Speed regulation method for hydraulic system, controller and hydraulic system

Abstract

The present invention relates to the field of engineering machinery. Disclosed are a speed regulation method for a hydraulic system, a controller and a hydraulic system. The speed regulation method comprises: acquiring real-time operating conditions of a hydraulic system; on the basis of the real-time operating conditions of the hydraulic system, determining an opening degree range of a handle; when the opening degree of the handle is in a first opening degree range, regulating the opening degree of an electro-hydraulic proportional valve, so as to regulate the speed of an execution mechanism; and, when the opening degree of the handle is in a second opening degree range, regulating the displacement of an electrically controlled variable displacement pump, so as to regulate the speed of the execution mechanism. The method of the present invention can be used for effectively improving the system response speed and flow stability in cold environments while ensuring micro-motion, thus reducing the throttling loss under high-flow operating conditions.

Description

Speed ​​regulation method, controller and hydraulic system for hydraulic system

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims the benefit of Chinese patent application No. 202311182519.1 filed on September 13, 2023, the contents of which are incorporated herein by reference. Technical Field

[0003] The present invention relates to the field of engineering machinery, and in particular to a speed regulation method, a controller and a hydraulic system for a hydraulic system. Background Art

[0004] The hydraulic system in construction machinery is responsible for transmission, specifically, pumps and valves working together to deliver fluid to drive the load. In practice, the mainstream hydraulic systems in construction machinery are divided into pump-controlled systems and load-sensing systems. The pump-controlled system consists of an electronically controlled pump, a reversing valve, and a pump. The displacement of the electronically controlled pump is controlled by the input current, the reversing valve controls the direction of movement of the actuator, and the pump supplies oil to the actuator at a speed determined by the input current. The load-sensing system consists of a load-sensing pump, whose displacement is controlled by the pressure generated by the load. An electro-hydraulic proportional valve controls the direction and speed of the actuator. A compensator valve maintains a constant pressure differential across the proportional valve ports. A shuttle valve selects the high-pressure oil line for connection to the load feedback line, and the LS line feeds the pressure signal back to the load-sensing pump and compensator valve. The pump supplies oil to the actuator at a speed also determined by the input current.

[0005] The pump control system responds to different operating conditions by varying the current to control the pump's output flow. The flow varies greatly and high precision is required, especially in micro-motion conditions, where precise adjustments need to be made within a small variable range. However, large-displacement electronically controlled pumps have poor signal resolution at low displacements, resulting in large errors during fine operations. The load-sensing system transmits pressurized oil as a signal to the pump through a load feedback pipe to control its response and displacement, but this significantly affects the system's response and flow rate. On the one hand, in cold working environments, there are issues with response delays and slow movement. On the other hand, the speed of the actuator is primarily controlled by the throttling of the main valve. Under high-flow conditions, throttling losses are large, and the longer the operating time, the greater the energy loss.

[0006] Summary of the Invention

[0007] The purpose of the present invention is to provide a speed regulation method, a controller and a hydraulic system for a hydraulic system, so as to solve the problem in the prior art that the hydraulic system is greatly affected by temperature and has large energy loss.

[0008] To achieve the above objectives, the present invention provides, in a first aspect, a speed control method for a hydraulic system, which is applied to a controller of the hydraulic system. The hydraulic system also includes an actuator, and an electrically controlled variable pump and an electro-hydraulic proportional valve that communicate with the controller, respectively. The method includes:

[0009] Obtain the real-time working conditions of the hydraulic system;

[0010] Determine the opening range of the handle according to the real-time working conditions of the hydraulic system;

[0011] When the handle opening is within the first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator;

[0012] When the opening degree of the handle is within the second opening degree range, the displacement of the electronically controlled variable displacement pump is adjusted to adjust the speed of the actuator.

[0013] In an embodiment of the present invention, determining the opening range of the handle according to the real-time working condition of the hydraulic system includes: obtaining a preset threshold value of the opening of the handle; when the opening of the handle is less than the preset threshold value, determining that the handle is within a first opening range; when the opening of the handle is greater than the preset threshold value, determining that the handle is within a second opening range.

[0014] In the embodiment of the present invention, the real-time working condition of the hydraulic system includes a high-flow working condition and a low-flow working condition.

[0015] In an embodiment of the present invention, determining the opening range of the handle according to the real-time working condition of the hydraulic system also includes: when the real-time working condition is a small flow condition, adjusting the opening of the handle to within the first opening range; when the real-time working condition is a large flow condition, adjusting the opening of the handle to within the second opening range.

[0016] In an embodiment of the present invention, when the opening of the handle is in the first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator includes: controlling the electronically controlled variable pump to output at a minimum stable flow rate; obtaining a first real-time flow demand; and adjusting the opening of the electro-hydraulic proportional valve under the condition that the minimum stable flow rate is greater than the first real-time flow demand.

[0017] In an embodiment of the present invention, when the opening of the handle is in the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator includes: controlling the valve port opening of the electro-hydraulic proportional valve to the maximum opening; obtaining a second real-time flow demand; and adjusting the displacement of the electronically controlled variable pump so that the displacement of the electronically controlled variable pump meets the second real-time flow demand.

[0018] In an embodiment of the present invention, when the opening of the handle is in the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator includes: obtaining a third real-time flow demand; adjusting the displacement of the electronically controlled variable pump so that the displacement of the electronically controlled variable pump meets the third real-time flow demand; and dynamically adjusting the valve port opening of the electro-hydraulic proportional valve according to the displacement of the electronically controlled variable pump under the condition that the valve flow rate of the electro-hydraulic proportional valve is greater than the displacement of the electronically controlled variable pump.

[0019] A second aspect of the present invention provides a controller, comprising:

[0020] a memory configured to store instructions; and

[0021] The processor is configured to call the instructions from the memory and implement the above-mentioned speed regulation method for the hydraulic system when executing the instructions.

[0022] A third aspect of the present invention provides a hydraulic system, comprising:

[0023] the aforementioned controller;

[0024] at least one hydraulic oil tank;

[0025] at least one electronically controlled variable displacement pump, communicating with the controller and connected to the hydraulic oil tank, configured to control the flow of the hydraulic system by adjusting the opening;

[0026] at least one electro-hydraulic proportional valve, in communication with the controller and connected to the electrically controlled variable displacement pump, configured to control flow in the hydraulic system by adjusting displacement; and

[0027] At least one actuator is connected to the electro-hydraulic proportional valve and is configured to drive a load.

[0028] A fourth aspect of the present invention provides a machine-readable storage medium having stored thereon instructions for causing a machine to execute the above-mentioned speed regulation method for a hydraulic system.

[0029] The above-mentioned speed control method for a hydraulic system obtains the real-time operating conditions of the hydraulic system and determines the handle opening range based on these conditions. When the handle opening is within a first opening range, the opening of the electro-hydraulic proportional valve is adjusted to adjust the actuator speed. When the handle opening is within a second opening range, the displacement of the electrically controlled variable pump is adjusted to adjust the actuator speed. This method combines the advantages of pump control and valve control, effectively improving the system's response speed and flow stability in cold environments while maintaining micro-mobility, and reducing throttling losses under high-flow conditions.

[0030] Other features and advantages of the present invention will be described in detail in the following detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The accompanying drawings are used to provide a further understanding of the present invention and constitute a part of the specification. Together with the following detailed description, they are used to explain the present invention but do not constitute a limitation of the present invention. In the accompanying drawings:

[0032] FIG1 schematically shows a simplified diagram of a hydraulic system according to an embodiment of the present application;

[0033] FIG2 schematically shows a flow chart of a speed regulation method for a hydraulic system according to an embodiment of the present application;

[0034] FIG3 schematically shows a diagram showing the relationship between the handle opening and the action of the actuator according to an embodiment of the present application;

[0035] FIG4 schematically shows a diagram showing the relationship between the handle opening and the power supply of the electro-hydraulic proportional valve according to an embodiment of the present application;

[0036] FIG5 schematically shows a relationship diagram between a handle opening and power supply of an electrically controlled variable displacement pump according to an embodiment of the present application;

[0037] FIG6( a ) schematically shows a relationship diagram between a handle opening and a pump-valve flow rate according to an embodiment of the present application;

[0038] FIG6( b ) schematically shows another diagram showing the relationship between the handle opening and the power supply to the electro-hydraulic proportional valve according to an embodiment of the present application;

[0039] FIG7 schematically shows a structural block diagram of a controller according to an embodiment of the present application;

[0040] FIG8 schematically shows a structural diagram of a hydraulic system according to an embodiment of the present application.

[0041] In the figure: 1. Hydraulic oil tank; 2. Electronically controlled variable pump; 3. Electro-hydraulic proportional valve; 4. Actuator. DETAILED DESCRIPTION

[0042] The following describes the specific embodiments of the present invention in detail with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present invention and are not intended to limit the present invention.

[0043] The hydraulic system in the prior art includes a pump control system and a load-sensitive system. The flow rate of the pump control system varies greatly and requires high precision. Especially under micro-motion conditions, precise adjustments need to be made within a small variable range, while large-displacement electronically controlled pumps have poor signal resolution at small displacements, resulting in large errors in fine operations. The load-sensitive system causes the response and flow rate of the hydraulic system to be greatly affected by temperature. In a cold working environment, there are problems of response delay and slow movement. The speed of the actuator mainly depends on the throttling speed regulation of the main valve. Under large working conditions, the throttling loss is large. Therefore, an embodiment of the present application provides a hydraulic system that may include a controller, at least one hydraulic oil tank, at least one electronically controlled variable pump, at least one electro-hydraulic proportional valve, and at least one actuator. The hydraulic system of the embodiment of the present application combines an electronically controlled variable pump and an electro-hydraulic proportional valve, eliminates the LS pipeline of the hydraulic system in the prior art, and replaces the pressure signal with an electrical signal, which can reduce the temperature sensitivity of the system and effectively solve the problems of slow response and decreased flow rate at low temperatures.

[0044] Figure 1 schematically shows a simplified diagram of a hydraulic system according to an embodiment of the present application. Figure 1 takes a hydraulic oil tank, an electronically controlled variable pump, an electro-hydraulic proportional valve and an actuator as an example. As shown in Figure 1, the hydraulic system of the embodiment of the present application includes a controller (not shown in the figure), a hydraulic oil tank 1, an electronically controlled variable pump 2, an electro-hydraulic proportional valve 3 and an actuator 4. The electronically controlled variable pump 2 and the electro-hydraulic proportional valve 3 both communicate with the controller, the electronically controlled variable pump 2 is connected to the hydraulic oil tank 1, the electro-hydraulic proportional valve 3 is connected to the electronically controlled variable pump 2, and the actuator 4 is connected to the electro-hydraulic proportional valve 3. The controller of the embodiment of the present application can select the electronically controlled variable pump 2 or the electro-hydraulic proportional valve 3 according to different working conditions to adjust the system flow and thereby adjust the speed of the actuator.

[0045] Figure 2 schematically illustrates a flow chart of a speed regulation method for a hydraulic system according to an embodiment of the present application. As shown in Figure 2, the speed regulation method for a hydraulic system according to an embodiment of the present application is applied to the hydraulic system shown in Figure 1. An embodiment of the present application provides a speed regulation method for a hydraulic system, which is applied to a controller of the hydraulic system. The hydraulic system also includes an actuator, an electrically controlled variable pump, and an electro-hydraulic proportional valve, each of which communicates with the controller. The method may include the following steps.

[0046] Step 201: Acquire the real-time working condition of the hydraulic system;

[0047] Step 202: Determine the opening range of the handle according to the real-time working conditions of the hydraulic system;

[0048] Step 203: When the handle opening is within the first opening range, adjust the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator;

[0049] Step 204 : When the handle opening is within the second opening range, adjust the displacement of the electronically controlled variable displacement pump to adjust the speed of the actuator.

[0050] In the embodiment of the present application, the real-time working conditions of the hydraulic system may include a high-flow working condition and a low-flow working condition.

[0051] Specifically, the controller can first obtain the real-time operating conditions of the hydraulic system, which include high-flow conditions and low-flow conditions. The controller can then determine the handle opening range based on the real-time operating conditions of the hydraulic system. The handle opening range can include a first opening range and a second opening range. The first opening range refers to the handle opening range when the hydraulic system is in a high-flow condition, and the second opening range refers to the handle opening range when the hydraulic system is in a low-flow condition. In other words, when it is determined that the hydraulic system is in a low-flow condition, the handle opening needs to be controlled within the first opening range; when it is determined that the hydraulic system is in a high-flow condition, the handle opening needs to be controlled within the second opening range.

[0052] In one example, a threshold, i.e., a preset threshold, can be pre-set. When the handle opening is less than the preset threshold, the handle is determined to be within a first opening range; when the handle opening is greater than the preset threshold, the handle is determined to be within a second opening range. When the hydraulic system is operating in a low-flow condition, the handle opening should first be adjusted to a range less than the preset threshold, and then the handle opening should be continuously adjusted to decrease. When the set value reaches the small opening range, the system is operating in a high-flow condition, the actuator is in an inching condition, and the electronically controlled variable pump maintains a minimum stable output flow rate. Adjusting the handle opening adjusts the opening of the electro-hydraulic proportional valve, and the flow rate of the hydraulic system is controlled by the electro-hydraulic proportional valve. The flow rate output by the electronically controlled variable pump is secondary throttled to achieve the desired flow rate, effectively resolving the issue of large errors during the system's inching condition. It should be noted that the pump's minimum stable flow rate must be greater than the flow rate required for the inching condition. When the hydraulic system is operating in a high-flow condition, the handle opening should first be adjusted to a range greater than the preset threshold, and then the handle opening should be continuously adjusted to increase it. The flow of the hydraulic system is controlled by an electronically controlled variable pump, and the valve core of the electro-hydraulic proportional valve is fully open. At this time, the displacement of the electronically controlled variable pump can be adjusted by adjusting the handle opening, so that the electronically controlled variable pump can output the flow required by the system, effectively solving the problem of large throttling loss in the system.

[0053] Through the above technical solution, the real-time operating conditions of the hydraulic system are first obtained, and the handle opening range is determined based on the real-time operating conditions of the hydraulic system. Then, when the handle opening is within the first opening range, the opening of the electro-hydraulic proportional valve is adjusted to adjust the speed of the actuator; when the handle opening is within the second opening range, the displacement of the electronically controlled variable pump is adjusted to adjust the speed of the actuator. This embodiment of the application combines the advantages of pump control and valve control, effectively improving the system's response speed and flow stability in cold environments while ensuring micro-mobility, and reducing throttling losses under high-flow conditions.

[0054] FIG3 schematically shows a diagram showing the relationship between the handle opening and the action of the actuator according to an embodiment of the present application. As shown in FIG3 , in the embodiment of the present application, step 202, determining the handle opening range according to the real-time working condition of the hydraulic system, may include:

[0055] Get the preset threshold of the handle opening;

[0056] When the opening degree of the handle is less than a preset threshold, determining that the handle is within a first opening degree range;

[0057] When the opening degree of the handle is greater than a preset threshold, it is determined that the handle is within a second opening degree range.

[0058] In the embodiment of the present application, step 202, determining the opening range of the handle according to the real-time working condition of the hydraulic system, may further include:

[0059] When the real-time working condition is a low flow condition, adjust the opening of the handle to within the first opening range;

[0060] When the real-time working condition is a high-flow working condition, adjust the opening of the handle to within the second opening range.

[0061] In the embodiment of the present application, the preset threshold value of the handle refers to the threshold value that distinguishes the first opening range from the second opening range. The preset threshold value is set in advance and stored in the controller according to actual conditions. When the hydraulic system is in a low-flow condition, the actuator is in a micro-motion condition. At this time, the handle opening needs to be adjusted to not exceed the preset threshold value and be within the first opening range. When the hydraulic system is in a high-flow condition, the actuator is in a high-speed condition. At this time, the handle opening needs to be adjusted to exceed the preset threshold value and be within the second opening range. Determining the opening range of the handle based on the preset threshold value of the handle facilitates more efficient subsequent adjustment of the hydraulic system under different working conditions.

[0062] In an embodiment of the present application, when the opening of the handle is within the first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator may include:

[0063] Control the electronically controlled variable pump to output at the minimum stable flow rate;

[0064] Obtain the first real-time traffic demand;

[0065] Under the condition that the minimum stable flow rate is greater than the first real-time flow rate requirement, the opening of the electro-hydraulic proportional valve is adjusted.

[0066] In the embodiment of the present application, when the handle is in the first opening range (i.e., the system is in a low-flow operating condition), the actuator is in an inching condition, the electronically controlled variable pump maintains a minimum stable output flow rate, and the operating handle adjusts the opening of the electro-hydraulic proportional valve, performing secondary throttling on the pump output flow rate to obtain the desired flow rate. This effectively resolves the problem of large errors during inching in the hydraulic system. The opening of the electro-hydraulic proportional valve must be adjusted to ensure that the minimum stable flow rate is greater than the first real-time flow demand. The first real-time flow demand is the flow demand during inching.

[0067] FIG4 schematically shows a diagram showing the relationship between the handle opening and the power supply of the electro-hydraulic proportional valve according to an embodiment of the present application. As shown in FIG4 , when the hydraulic system is in a low-flow condition, the handle opening is first adjusted to be within a first opening range. When the handle opening decreases to below the preset threshold value K1, the electronically controlled variable pump immediately drops to the minimum stable flow rate and continues to output at the minimum stable flow rate, which hardly changes with the handle opening. Then, the real-time flow demand of the hydraulic system, i.e., the first real-time flow demand, is obtained. Under the condition that the minimum stable flow rate of the electronically controlled variable pump is greater than the first real-time flow demand, the valve core opening of the electro-hydraulic proportional valve is adjusted to change with the handle opening, and the required flow rate is output after throttling. The relationship between the handle opening and the power supply of the electro-hydraulic proportional valve is shown in FIG4 . When the handle opening is less than the preset threshold value K1 and continues to decrease, the control current of the electronically controlled variable pump remains at a minimum, and the current of the electro-hydraulic proportional valve decreases parabolically to achieve fine control of small flows.

[0068] In the embodiment of the present application, when the opening of the handle is within the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator may include:

[0069] Control the valve opening of the electro-hydraulic proportional valve to the maximum opening;

[0070] Obtaining the second real-time traffic demand;

[0071] The displacement of the electronically controlled variable pump is adjusted so that the displacement of the electronically controlled variable pump meets the second real-time flow demand.

[0072] In this embodiment of the present application, when the handle is in the second opening range, i.e., high-flow operating conditions, the electro-hydraulic proportional valve is fully opened, and the operating handle controls the displacement of the electronically controlled variable pump, effectively resolving the issue of large throttling losses in the hydraulic system. The displacement of the electronically controlled variable pump must meet the second real-time flow requirement, i.e., the flow rate required by the hydraulic system under high-flow operating conditions.

[0073] FIG5 schematically illustrates a diagram showing the relationship between the handle opening and the power supply to the electronically controlled variable pump according to an embodiment of the present application. As shown in FIG5 , specifically, when the hydraulic system is in a high-flow operating condition, the handle opening is first adjusted to be within the second opening range. When the handle opening increases and exceeds the preset threshold value K1, the electro-hydraulic proportional valve is energized, and the valve core is fully open in the right position, without throttling. The real-time flow demand of the hydraulic system, i.e., the second real-time flow demand, is then obtained. At this time, the displacement of the electronically controlled variable pump changes with the handle opening, and the output meets the second real-time flow demand. At this time, the actuator speed is completely controlled by the electronically controlled variable pump. The relationship between the handle opening and the power supply to the electronically controlled variable pump is shown in FIG5 . When the handle opening continues to increase beyond the preset threshold value K1, the current of the electronically controlled variable pump increases parabolically to achieve smooth control of the high flow rate. The control current of the electro-hydraulic proportional valve jumps to the maximum, and the valve core of the electro-hydraulic proportional valve is fully open, serving only as a flow passage.

[0074] In the embodiment of the present application, when the opening of the handle is in the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator may include:

[0075] Obtain third-party real-time traffic demand;

[0076] adjusting the displacement of the electronically controlled variable pump so that the displacement of the electronically controlled variable pump meets the third real-time flow demand;

[0077] Under the condition that the valve flow rate of the electro-hydraulic proportional valve is greater than the displacement of the electronically controlled variable pump, the valve port opening of the electro-hydraulic proportional valve is dynamically adjusted according to the displacement of the electronically controlled variable pump.

[0078] In an embodiment of the present application, to further optimize the flow control of the hydraulic system and address flow distribution during the combined action of multiple actuators, the proportional characteristics of the electro-hydraulic proportional valve can be further utilized based on the above-mentioned control method. Figure 6(a) schematically illustrates a relationship between handle opening and pump-valve flow according to one embodiment of the present application, and Figure 6(b) schematically illustrates another relationship between handle opening and electro-hydraulic proportional valve power supply according to another embodiment of the present application. As shown in Figures 6(a) and 6(b), in one example, the hydraulic system comprises only one oil tank, an electrically controlled variable pump, an electro-hydraulic proportional valve, and an actuator. The third real-time flow demand is the real-time flow demand of the single pump-valve structure when the hydraulic system is operating under high flow conditions, which is also the real-time flow demand of the hydraulic system. In another example, the hydraulic system comprises multiple oil tanks, electrically controlled variable pumps, electro-hydraulic proportional valves, and actuators. The third real-time flow demand is the flow required by any one of the multiple pump-valve structures when the hydraulic system is operating under high flow conditions and multiple actuators are operating under combined action.

[0079] When the hydraulic system is operating at high flow, the third real-time flow demand is first obtained, and the displacement of the electronically controlled variable pump is adjusted to meet the third real-time flow demand. Then, while ensuring that the electro-hydraulic proportional valve is not throttling (that is, ensuring that the valve flow rate of the electro-hydraulic proportional valve is greater than the displacement of the electronically controlled variable pump), the valve core opening of the electro-hydraulic proportional valve is adjusted to dynamically change with the displacement of the electronically controlled variable pump. The pump-valve flow rate variation at this time is shown in Figure 6(a), and the handle opening and electro-hydraulic proportional valve power curve is shown in Figure 6(b).

[0080] FIG7 schematically shows a block diagram of a controller according to an embodiment of the present application. As shown in FIG7 , the present application provides a controller, which may include:

[0081] Memory 710 configured to store instructions; and

[0082] The processor 720 is configured to call instructions from the memory 710 and implement the above-mentioned speed regulation method for the hydraulic system when executing the instructions.

[0083] Specifically, in the embodiment of the present application, the processor 720 may be configured to:

[0084] Obtain the real-time working conditions of the hydraulic system;

[0085] Determine the opening range of the handle according to the real-time working conditions of the hydraulic system;

[0086] When the handle opening is within the first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator;

[0087] When the opening degree of the handle is within the second opening degree range, the displacement of the electronically controlled variable displacement pump is adjusted to adjust the speed of the actuator.

[0088] Furthermore, the processor 720 may be further configured to:

[0089] Get the preset threshold of the handle opening;

[0090] When the opening degree of the handle is less than a preset threshold, determining that the handle is within a first opening degree range;

[0091] When the opening degree of the handle is greater than a preset threshold, it is determined that the handle is within a second opening degree range.

[0092] In the embodiment of the present application, the real-time working conditions of the hydraulic system include a high-flow working condition and a low-flow working condition.

[0093] Furthermore, the processor 720 may be further configured to:

[0094] When the real-time working condition is a low flow condition, adjust the opening of the handle to within the first opening range;

[0095] When the real-time working condition is a high-flow working condition, adjust the opening of the handle to within the second opening range.

[0096] Furthermore, the processor 720 may be further configured to:

[0097] Control the electronically controlled variable pump to output at the minimum stable flow rate;

[0098] Obtain the first real-time traffic demand;

[0099] Under the condition that the minimum stable flow rate is greater than the first real-time flow rate requirement, the opening of the electro-hydraulic proportional valve is adjusted.

[0100] Furthermore, the processor 720 may be further configured to:

[0101] Control the valve opening of the electro-hydraulic proportional valve to the maximum opening;

[0102] Obtaining the second real-time traffic demand;

[0103] The displacement of the electronically controlled variable pump is adjusted so that the displacement of the electronically controlled variable pump meets the second real-time flow demand.

[0104] Furthermore, the processor 720 may be further configured to:

[0105] Obtain third-party real-time traffic demand;

[0106] adjusting the displacement of the electronically controlled variable pump so that the displacement of the electronically controlled variable pump meets the third real-time flow demand;

[0107] Under the condition that the valve flow rate of the electro-hydraulic proportional valve is greater than the displacement of the electronically controlled variable pump, the valve port opening of the electro-hydraulic proportional valve is dynamically adjusted according to the displacement of the electronically controlled variable pump.

[0108] Through the above technical solution, the real-time operating conditions of the hydraulic system are first obtained, and the handle opening range is determined based on the real-time operating conditions of the hydraulic system. Then, when the handle opening is within the first opening range, the opening of the electro-hydraulic proportional valve is adjusted to adjust the speed of the actuator; when the handle opening is within the second opening range, the displacement of the electronically controlled variable pump is adjusted to adjust the speed of the actuator. This application combines the advantages of pump control and valve control, effectively improving the system's response speed and flow stability in cold environments while ensuring micro-mobility, and reducing throttling losses under high-flow conditions.

[0109] FIG8 schematically shows a structural diagram of a hydraulic system according to an embodiment of the present application. As shown in FIG8 , the embodiment of the present application further provides a hydraulic system, which may include:

[0110] The above-mentioned controller (not shown);

[0111] At least one hydraulic oil tank 1;

[0112] at least one electronically controlled variable displacement pump 2, communicating with the controller and connected to the hydraulic oil tank 1, configured to control the flow of the hydraulic system by adjusting the opening;

[0113] at least one electro-hydraulic proportional valve 3 , communicating with the controller and connected to the electronically controlled variable pump 2 , configured to control the flow of the hydraulic system by adjusting the displacement; and

[0114] At least one actuator 4 is connected to the electro-hydraulic proportional valve 3 and is configured to drive a load.

[0115] The hydraulic system of the embodiment of the present application combines an electrically controlled variable pump and an electro-hydraulic proportional valve, eliminates the LS pipeline, and replaces the pressure signal with an electrical signal, which can reduce the temperature sensitivity of the system and effectively solve the problems of slow response and decreased flow at low temperatures. The hydraulic system of the embodiment of the present application mainly includes a controller (not shown in the figure), a hydraulic oil tank 1, an electrically controlled variable pump 2, an electro-hydraulic proportional valve 3 and an actuator 4. In actual applications, the controller can select an electrically controlled variable pump and an electro-hydraulic proportional valve according to different working conditions to determine the system flow and thereby adjust the speed of the actuator. Figure 1 is a simplified schematic diagram of the hydraulic system in the embodiment of the present application. In fact, as shown in Figure 8, there may be multiple hydraulic oil tanks, multiple electrically controlled variable pumps, multiple electro-hydraulic proportional valves and multiple actuators.

[0116] An embodiment of the present application further provides a machine-readable storage medium having stored thereon instructions for causing a machine to execute the above-mentioned speed regulation method for a hydraulic system.

[0117] The preferred embodiments of the present invention are described in detail above in conjunction with the accompanying drawings. However, the present invention is not limited to the specific details in the above embodiments. Within the technical concept of the present invention, various simple modifications can be made to the technical solution of the present invention, and these simple modifications all fall within the scope of protection of the present invention.

[0118] It should also be noted that the various specific technical features described in the above specific embodiments can be combined in any appropriate manner without contradiction. To avoid unnecessary repetition, the present invention will not further describe various possible combinations.

[0119] In addition, the various embodiments of the present invention may be arbitrarily combined, and as long as they do not violate the concept of the present invention, they should also be regarded as the contents disclosed by the present invention.

Claims

1. A speed regulation method for a hydraulic system, characterized in that: A controller applied to a hydraulic system, wherein the hydraulic system further comprises an actuator, and an electrically controlled variable pump and an electro-hydraulic proportional valve respectively communicating with the controller, wherein the method comprises: Obtaining the real-time working condition of the hydraulic system; Determining the opening range of the handle according to the real-time working condition of the hydraulic system; When the opening of the handle is within a first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator; When the opening degree of the handle is within the second opening degree range, the displacement of the electronically controlled variable displacement pump is adjusted to adjust the speed of the actuator.

2. The speed regulation method according to claim 1, characterized in that: Determining the opening range of the handle according to the real-time working condition of the hydraulic system includes: Get the preset threshold of the handle opening; When the opening degree of the handle is less than the preset threshold, determining that the handle is within a first opening degree range; When the opening degree of the handle is greater than the preset threshold, it is determined that the handle is within a second opening degree range.

3. The speed regulation method according to claim 1, characterized in that: The real-time working conditions of the hydraulic system include a large flow working condition and a small flow working condition.

4. The speed regulation method according to claim 3, characterized in that: Determining the opening range of the handle according to the real-time working condition of the hydraulic system also includes: When the real-time working condition is a low flow working condition, adjusting the opening of the handle to within the first opening range; When the real-time working condition is a large flow condition, the opening of the handle is adjusted to within the second opening range.

5. The speed regulation method according to claim 1, characterized in that: When the opening of the handle is within the first opening range, adjusting the opening of the electro-hydraulic proportional valve to adjust the speed of the actuator includes: Controlling the electronically controlled variable pump to output at a minimum stable flow rate; Obtain the first real-time traffic demand; Under the condition that the minimum stable flow rate is greater than the first real-time flow rate requirement, the opening of the electro-hydraulic proportional valve is adjusted.

6. The speed regulation method according to claim 1, characterized in that: When the opening of the handle is within the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator includes: Controlling the valve opening of the electro-hydraulic proportional valve to be the maximum opening; Obtaining the second real-time traffic demand; The displacement of the electronically controlled variable pump is adjusted so that the displacement of the electronically controlled variable pump meets the second real-time flow demand.

7. The speed regulation method according to claim 1, characterized in that: When the opening of the handle is within the second opening range, adjusting the displacement of the electronically controlled variable pump to adjust the speed of the actuator includes: Obtain third-party real-time traffic demand; adjusting the displacement of the electronically controlled variable pump so that the displacement of the electronically controlled variable pump meets the third real-time flow demand; Under the condition that the valve flow rate of the electro-hydraulic proportional valve is greater than the displacement of the electrically-controlled variable pump, the valve port opening of the electro-hydraulic proportional valve is dynamically adjusted according to the displacement of the electrically-controlled variable pump.

8. A controller, characterized in that: include: a memory configured to store instructions; as well as A processor is configured to call the instructions from the memory and implement the speed regulation method for a hydraulic system according to any one of claims 1 to 7 when executing the instructions.

9. A hydraulic system, characterized in that: include: The controller according to claim 8; at least one hydraulic oil tank; at least one electrically controlled variable displacement pump, communicating with the controller and connected to the hydraulic oil tank, configured to control the flow of the hydraulic system by adjusting the opening; at least one electro-hydraulic proportional valve, in communication with the controller and connected to the electrically controlled variable displacement pump, configured to control the flow of the hydraulic system by adjusting the displacement; as well as At least one actuator is connected to the electro-hydraulic proportional valve and is configured to drive a load.

10. A machine-readable storage medium, characterized in that: The machine-readable storage medium stores instructions, which are used to enable a machine to execute the speed regulation method for a hydraulic system according to any one of claims 1 to 7.

Images