being connected to a hydraulic system, the hydraulic system having a logic valve group and a motor forward / reverse control group, the logic valve group being connected to an oil tank through a valve control system, the hydraulic motor being connected to an SK pressure reducing overflow valve through an SH shuttle valve, the SK pressure reducing overflow valve being connected to a brake inside the internal reducer, and one of the hydraulic motors being a variable displacement motor and the other being a fixed displacement motor.

[0005] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the variable motor has ports A1 and B1, and the fixed motor has ports A2 and B2. Ports A1, B1, A2, and B2 are all connected to the oil tank.

[0006] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the logic valve group includes a CA1 two-way logic valve, a CA2 two-way logic valve, and a CA3 two-way logic valve.

[0007] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the motor forward and reverse rotation control group has an A motor forward and reverse rotation control port and a B motor forward and reverse rotation control port, and both the A motor forward and reverse rotation control port and the B motor forward and reverse rotation control port are connected to the SV speed switching solenoid valve through the SH shuttle valve.

[0008] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the forward and reverse control port of motor A is connected to the balance valve CB, the balance valve CB is connected to the A1 port of the variable motor, and the B1 port of the variable motor is connected to the oil tank through a valve control system.

[0009] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the forward and reverse control port of motor A is connected to the CA2 two-way logic valve, the CA2 two-way logic valve is connected to the B2 port of the fixed displacement motor, the B1 port of the fixed displacement motor is connected to the CA3 two-way logic valve, and the CA3 two-way logic valve is connected to the oil tank through a valve control system.

[0010] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the forward and reverse control port of motor B is connected to the CA3 two-way logic valve, the CA3 two-way logic valve is connected to the A2 port of the fixed displacement motor, and the B2 port of the fixed displacement motor is connected to the oil tank through the CB balance valve.

[0011] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable winch, the forward and reverse control port of motor B is connected to port B1 of the variable motor, and port A1 of the variable motor is connected to the oil tank through the CB balance valve.

[0012] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the hydraulic system has a replenishing valve group, which includes a CK1 replenishing check valve, a CK2 replenishing check valve, and a CK3 check valve.

[0013] In the aforementioned low-cost, flexible, and efficient dual-motor driven continuously variable speed winch, the Pil pilot control port of the variable motor is connected to the PSH pilot proportional pressure reducing valve, and the PSH pilot proportional pressure reducing valve is connected to the SV speed switching solenoid valve.

[0014] Compared with existing technologies, the advantages of this utility model are: 1. The device uses a combination of fixed-displacement and variable-displacement motors, which is more flexible. When under heavy load, two motors are used to lift simultaneously, while when under no-load or light load, one variable-displacement motor is used. This can improve work efficiency while reducing the purchase cost of hydraulic components and subsequent maintenance costs.

[0015] 2. The device's dual-motor design makes power transmission more flexible and efficient. Compared with traditional single-motor systems, it reduces energy loss, better adapts to different loads, and improves overall transmission efficiency.

[0016] 3. The device is simple in cost, the valve block of the valve group can be completed by machining, there is no need to cast the flow channel design, the production cycle is short, the hydraulic components can be assembled from mature cartridge valves, the replacement is strong, and the later maintenance and replacement costs are low. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of this utility model.

[0018] Figure 2 This is a schematic diagram of the low-to-medium speed, high-torque output mode of this utility model.

[0019] Figure 3 This is a schematic diagram of the high-speed, low-torque output mode of this utility model.

[0020] In the diagram: Frame 1, Drive support 11, Built-in reducer 12, Winch 13, Variable displacement motor 14, Fixed displacement motor 15, Valve control system 2, Oil tank 3. Detailed Implementation

[0021] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0022] like Figure 1-3 As shown, a low-cost, flexible, and efficient dual-motor driven continuously variable speed winch includes a frame 1. Drive supports 11 are respectively provided at both ends of the upper side of the frame 1. An internal reducer 12 is provided on the adjacent side of the two drive supports 11. A winch drum 13 is provided between the two internal reducers 12. A hydraulic motor is provided on the side of the drive supports 11 away from the internal reducers 12. The hydraulic motor is connected to a hydraulic system. The hydraulic system has a logic valve group and a motor forward / reverse control group. The logic valve group is connected to an oil tank 3 through a valve control system 2. The hydraulic motor is connected to an SK pressure-reducing relief valve through an SH shuttle valve. The SK pressure-reducing relief valve is connected to a brake inside the internal reducer 12. One of the hydraulic motors is a variable displacement motor 14, and the other hydraulic motor is a fixed displacement motor 15. Dual hydraulic motors are matched with a reducer on each side to achieve lifting with the same torque and speed. One side is driven by a hydraulically controlled variable motor 14 (HD2 or HD2D) and the reducer is driven by a fixed displacement motor 15 of the same displacement. The maximum displacement of the two motors is exactly the same, and the specifications and reduction ratio of the built-in reducer 12 are also exactly the same.

[0023] The variable displacement motor 14 has ports A1 and B1, and the fixed displacement motor 15 has ports A2 and B2. Ports A1, B1, A2 and B2 are all connected to the oil tank 3.

[0024] Specifically, the logic valve group includes CA1 two-way logic valve, CA2 two-way logic valve and CA3 two-way logic valve.

[0025] Meanwhile, the motor forward and reverse rotation control group has a forward and reverse rotation control port for motor A and a forward and reverse rotation control port for motor B, and both the forward and reverse rotation control ports for motor A and motor B are connected to the speed switching solenoid valve via the SH shuttle valve.

[0026] Furthermore, the forward and reverse control port of motor A is connected to the balance valve CB, the balance valve CB is connected to port A1 of variable motor 14, and port B1 of variable motor 14 is connected to oil tank 3 through valve control system 2.

[0027] Furthermore, the forward and reverse control port of motor A is connected to the CA2 two-way logic valve, the CA2 two-way logic valve is connected to the B2 port of the fixed displacement motor 15, the B1 port of the fixed displacement motor 15 is connected to the CA3 two-way logic valve, and the CA3 two-way logic valve is connected to the oil tank 3 through the valve control system 2.

[0028] Clearly, the forward and reverse control port of motor B is connected to the CA3 two-way logic valve, the CA3 two-way logic valve is connected to the A2 port of the fixed displacement motor 15, and the B2 port of the fixed displacement motor 15 is connected to the oil tank 3 through the CB balance valve.

[0029] Furthermore, the forward and reverse control port of motor B is connected to port B1 of variable motor 14, and port A1 of variable motor 14 is connected to oil tank 3 through CB balance valve.

[0030] Specifically, the hydraulic system has a replenishing valve assembly, which includes a CK1 replenishing check valve, a CK2 replenishing check valve, and a CK3 check valve.

[0031] In addition, the Pil pilot control port of the variable motor 14 is connected to the PSH pilot proportional pressure reducing valve, which is connected to the SV speed switching solenoid valve. The variable motor 14 is a motor with HD2D hydraulic variable displacement control. That is, when a pilot signal is applied to the Pil pilot control port, the displacement of the variable motor 14 will proportionally change from a large displacement to a small displacement. This can increase the operating speed of the variable motor 14 and reduce the output torque. When the output torque is the same, the smaller the displacement of the variable motor 14, the higher the pressure required for the variable motor 14. When the pressure is high enough, the pressure cut-off valve inside the variable motor 14 will be activated under the pressure to switch the motor displacement from a small displacement to a large displacement. In the initial state, when there is no pilot oil or the pilot oil pressure is low at the Pil pilot control port, the initial state of the variable motor 14 is a large displacement, low speed, and high torque output state.

[0032] like Figure 2 As shown, the principle of low-speed, high-torque output mode is as follows: Regardless of whether oil is supplied through the forward / reverse control port of motor A and returned through the forward / reverse control port of motor B, or vice versa, the only difference between the two oil supply methods is the direction of motor rotation. The high-pressure oil passing through the SH shuttle valve and then through the SK pressure reducing and overflow valve will deliver the reduced pressure to the internal brake of the built-in reducer 12, causing the brake to open. When oil returns through both the forward and reverse control ports of motors A and B, the brake will be released under the action of the internal disc spring or spring. The hydraulic oil discharged from the brake is depressurized through the D brake return damper. The magnitude of the damping determines the braking time of the built-in reducer 12. The larger the damping orifice, the faster the braking. However, braking too fast can easily cause the internal brake of the built-in reducer 12 to burn out. The release of brake oil will automatically lock the output shaft of the motor, and the winch reducer will automatically stop to achieve safety self-locking.

[0033] When the SV speed switching solenoid valve is de-energized, the high-pressure oil passes through the SH shuttle valve and then through the SV speed switching solenoid valve. The CA1 two-way logic valve is closed, and the CA2 / CA3 logic valves are open. Therefore, if oil enters the forward / reverse control port of motor A, the high-pressure oil from the forward / reverse control port of motor A will pass through the CB balance valve and then flow in two parallel paths. One path first passes through port A1 of variable motor 14 and then through port B1, directly returning to valve control system 2 and then to oil tank 3. The other path passes through the CA2 two-way logic valve and then through port B2 to enter the fixed displacement motor 15. At this time, the CA3 two-way logic valve is open, and the return oil from the motor returns to valve control system 2 through the CA3 two-way logic valve and finally to oil tank 3. In this state, the outlet of the PSH pilot proportional pressure reducing valve is connected to the Pil pilot control port of the variable motor 14. However, since the oil inlet of the PSH pilot proportional pressure reducing valve is connected to the return oil of the SV speed switching solenoid valve, the PSH has not been activated. Therefore, the variable motor 14 is always in the initial state, that is, the variable motor 14 is in the large displacement state. At this time, it is equivalent to two motors working in parallel.

[0034] Similarly, when oil enters through the forward / reverse control port of motor B and exits through the forward / reverse control port of motor A, the hydraulic oil from the forward / reverse control port of motor B will also flow in two parallel paths. One path passes through the CA3 two-way logic valve, then through port A2 to reach the fixed displacement motor 15. The oil from the fixed displacement motor 15 is output through port B2, and returns to the oil tank 3 through the CB balance valve. The other path passes through port B1 of the variable displacement motor 14, then returns from port A1 of the variable displacement motor 14 through the CB balance valve to the oil tank 3. Therefore, when the SV speed switching solenoid valve is de-energized, both the variable displacement motor 14 and the fixed displacement motor 15 operate at the same displacement and in a high displacement state, which is a low-speed, high-torque operating mode. Changing the oil inlet direction of the forward / reverse control port of motor A or motor B can switch the rotation direction of the hydraulic motor. When oil enters through the forward / reverse control port of motor A, it is the lifting direction; when oil enters through the forward / reverse control port of motor B, it is the lowering direction of the winch. The CB balance valve allows oil to enter the forward and reverse control port of motor A without resistance. When oil enters the forward and reverse control port of motor B and returns oil to the forward and reverse control port of motor A, it balances and stabilizes the descent speed of the heavy object, preventing overspeed during descent and avoiding unsafe lifting accidents.

[0035] like Figure 3 As shown, the principle of high-speed, low-torque output mode is as follows: Regardless of whether oil is supplied to the forward / reverse control port of motor A or motor B, when the SV speed switching solenoid valve is energized, the CA1 two-way logic valve opens, while the CA2 / CA3 two-way logic valves close. The fixed displacement motor 15 is in a free-running state, and the pressure at ports A2 / B2 is consistent. During idling, oil replenishment at port T is completed by the CK1 oil replenishment check valve. Simultaneously, the high-pressure oil from either the forward / reverse control port of motor A or motor B passes through the SH shuttle valve and then through the SV speed switching solenoid valve. The inlet of the PSH pilot proportional pressure reducing valve is under high pressure, and the PSH pilot proportional pressure reducing valve is activated. When an electrical signal is given, pilot oil of a certain pressure is output to the Pil pilot control port of the variable displacement motor 14, which allows the motor to change from a large displacement to a small displacement. That is, at this time, the drive mode of the built-in reducer 12 changes from two motors to being driven entirely by one variable displacement motor 14, while the other motor is functionally disabled and in a free-running state without outputting torque.

[0036] During lifting, oil enters through the forward / reverse control port of motor A and passes through the CB balance valve. Since the CA2 two-way logic valve is closed, the oil from the forward / reverse control port of motor A only flows to the variable motor 14. Therefore, with the flow rate and displacement remaining constant, the speed is twice that of the original two-motor drive mode, and the maximum torque becomes 0.5 times that of the original dual-motor drive mode. The hydraulic oil output from the variable motor 14 returns directly to the oil tank 3 through port B1. When a higher lifting speed is required, such as in light-load or rapid lifting with an empty hook, an electrical signal is sent to the PSH pilot proportional pressure reducing valve. The larger the electrical signal, the higher the output pilot pressure, thus reducing the motor displacement. With the same input flow rate, the motor speed is higher, resulting in a higher lifting speed. When the lifting cannot reach the desired load, the internal pressure of the motor automatically senses and cuts off the pressure, switching the motor to a high-displacement state. Alternatively, an external SW pressure switch signal can be used to switch to a dual-motor high-torque lifting state.

[0037] During descent, oil enters through the forward / reverse control port of motor B and returns through the forward / reverse control port of motor A. At this time, the CA3 two-way logic valve is closed, and the pilot oil of the CB balance valve opens the CB balance valve. The fixed displacement motor 15 remains in a passive idling state. The oil flow entering through the forward / reverse control port of motor B is no longer divided into two, but is directly input to the variable displacement motor 14 through port B1. The output flow of the variable displacement motor 14 returns to the oil tank 3 through port A1 and the CB balance valve. If the descent speed needs to be increased, such as in light load or empty hook descent conditions requiring rapid descent, the PSH pilot proportional pressure reducing valve remains active. When an electrical signal is given, the PSH pilot proportional pressure reducing valve outputs a higher pressure pilot signal, and the variable displacement motor 14 will switch to a small displacement working mode. At this time, under the same input flow, the motor speed will increase. The CK1 / CK2 oil replenishment check valve can replenish oil to the fixed displacement motor 15 and the variable displacement motor 14 under any descent condition to prevent insufficient oil supply caused by motor overspeed descent, which could lead to unstable speed or cavitation.

[0038] Therefore, in the high-speed, low-torque output mode, the fixed-displacement motor 15 is in floating or passive idling operation. At this time, the maximum torque of the high-speed, low-torque output is 0.5 times that of the low-speed, high-torque lifting mode. Under this torque condition, the lifting speed of the winch can be steplessly adjusted, thereby improving the overall lifting / lowering efficiency.

[0039] The principle of this embodiment is as follows: The dual-motor drive of a single winch drum 13 provides a tremendous driving force unmatched by a single motor, making it suitable for heavy-duty lifting and traction operations. It allows for flexible switching between operating modes: Light-load high-speed mode: only the variable motor 14 operates, achieving high-speed operation and improved efficiency by reducing its displacement; Heavy-load low-speed mode: both motors operate simultaneously, providing maximum torque for smooth and powerful lifting of heavy loads. Simultaneously, the displacement of the variable motor 14 is steplessly adjusted via the PSH pilot proportional pressure reducing valve, enabling smooth and continuous speed control between maximum and minimum speeds without shift shock. The proportional control allows for fine-tuning of the speed, achieving precise matching between heavy-load low-speed and light-load high-speed operation, enabling both precise operation and high efficiency.

[0040] The specific embodiments described herein are merely illustrative examples illustrating the spirit of this utility model. Those skilled in the art to which this utility model pertains may make various modifications or additions to the described specific embodiments or use similar methods to substitute them, without departing from the spirit of this utility model or exceeding the scope defined by the appended claims.

[0041] Although this document frequently uses terms such as frame 1, drive support 11, built-in reducer 12, winch drum 13, variable displacement motor 14, fixed displacement motor 15, valve control system 2, and oil tank 3, the possibility of using other terms is not excluded. These terms are used merely for the convenience of describing and explaining the essence of this utility model; interpreting them as any additional limitation would contradict the spirit of this utility model.

Claims

1. A low-cost, flexible, and efficient dual-motor driven continuously variable speed winch device, comprising a frame (1), wherein drive supports (11) are respectively provided at both ends of the upper side of the frame (1), a built-in reducer (12) is provided on the adjacent side of the two drive supports (11), a winch drum (13) is provided between the two built-in reducers (12), and a hydraulic motor is provided on the side of the drive supports (11) away from the built-in reducers (12), characterized in that, The hydraulic motor is connected to the hydraulic system, which has a logic valve group and a motor forward and reverse control group. The logic valve group is connected to the oil tank (3) through the valve control system (2). The hydraulic motor is connected to the SK pressure relief valve through the SH shuttle valve. The SK pressure relief valve is connected to the brake inside the built-in reducer (12). One of the hydraulic motors is a variable motor (14), and the other hydraulic motor is a fixed motor (15).

2. The low-cost, flexible, and efficient dual-motor driven continuously variable speed winch device according to claim 1, characterized in that, The variable motor (14) has ports A1 and B1, and the fixed motor (15) has ports A2 and B2. Ports A1, B1, A2 and B2 are all connected to the oil tank (3).

3. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 2 wherein, The logic valve group includes CA1 two-way logic valve, CA2 two-way logic valve and CA3 two-way logic valve.

4. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 3 wherein, The motor forward and reverse rotation control group has a motor A forward and reverse rotation control port and a motor B forward and reverse rotation control port, and both the motor A forward and reverse rotation control port and the motor B forward and reverse rotation control port are connected to the SV speed switching solenoid valve through the SH shuttle valve.

5. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 4 wherein, The forward and reverse control port of motor A is connected to the balance valve CB. The balance valve CB is connected to port A1 of variable motor (14). Port B1 of variable motor (14) is connected to oil tank (3) through valve control system (2).

6. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 4 wherein, The forward and reverse control port of motor A is connected to the CA2 two-way logic valve. The CA2 two-way logic valve is connected to the B2 port of the fixed displacement motor (15). The B1 port of the fixed displacement motor (15) is connected to the CA3 two-way logic valve. The CA3 two-way logic valve is connected to the oil tank (3) through the valve control system (2).

7. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 4 wherein, The forward and reverse control port of motor B is connected to the CA3 two-way logic valve, the CA3 two-way logic valve is connected to the A2 port of the fixed displacement motor (15), and the B2 port of the fixed displacement motor (15) is connected to the oil tank (3) through the CB balance valve.

8. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 4 wherein, The forward and reverse control port of motor B is connected to port B1 of variable motor (14), and port A1 of variable motor (14) is connected to oil tank (3) through CB balance valve.

9. A low cost flexible and efficient dual motor drive infinitely variable speed hoist as claimed in claim 1 wherein, The hydraulic system has a replenishing valve assembly, which includes a CK1 replenishing check valve, a CK2 replenishing check valve, and a CK3 check valve.

10. A low-cost, flexible, and efficient dual-motor driven continuously variable speed winch device according to claim 1, characterized in that, The Pil pilot control port of the variable motor (14) is connected to the PSH pilot proportional pressure reducing valve, and the PSH pilot proportional pressure reducing valve is connected to the SV speed switching solenoid valve.

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