A multi-stage speed regulation control method for the main machine of a mobile vertical shaft impact crusher station

Abstract

The present invention discloses a multi-stage speed regulation control method for the main engine of a mobile vertical shaft impact crusher station. By using the electro-hydraulic proportional valve of the main engine pump, the engine, and the electro-hydraulic proportional valve of the main engine motor, the main engine is subjected to successive approximation multi-stage speed regulation control, which can efficiently, reliably, and precisely adjust the rotational speed of the main engine, keep the equipment always in the state of maximum production capacity and the most comfortable working condition, reduce the probability of equipment failure, and thus bring the maximum economic benefits to customers while increasing the service life of the equipment.

Description

Technical Field

[0001] The present invention relates to the technical field of the main engine speed regulation of a mobile vertical shaft impact crusher, and specifically to a multi-stage speed regulation control method for the main engine of a mobile vertical shaft impact crusher. Background Art

[0002] With the increasing demand for construction sand in China's social and economic construction, natural sand can no longer meet the needs of engineering construction, and the application of manufactured sand is becoming more and more extensive. As a sand-making equipment, the vertical shaft impact crusher has also been widely used. The mobile vertical shaft impact crusher is a mining and mechanical equipment for crushing rocks and making sand, which is often used in the mining crushing and sand-making links. It has the characteristics of stable and reliable operation, convenient maintenance, and high sand-making rate. It is especially suitable for stone shaping and the production of manufactured sand, and is widely used in the fine crushing operations of industries such as hydropower, construction, cement, and metal mines.

[0003] The impact speed is one of the main working parameters of the vertical shaft impact crusher. Based on the research on it, the working speed of the main shaft can be reasonably selected. The appropriate main engine speed can improve the working efficiency and energy conservation and consumption reduction at the same time, bringing the greatest economic benefits to users.

[0004] At present, there are many methods for regulating the main engine speed of a mobile vertical shaft impact crusher, including: (1) controlling the current of the solenoid valve of the main engine pump. The main engine pump is directly driven by the engine and powered by the engine. This pump is a variable displacement pump, and the opening of the swash plate of the main engine pump can be adjusted by adjusting the current of the solenoid valve to realize the adjustment of the displacement of the main engine pump; (2) adjusting the main engine speed by adjusting the current of the electro-hydraulic proportional valve. When the flow rate of the main engine pump remains unchanged, the main engine speed is inversely proportional to the displacement of the main engine motor, that is, the larger the displacement of the main engine motor, the lower the main engine speed, and the smaller the displacement of the main engine motor, the higher the main engine speed. (3) adjusting the main engine speed by adjusting the engine speed. Theoretically, the flow rate of the main engine pump is proportional to the displacement and speed. Therefore, it is hoped to increase the flow rate of the main engine pump by increasing the speed of the main engine pump. The main engine pump is directly driven by the engine. Therefore, increasing the engine speed can increase the speed of the main engine pump, and then increase the flow rate of the main engine pump. The main engine pump drives the main engine motor, and increasing the flow rate of the main engine pump can increase the speed of the main engine motor.

[0005] The above three main engine speed regulation methods are often used separately at present, or are adjusted on site by the staff according to experience. This method often cannot meet the requirements of the main engine speed. Even if the speed requirement is met, it may also cause some systems to be in an overloaded working state, resulting in a large increase in fuel consumption and a decrease in the energy utilization cost performance, which does not meet the requirements of green and low-carbon, and when the system load is too large, it will cause problems such as the hydraulic system pressure exceeding the limit. Summary of the Invention

[0006] To solve the defects existing in the above-mentioned prior art, the present invention provides a multi-stage speed regulation control method for the main engine of a mobile vertical shaft impact crusher station. By using the main engine pump electro-hydraulic proportional valve, the engine, and the main engine motor electro-hydraulic proportional valve, the main engine is controlled by successive approximation multi-stage speed regulation, which can efficiently, reliably, and precisely adjust the main engine speed.

[0007] The technical solution adopted by the present invention: A multi-stage speed regulation control method for the main engine of a mobile vertical shaft impact crusher station, comprising the following steps:

[0008] S1: Initialize the system settings, including: the maximum working pressure of the hydraulic system, the set value of the main engine speed, the maximum working current of the main engine pump solenoid valve, the minimum working current of the main engine pump solenoid valve, the minimum working speed of the engine, the maximum working speed of the engine, the minimum working current of the main engine motor electro-hydraulic proportional valve, the maximum working current of the main engine motor electro-hydraulic proportional valve, the minimum working speed of the main engine, and the maximum working speed of the main engine;

[0009] S2: Collect system data, including: the working current signal of the main engine pump solenoid valve, the working current signal of the electro-hydraulic proportional valve, the hydraulic system pressure signal, the main engine speed signal, and the engine speed signal;

[0010] S3: Judge whether the working pressure of the hydraulic system reaches the set value according to the hydraulic system pressure signal. If it reaches or exceeds the set value, return to step S2; otherwise, proceed to step S4;

[0011] S4: Judge whether the main engine speed is less than the set value according to the main engine speed signal. If it is less than the set value, enter step S5 for main engine speed increase control; if it is greater than the set value, enter step S8 for main engine speed decrease control;

[0012] S5: Judge whether the working current of the main engine pump solenoid valve reaches the upper limit according to the working current signal of the main engine pump solenoid valve. If it does not reach the upper limit, control the current of the main engine pump solenoid valve to rise and return to step S2; if the working current of the main engine pump solenoid valve reaches the upper limit, it means that only adjusting the displacement of the main engine pump cannot meet the demand for increasing the main engine speed, and enter step S6;

[0013] S6: Judge whether the engine speed reaches the upper limit according to the engine speed signal. If it does not reach the upper limit, control the engine speed to rise and then return to step S2; if the engine speed reaches the upper limit, it means that the engine speed reaching the upper limit can no longer meet the demand for increasing the main engine speed, and enter step S7;

[0014] S7: Judge whether the current of the main engine motor proportional valve reaches the lower limit according to the working current signal of the electro-hydraulic proportional valve. If it does not reach the lower limit, control the current of the main engine motor electro-hydraulic proportional valve to decrease and then return to step S2;

[0015] S8: Determine whether the current of the proportional valve of the main engine motor has reached the upper limit according to the working current signal of the electro-hydraulic proportional valve. If not, control to increase the current of the electro-hydraulic proportional valve of the main engine motor, and then return to step S2; if the current of the proportional valve of the main engine motor has reached the upper limit, it means that increasing the current of the electro-hydraulic proportional valve of the main engine motor can no longer meet the requirement of reducing the main engine speed, and enter step S9;

[0016] S9: Determine whether the engine speed has reached the lower limit according to the engine speed signal. If not, control the engine speed to decrease, and then return to step S2; if the engine speed has reached the lower limit, it means that the engine speed reaching the lower limit can no longer meet the requirement of reducing the main engine speed, and enter step S10;

[0017] S10: Determine whether the working current of the solenoid valve of the main engine pump has reached the lower limit according to the working current signal of the solenoid valve of the main engine pump. If not, control to reduce the current of the solenoid valve of the main engine pump, and then return to step S2.

[0018] Preferably, the method of controlling the increase of the current of the solenoid valve of the main engine pump in step S5 adopts the method of increasing step by step in N steps. The current is divided into N steps from 0 to the upper limit, and the current value is increased step by step.

[0019] Preferably, the method of controlling the increase of the engine speed in step S6 adopts the method of N-level speed control. The engine speed is divided into N levels from the lower limit to the upper limit, and different levels of engine speeds are adopted according to the control signal.

[0020] Preferably, the method of controlling the reduction of the current of the electro-hydraulic proportional valve of the main engine motor in step S7 adopts the method of decreasing step by step in N steps. The current is divided into N steps from the upper limit to the lower limit, and the current value is decreased step by step.

[0021] Preferably, the method of controlling the increase of the current of the electro-hydraulic proportional valve of the main engine motor in step S8 adopts the method of increasing step by step in N steps. The current is divided into N steps from the lower limit to the upper limit, and the current value is increased step by step.

[0022] Preferably, the method of controlling the decrease of the engine speed in step S9 adopts the method of N-level speed control. The engine speed is divided into N levels from the upper limit to the lower limit, and different levels of engine speeds are adopted according to the control signal.

[0023] Preferably, the method of controlling the reduction of the current of the solenoid valve of the main engine pump in step S10 adopts the method of decreasing step by step in N steps. The current is divided into N steps from the upper limit to 0, and the current value is decreased step by step.

[0024] Advantages of the present invention: By using the host pump electro-hydraulic proportional valve, the engine, and the host motor electro-hydraulic proportional valve to perform successive approximation multi-stage speed control on the host, the host speed can be adjusted efficiently, reliably, and precisely, enabling the equipment to always operate at the maximum production capacity and the most comfortable working state, reducing the probability of equipment failure, thereby bringing the greatest economic benefits to customers while increasing the service life of the equipment. Brief Description of the Drawings

[0025] Figure 1 is the flowchart of the multi-stage speed control method of the present invention. Detailed Embodiments

[0026] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0027] Please refer to Figure 1 , taking the XPL1000 mobile vertical shaft impact crusher product produced by our company as an example, its multi-stage speed control method is as follows:

[0028] S1: After the system runs, initialization settings need to be performed. The initialization content includes: the maximum working pressure of the hydraulic system, the set value of the host speed, the maximum working current of the host pump solenoid valve, the minimum working current of the host pump solenoid valve, the minimum working speed of the engine, the maximum working speed of the engine, the minimum working current of the host motor electro-hydraulic proportional valve, the maximum working current of the host motor electro-hydraulic proportional valve, the minimum working speed of the host, and the maximum working speed of the host;

[0029] S2: Collection of system data. The collected content includes: the working current signal of the host pump solenoid valve, the working current signal of the electro-hydraulic proportional valve, the hydraulic system pressure signal, the host speed signal, and the engine speed signal. These signals are calculated and converted into corresponding working currents, pressures, and speeds, sent to the display for display, and provide a basis for subsequent host speed regulation;

[0030] S3: Determine whether the working pressure of the hydraulic system reaches the set value. If it reaches or exceeds, directly return to step S2. If it does not reach the set value, proceed to step S4;

[0031] S4: Determine whether the host speed is less than the set value according to the host speed signal. If it is less than the set value, enter step S5 for host speed increase control. If it is greater than the set value, enter step S8 for host speed decrease control;

[0032] S5: Determine whether the working current of the main pump solenoid valve reaches the upper limit. If not, control the current of the main pump solenoid valve to increase, and then return to step S2. The control of the main solenoid valve current adopts a three-step successive approximation method. The current takes 2.3S from 0 - 225mA, 80S from 225 - 425mA, and 50S from 425 - 600mA. If the current reaches the upper limit, it indicates that only adjusting the main pump displacement can no longer meet the demand for increasing the main engine speed, and it is necessary to enter step S6;

[0033] S6: Determine whether the engine speed reaches the speed upper limit. If not, control the engine speed to increase, and then return to step 2. The increase of the engine speed adopts stepwise speed control. There are four speeds available for use, which are 1500rpm, 1600rpm, 1700rpm, and 1800rpm respectively. In this way, the requirement of quickly changing the engine speed can be achieved. If the engine speed reaches the upper limit, it indicates that increasing the engine speed to the upper limit can no longer meet the demand for increasing the main engine speed, and it is necessary to enter step S7;

[0034] S7: Determine whether the current of the main motor electro-hydraulic proportional valve reaches the lower limit. If not, control the current of the main motor electro-hydraulic proportional valve to decrease, and then return to step 2. The time span of the main motor current from 500mA to 300mA is controlled within 8.5S, and it is also adjusted by the successive approximation method. Through the process of steps 5 - 7, the speed increase target of the main engine speed can be completed;

[0035] S8: This step is the first step to reduce the main engine speed. Determine whether the current of the main motor electro-hydraulic proportional valve reaches the upper limit. If not, control the current of the main motor electro-hydraulic proportional valve to increase, and then return to step 2. The time span of the main motor current from 300mA to 500mA is controlled within 8.5S, and it is also carried out by the successive approximation method. If the current reaches the upper limit, it indicates that only increasing the main motor current can no longer meet the demand for reducing the main engine speed, and it is necessary to enter step S9;

[0036] S9: Determine whether the engine speed reaches the speed lower limit. If not, control the engine speed to decrease, and then return to step 2. The decrease of the engine speed also adopts stepwise speed control. If the engine speed reaches the lower limit, it indicates that reducing the engine speed to the lower limit can no longer meet the demand for reducing the main engine speed, and it is necessary to enter step S10;

[0037] S10: Determine whether the working current of the main pump solenoid valve reaches the current lower limit. If not, control the current of the main pump solenoid valve to decrease, and then return to step 2. The decrease control of the main pump solenoid valve current also adopts a three-step successive approximation method. Through the process of steps S8 - S10, the deceleration process of the main engine speed can be completed.

[0038] In this embodiment, the purpose of the time span of current control is to ensure the smoothness of the speed regulation process. The time span is set differently according to different models. The selection of the time span is mainly based on observing the main engine pressure fluctuation and the vibration of the whole machine, taking into account the smoothness of the main engine startup and the customer's experience of using the equipment. For example, the time span for the main engine motor current to change from 300 mA to 500 mA is controlled within 8.5 s. Here, 8.5 s is based on monitoring the main engine pressure and the vibration amplitude of the whole machine during the process of the current changing from 300 mA to 500 mA. If the main engine pressure does not exceed the design upper limit and the vibration amplitude of the whole machine does not exceed the required value of the customer within 8.5 s, it indicates that the speed regulation effect of controlling the time span of the main engine motor current from 300 mA to 500 mA within 8.5 s is smooth. Otherwise, the time span of speed regulation should be appropriately extended. This logic is also used for adjustment of other models of products. For the setting of current steps and speed steps, different current steps and speed steps can be set according to material type, customer requirements, finished product requirements, etc.

[0039] After the above 10 steps, the system can better complete the multi-level regulation of the main engine speed, comprehensively considering the requirements of the main engine power, working efficiency, engine fuel consumption, etc., so that it is always in the optimal working state.

Claims

1. A multi-stage speed control method for the main machine of a mobile vertical shaft impact crusher station, characterized in that: It includes the following steps: S1: Initialize the system settings, including: the maximum working pressure of the hydraulic system, the set value of the main machine speed, the maximum working current of the main machine pump solenoid valve, the minimum working current of the main machine pump solenoid valve, the minimum working speed of the engine, the maximum working speed of the engine, the minimum working current of the main machine motor electro-hydraulic proportional valve, the maximum working current of the main machine motor electro-hydraulic proportional valve, the minimum working speed of the main machine, and the maximum working speed of the main machine; S2: Collect system data, including: the working current signal of the main machine pump solenoid valve, the working current signal of the electro-hydraulic proportional valve, the pressure signal of the hydraulic system, the main machine speed signal, and the engine speed signal; S3: Judge whether the working pressure of the hydraulic system reaches the set value according to the pressure signal of the hydraulic system. If it reaches or exceeds the set value, return to step S2; otherwise, go to step S4; S4: Judge whether the main machine speed is less than the set value according to the main machine speed signal. If it is less than the set value, enter step S5 for the speed increase control of the main machine; if it is greater than the set value, enter step S8 for the speed decrease control of the main machine; S5: Judge whether the working current of the main machine pump solenoid valve reaches the upper limit according to the working current signal of the main machine pump solenoid valve. If it does not reach the upper limit, control the current of the main machine pump solenoid valve to rise and return to step S2; if the working current of the main machine pump solenoid valve reaches the upper limit, it means that only adjusting the displacement of the main machine pump cannot meet the requirement of increasing the main machine speed, and enter step S6; S6: Judge whether the engine speed reaches the upper limit according to the engine speed signal. If it does not reach the upper limit, control the engine speed to rise and then return to step S2; if the engine speed reaches the upper limit, it means that the engine speed reaching the upper limit cannot meet the requirement of increasing the main machine speed, and enter step S7; S7: Judge whether the current of the main machine motor proportional valve reaches the lower limit according to the working current signal of the electro-hydraulic proportional valve. If it does not reach the lower limit, control the current of the main machine motor electro-hydraulic proportional valve to decrease and then return to step S2; S8: Judge whether the current of the main machine motor proportional valve reaches the upper limit according to the working current signal of the electro-hydraulic proportional valve. If it does not reach the upper limit, control the current of the main machine motor electro-hydraulic proportional valve to increase and then return to step S2; if the current of the main machine motor proportional valve has reached the upper limit, it means that increasing the current of the main machine motor electro-hydraulic proportional valve cannot meet the requirement of reducing the main machine speed, and enter step S9; S9: Judge whether the engine speed reaches the lower limit according to the engine speed signal. If it does not reach the lower limit, control the engine speed to decrease and then return to step S2; if the engine speed reaches the lower limit, it means that the engine speed reaching the lower limit cannot meet the requirement of reducing the main machine speed, and enter step S10; S10: Judge whether the working current of the main machine pump solenoid valve reaches the lower limit according to the working current signal of the main machine pump solenoid valve. If it does not reach the lower limit, control the current of the main machine pump solenoid valve to decrease and then return to step S2.

2. The multi-stage speed control method for the main machine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S5, the method of controlling the current increase of the main pump solenoid valve adopts a step-by-step increase in N steps. The current is divided into N steps from 0 to the upper limit, and the current magnitude is increased step by step.

3. A multi-stage speed control method for the main engine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S6, the method of controlling the engine speed increase adopts a method of N-level speed control. The engine speed is divided into N levels from the lower limit to the upper limit, and different levels of speed are adopted according to the control signal.

4. A multi-stage speed control method for the main engine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S7, the method of controlling the reduction of the current of the main motor electro-hydraulic proportional valve adopts a step-by-step decrease in N steps. The current is divided into N steps from the upper limit to the lower limit, and the current magnitude is decreased step by step.

5. A multi-stage speed control method for the main engine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S8, the method of controlling the increase of the current of the main motor electro-hydraulic proportional valve adopts a step-by-step increase in N steps. The current is divided into N steps from the lower limit to the upper limit, and the current magnitude is increased step by step.

6. A multi-stage speed control method for the main engine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S9, the method of controlling the engine speed decrease adopts a method of N-level speed control. The engine speed is divided into N levels from the upper limit to the lower limit, and different levels of speed are adopted according to the control signal.

7. A multi-stage speed control method for the main engine of a mobile vertical shaft impact crusher station according to claim 1, characterized in that: In step S10, the method of controlling the reduction of the current of the main pump solenoid valve adopts a step-by-step decrease in N steps. The current is divided into N steps from the upper limit to 0, and the current magnitude is decreased step by step.

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