Hydraulic system for improving frequent positive and negative rotation reliability of gear motor

Abstract

The utility model relates to a hydraulic system for improving the reliability of frequent positive and negative rotation of a gear motor. The hydraulic system comprises a positive and negative rotation motor, a reversing valve, a secondary overflow valve and an oil way system for connecting all parts, a first internal oil way and a second internal oil way are arranged in the secondary overflow valve, the first internal oil way is communicated with the second internal oil way, and preset pressure threshold values of the first internal oil way and the second internal oil way are different. The gear motor solves the technical problems that in the prior art, a hydraulic system is large in impact, key parts are prone to being damaged, and the reliability of a whole machine is poor in the frequent forward and reverse rotation process of the gear motor.

Description

Technical Field

[0001] This invention relates to a hydraulic system that increases the reliability of a gear motor during frequent forward and reverse rotation. Background Technology

[0002] In existing hydraulic system technology, the forward and reverse rotation of a gear motor is often used to drive the fan, achieving forward and reverse rotation to meet the switching needs of the fan's blowing direction under different working conditions. This technology is simple in structure and responds quickly, and is widely used in engineering machinery, agricultural equipment, and some industrial equipment. Its main principle is to adjust the flow of hydraulic oil through a hydraulic control circuit, causing the output shaft of the gear motor to rotate in the forward or reverse direction, thereby driving the fan to switch between forward and reverse rotation.

[0003] However, in practical applications, this method of relying on gear motors to frequently switch between forward and reverse directions has significant drawbacks. Especially during the instant of reverse switching, a large impact pressure is generated within the hydraulic system. This not only causes pressure fluctuations and shocks to the system pipelines and connecting components, but may also subject critical components such as the hydraulic pump and gear motor to unnecessary load shocks, thereby affecting their service life and operational stability. Furthermore, the mechanical shocks caused by frequent switching may also lead to increased operating noise, higher energy consumption, and decreased control precision, reducing overall machine reliability and maintenance efficiency.

[0004] Therefore, in order to address the above-mentioned shortcomings, it is necessary to improve the design of this type of fan-driven hydraulic system to enhance the stability of system operation and the durability of key components, thereby enhancing the overall reliability and safety of the product. Utility model content:

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a hydraulic system that increases the reliability of gear motors during frequent forward and reverse rotation.

[0006] A hydraulic system for increasing the reliability of a gear motor in frequent forward and reverse rotation includes a forward and reverse motor, a directional valve, a two-stage relief valve, and an oil circuit system connecting the various components. The two-stage relief valve has a first internal oil circuit and a second internal oil circuit, which are connected to each other. The preset pressure thresholds of the first internal oil circuit and the second internal oil circuit are different.

[0007] Furthermore, the directional valve is a three-position four-way directional valve.

[0008] Furthermore, the three-position four-way directional valve includes a first oil port, a second oil port, a third oil port, a fourth oil port, and a first station, a second station, and a third station;

[0009] First station: The first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port;

[0010] Second workstation: The first oil port, the second oil port, the third oil port, and the fourth oil port are interconnected;

[0011] Third station: The first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port.

[0012] Furthermore, the oil circuit system includes an oil outlet circuit, a return circuit, a first oil circuit, and a second oil circuit. One end of the return circuit and the oil outlet circuit are respectively connected to the first and second oil ports of a three-position four-way directional valve. One end of the first and second oil circuits are respectively connected to the third and fourth oil ports. The forward and reverse motors are connected to the other ends of the first and second oil circuits. A two-stage relief valve is connected between the oil outlet circuit and the return circuit.

[0013] Furthermore, the forward and reverse motors are connected to the oil tank via a separate oil return circuit.

[0014] Beneficial effects: Compared with the prior art, the present invention has the following advantages:

[0015] The hydraulic system effectively controls hydraulic shocks during frequent forward and reverse rotation of the motor by incorporating a two-stage relief valve with a buffer function. The two-stage relief valve includes a first internal oil circuit and a second internal oil circuit that are interconnected. The first internal oil circuit is set with a lower primary pressure threshold. When the system pressure rises to this threshold at the initial stage of motor commutation, the first oil circuit opens first to initiate primary pressure relief, mitigating the instantaneous impact during the pressure rise.

[0016] If the system experiences a significant impact or the pressure continues to rise above the threshold, the second internal oil circuit will also open, further increasing the pressure relief flow and thus increasing the energy release. This ensures rapid pressure balance and minimizes the mechanical impact on the motor and the entire system. This "staged, step-by-step pressure relief" mechanism makes the reversing process smoother and has adaptive capabilities, automatically adjusting the pressure relief strategy according to the pressure level.

[0017] Compared to traditional single-stage overflow solutions, this design exhibits superior buffering capacity and system stability when dealing with frequent reversals or sudden load changes, thereby improving the reliability and safety of the hydraulic system. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of a hydraulic system;

[0019] Figure 2 This is a schematic diagram of a reversing valve;

[0020] Figure 3 This is a schematic diagram of a two-stage relief valve;

[0021] In the diagram, 1 is the oil outlet, 2 is the oil return, 3 is the secondary relief valve, 4 is the directional valve, 5 is the second oil passage, 6 is the first oil passage, 7 is the first station, 8 is the second station, 9 is the third station, 10 is the first oil port, 11 is the second oil port, 12 is the third oil port, 13 is the fourth oil port, 14 is the second internal oil passage, and 15 is the first internal oil passage. Detailed Implementation

[0022] To enhance understanding of this utility model, the present utility model will be further described in detail below with reference to the embodiments and accompanying drawings. These embodiments are only used to explain the present utility model and do not constitute a limitation on the scope of protection of the present utility model.

[0023] A hydraulic system for increasing the reliability of a gear motor in frequent forward and reverse rotation includes a forward and reverse motor, a reversing valve 4, a secondary relief valve 3, and an oil circuit system connecting the various components. The secondary relief valve 3 has a first internal oil circuit 15 and a second internal oil circuit 14, which are connected to each other. The preset pressure thresholds of the first internal oil circuit 15 and the second internal oil circuit 14 are different.

[0024] The hydraulic system in this patent achieves effective control of hydraulic shock during frequent forward and reverse rotation of the motor by setting a two-stage relief valve 3 with a buffer function. The two-stage relief valve 3 includes a first internal oil passage 15 and a second internal oil passage 14 that are interconnected. The first internal oil passage 15 is set with a lower primary pressure threshold. When the system pressure rises to this threshold at the initial stage of motor reversal, the first oil passage 15 opens first to initiate primary pressure relief and alleviate the instantaneous impact during the pressure rise.

[0025] If the system experiences a significant impact or the pressure continues to rise above the threshold, the second internal oil circuit 14 will also open, further increasing the pressure relief flow and thus increasing the energy release. This ensures rapid pressure balance and minimizes the mechanical impact on the motor and the entire system. This "staged, step-by-step pressure relief" mechanism makes the reversing process smoother and has adaptive capabilities, automatically adjusting the pressure relief strategy according to the pressure level.

[0026] Compared to traditional single-stage overflow solutions, this design exhibits superior buffering capacity and system stability when dealing with frequent reversals or sudden load changes, thereby improving the reliability and safety of the hydraulic system.

[0027] By incorporating two internal oil circuits with different pressure thresholds within the secondary relief valve 3, the system can adaptively adjust the pressure according to changes in flow direction when the motor frequently reverses direction. This enhances the system's adaptability to pressure fluctuations, thereby improving the stability and reliability of the motor under frequent forward and reverse operation. This structure not only improves the commutation response speed but also effectively avoids motor shock or jamming caused by unstable pressure. Furthermore, through differentiated threshold settings, the system can more accurately release energy under different flow conditions, improving energy efficiency and extending the system's service life.

[0028] In one possible implementation, the reversing valve 4 is a three-position four-way reversing valve 4.

[0029] In this embodiment, a three-position four-way directional control valve 4 is used as the core control component. Compared with a conventional two-position directional control valve 4, the three-position four-way directional control valve 4 has three working positions and four oil ports, enabling more flexible oil flow control. By switching between the three positions, the forward, reverse, and neutral states of the motor can be controlled separately, thus adapting to more complex operating requirements. During frequent forward and reverse rotation, the three-position four-way directional control valve 4 can effectively reduce the impact during directional switching and improve directional stability.

[0030] By incorporating a three-position four-way directional valve 4, the directional efficiency and flow control accuracy of the hydraulic system during frequent forward and reverse rotation of the motor can be significantly improved. Its neutral position allows the system to enter a pressure relief or pressure holding state when motor operation is not required, enhancing energy efficiency and safety. Simultaneously, the three-position structure provides superior pressure balancing capabilities, reducing pressure fluctuations caused by directional changes, thereby extending equipment life and reducing the frequency of failures.

[0031] In one possible implementation, the three-position four-way directional valve 4 includes a first oil port 10, a second oil port 11, a third oil port 12, a fourth oil port 13, and a first station 7, a second station 8, and a third station 9.

[0032] First station 7: First oil port 10 is connected to third oil port 12, and second oil port 11 is connected to fourth oil port 13;

[0033] Second station 8: First oil port 10, second oil port 11, third oil port 12, and fourth oil port 13 are interconnected;

[0034] Third station 9: First oil port 10 is connected to fourth oil port 13, and second oil port 11 is connected to third oil port 12.

[0035] The three-position four-way directional valve 4 achieves different oil circuit switching functions through three working positions. In the first position 7, hydraulic oil flows from the first port 10 to the third port 12, while the second port 11 flows to the fourth port 13, corresponding to the forward operation of the motor. In the third position 9, the oil flow direction is opposite to that of the first position 7, corresponding to the reverse operation of the motor. In the second position 8, i.e., the neutral position, the four ports are interconnected, forming a fully open state, which helps to balance pressure and relieve system pressure under no-load conditions, avoiding hydraulic shock.

[0036] This structure gives the directional control valve 4 greater functional flexibility and control precision, allowing the system to switch and stop the motor without cutting off the main oil supply. Especially in frequent switching applications, the full-port neutral position effectively avoids shocks and damage caused by momentary flow interruptions, improving switching stability and motor life. At the same time, the simple port layout facilitates integration into standard hydraulic modules, enhancing the system's compactness.

[0037] In one possible implementation, the oil circuit system includes an oil outlet 1, an oil return 2, a first oil circuit 6, and a second oil circuit 5. One end of the oil return 2 and the oil outlet 1 are respectively connected to the first oil port 10 and the second oil port 11 of the three-position four-way directional valve 4. One end of the first oil circuit 6 and the second oil circuit 5 are respectively connected to the third oil port 12 and the fourth oil port 13. The forward and reverse motors are connected to the other ends of the first oil circuit 6 and the second oil circuit 5. The two-stage overflow valve 3 is connected between the oil outlet 1 and the oil return 2.

[0038] The hydraulic system is structurally designed by configuring a first oil passage 6 and a second oil passage 5 between the directional valve 4 and the motor. These passages control the oil input and output in the forward and reverse directions of the motor, respectively. Simultaneously, the return oil passage 2 and the outlet oil passage 1 are connected to the directional valve 4 to achieve the main oil flow circulation path. A secondary relief valve 3 is installed between the outlet oil passage 1 and the return oil passage 2. During system reversal or in case of abnormal load, it selectively releases pressure based on different internal pressure threshold channels, maintaining stable system operation and protecting components from impact damage.

[0039] By rationally constructing the hydraulic circuit system, multiple functions such as motor drive, reversing, and pressure relief are integrated, improving the overall responsiveness and reliability of the hydraulic system. The addition of the secondary relief valve 3 significantly enhances the system's ability to cope with frequent reversing and pressure shocks. This structure facilitates modular layout, reducing system complexity and installation costs. Through precise design of the hydraulic circuit path, efficient energy transmission and pressure regulation for bidirectional motor control are achieved.

[0040] In one possible implementation, the forward and reverse motor is connected to the oil tank via a separate return oil circuit 2.

[0041] In this embodiment, the return oil section of the forward and reverse motor no longer shares the main return oil circuit 2 with the reversing valve 4. Instead, an independent return oil circuit 2 is provided to directly lead the motor's return oil back to the oil tank. This independent return oil circuit 2 is a dedicated return oil circuit 2, which can avoid interference and back pressure effects during the system's return oil process. After the hydraulic oil drives the motor to run via the first oil circuit 6 or the second oil circuit 5, its return oil flow flows back to the oil tank via this independent return oil circuit 2, forming a stable oil circulation system.

[0042] By providing the motor with an independent return oil path, the system's return oil back pressure is significantly reduced, improving the motor's commutation response speed and enhancing operational stability. Simultaneously, it avoids interference and energy loss caused by multiple components sharing the same return oil path, thus improving the overall efficiency of the hydraulic system. Furthermore, the independent return oil structure reduces oil temperature rise, improves system heat dissipation, and reduces the backflow and accumulation of impurities in the pipeline, helping to extend the service life of system components.

[0043] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A hydraulic system for increasing the reliability of frequent forward and reverse rotation of a gear motor, characterized by, It includes a forward and reverse motor, a reversing valve, a two-stage relief valve, and an oil circuit system connecting the various components. The two-stage relief valve has a first internal oil circuit and a second internal oil circuit, which are connected to each other. The preset pressure thresholds of the first internal oil circuit and the second internal oil circuit are different.

2. The hydraulic system of claim 1, wherein, The aforementioned directional valve is a three-position four-way directional valve.

3. The hydraulic system of claim 2, wherein, The three-position four-way directional valve includes a first oil port, a second oil port, a third oil port, a fourth oil port, and a first working position, a second working position, and a third working position; First station: The first oil port is connected to the third oil port, and the second oil port is connected to the fourth oil port; Second workstation: The first oil port, the second oil port, the third oil port, and the fourth oil port are interconnected; Third station: The first oil port is connected to the fourth oil port, and the second oil port is connected to the third oil port.

4. The hydraulic system of claim 3, wherein, The oil circuit system includes an oil outlet circuit, an oil return circuit, a first oil circuit, and a second oil circuit. One end of the oil return circuit and the oil outlet circuit are respectively connected to the first and second oil ports of a three-position four-way directional valve. One end of the first and second oil circuits are respectively connected to the third and fourth oil ports. The forward and reverse motors are connected to the other ends of the first and second oil circuits. A two-stage relief valve is connected between the oil outlet circuit and the oil return circuit.

5. The hydraulic system of claim 4, wherein, The forward and reverse motors are connected to the oil tank via a separate return oil circuit.

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