WO2023185114A1

WO2023185114A1 - Control method for engineering device, and processor and engineering device

Info

Publication number: WO2023185114A1
Application number: PCT/CN2022/140051
Authority: WO
Inventors: 宋建清; 何伟; 沈昌武; 黄珍
Original assignee: 中联重科股份有限公司
Priority date: 2022-03-31
Filing date: 2022-12-19
Publication date: 2023-10-05
Also published as: CN114815603A

Abstract

A control method for an engineering device, and a processor and an engineering device. The engineering device comprises an engine, a proportional pressure reducing valve (21), a plunger pump (18) and a control valve (15), wherein the control valve (15) is respectively connected to the proportional pressure reducing valve (21) and the plunger pump (18). The control method comprises: determining a first effective output torque of an engine under a first working condition (201); determining a second effective output torque of the engine under a second working condition (202); determining the current effective output torque of the engine (203); according to the first effective output torque, the second effective output torque and the current effective output torque, determining an input current of a proportional pressure reducing valve (21), so as to determine an output pressure of the proportional pressure reducing valve (21) (204); and adjusting a torque control value of a control valve (15) according to the output pressure of the proportional pressure reducing valve (21), so as to adjust the displacement of a plunger pump (18), thereby adjusting the working speed of a corresponding execution element of the engine (205). An effective output torque of an engine can fully participate in an operation, thereby improving the utilization rate of the effective torque of the engine, and thus improving the working efficiency.

Description

Control method, processor and engineering equipment for engineering equipment

Cross-references to related applications

This application claims the rights and interests of Chinese patent application 202210346051.4 submitted on March 31, 2022. The content of this application is incorporated into this article by reference.

Technical field

The present invention relates to the technical field of engineering machinery, and specifically to a control method, a processor and engineering equipment for engineering equipment.

Background technique

With the rapid development of engineering machinery and the implementation of environmental protection policies, the power and torque of engines used in engineering machinery are gradually becoming smaller in design and selection when meeting driving and operating requirements. In order to meet the requirements of various operating conditions and avoid engine stalling or excessive engine power and torque matching under heavy load conditions, constant power variable piston pumps are commonly used in the construction machinery industry, which not only reduces energy consumption, but also meets the requirements of Various working conditions requirements.

Constant power variable piston pump: In order to prevent the engine (or motor) from exceeding its rated output torque, causing the engine to stall instantly and fail to work normally, the piston pump is designed with a control valve. After the working pressure P of the oil pump exceeds a certain value, the displacement q of the oil pump is inversely proportional to the working pressure P. As the working pressure P increases, the displacement q decreases, so that the torque of the oil pump M=P*q=C (constant), and the Torque remains unchanged. A variable piston pump with such a constant torque control device is called a constant power variable piston pump.

Under heavy load conditions, the constant power control valve continues to function. In order to prevent the engine from stalling, the constant power control valve puts the system in a constant torque state. At this time, only part of the displacement of the plunger pump is involved in the work, and the corresponding actuator of the engine cannot be used. Working at the maximum speed, the working efficiency is low; the engine is in a power-rich state, and the excess torque cannot participate in work.

Contents of the invention

The purpose of the present invention is to overcome the problem in the prior art that the actuator corresponding to the engine cannot work at the maximum speed and the working efficiency is low; the engine is in a power-rich state and the excess torque cannot participate in doing work, and provides an engineering equipment Control methods, processors and engineering equipment to solve the above problems.

In order to achieve the above object, the first aspect of the present invention provides a control method for engineering equipment. The engineering equipment includes an engine, a proportional pressure reducing valve, a plunger pump and a control valve. The control valve is connected to the proportional pressure reducing valve and the plunger pump respectively. Connection and control methods include:

Determine the first effective output torque of the engine under the first operating condition;

Determine the second effective output torque of the engine under the second operating condition;

Determine the current effective output torque of the engine;

Determine the input current of the proportional pressure reducing valve according to the first effective output torque, the second effective output torque and the current effective output torque to determine the output pressure of the proportional pressure reducing valve;

The torque control value of the control valve is adjusted according to the output pressure of the proportional pressure reducing valve to adjust the displacement of the plunger pump, thereby adjusting the working speed of the corresponding actuator of the engine. The control valve keeps the power of the plunger pump constant based on the torque control value. .

Specifically, the first working condition includes an idle working condition; the second working condition includes: the load pressure of the corresponding actuator of the engine is the largest and the displacement of the plunger pump is the largest.

Specifically, the input current of the proportional pressure reducing valve satisfies the following formula (1):

I＝(M-M1)/(M2-M1)*100% Formula (1)

Among them, I represents the current percentage of the proportional pressure reducing valve when the effective output torque of the engine is M. The current percentage is the percentage of the input current and the maximum allowable current of the proportional pressure reducing valve. M represents the current effective output torque of the engine, M1 Indicates the effective output torque of the engine under idling conditions, and M2 indicates the effective output torque of the engine under the second operating condition.

Specifically, adjusting the torque control value of the control valve according to the output pressure of the proportional pressure reducing valve to adjust the displacement of the plunger pump, thereby adjusting the working speed of the corresponding actuator of the engine, includes:

During the change from the first working condition to the second working condition, when the effective output torque of the engine increases, the current of the proportional pressure reducing valve is increased, so that the output pressure of the proportional pressure reducing valve is increased, and the control valve is increased. The variable pressure causes the torque control value of the control valve to increase, thereby increasing the displacement of the plunger pump and increasing the working speed of the actuator.

Specifically, increasing the variable pressure of the control valve includes:

Increase the variable pressure of the control valve according to the increase in the output pressure of the proportional pressure reducing valve; and/or

The variable pressure of the control valve is increased according to the increase in current of the proportional pressure reducing valve.

Specifically, the engineering equipment also includes a control piston and a rocker. The control piston is connected to the control valve and the rocker respectively. The rocker is connected to the plunger pump. The control method also includes:

When the variable pressure of the control valve increases, the control piston is pushed to move and the rocker is driven to move, so that the displacement of the plunger pump increases, thereby increasing the working speed of the actuator.

Specifically, the actuator includes an oil pump. When the power of the plunger pump is constant, the torque of the oil pump satisfies the following formula (2):

M3＝P*q＝C Formula (2)

Among them, M3 represents the torque of the oil pump, P represents the working pressure of the oil pump, q represents the displacement of the oil pump, C is the constant corresponding to the torque control value of the control valve, and C increases when the torque control value increases.

Specifically, during the change from the first working condition to the second working condition, the engine speed increases and the effective output torque of the engine increases.

A second aspect of the present invention provides a processor configured to execute the above control method for engineering equipment.

A third aspect of the present invention provides engineering equipment, including the above-mentioned processor.

In the embodiment of the present invention, the effective output torque of the engine is detected, and the input current of the proportional pressure reducing valve is controlled according to the effective output torque of the engine. Specifically, when the effective output torque of the engine increases, the input current of the proportional pressure reducing valve is increased, so that the output pressure of the proportional pressure reducing valve is increased, which increases the torque control value of the constant power control valve, and subsequently increases The displacement of the plunger pump. In this way, the working speed of the actuator under heavy load conditions is effectively increased and the work efficiency is improved. By detecting the effective output torque of the engine, the output pressure of the proportional pressure reducing valve increases in proportion to the effective output torque of the engine, so that the effective output torque of the engine can fully participate in the operation and reduce torque waste. Under heavy load conditions, the utilization of the engine's effective torque is improved.

Description of drawings

The drawings are used to provide a further understanding of the present invention and constitute a part of the specification. They are used to explain the present invention together with the following specific embodiments, but do not constitute a limitation of the present invention. In the attached picture:

Figure 1 schematically shows one of the hardware connection diagrams of engineering equipment;

Figure 2 schematically shows a flow chart of a control method for engineering equipment according to an embodiment of the present invention;

Figure 3 schematically shows a hardware connection diagram of engineering equipment according to an embodiment of the present invention;

Figure 4 schematically shows a graph of the output torque of the engine and the current of the proportional pressure reducing valve according to an embodiment of the present invention;

FIG. 5 schematically shows a graph of current and pressure of a proportional pressure reducing valve according to an embodiment of the present invention.

Detailed ways

Specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described here are only used to illustrate and explain the present invention, and are not intended to limit the present invention.

In order to facilitate understanding of the specific implementation details and advantages of using proportional control valves for control in the embodiment of the present invention, before that, the solution of using solenoid valves for control is first described in conjunction with Figure 1 , which schematically shows engineering equipment. One of the hardware connection diagrams.

Constant power variable piston pump: In order to prevent the engine (or motor) from exceeding its rated output torque, causing the engine to stall instantly and fail to work normally, the piston pump is designed with a control valve. The displacement q of the oil pump is inversely proportional to the working pressure P. After the working pressure P of the oil pump exceeds a certain value, the working pressure P increases and the displacement q of the oil pump decreases, so that M=P*q=C (constant), the torque of the oil pump M remains unchanged. A variable piston pump with such a constant torque control device is called a constant power variable piston pump.

With the rapid development of engineering machinery and the implementation of environmental protection policies, the power and torque of engines used in engineering equipment are gradually becoming smaller in design and selection when meeting driving and operating requirements. In order to meet the requirements of various operating conditions and avoid engine stalling or excessive engine power and torque matching under heavy load conditions, constant power variable piston pumps are commonly used in the construction machinery industry, which not only reduces energy consumption, but also meets the requirements of Various working conditions requirements.

Figure 1 shows the control system of a constant power variable plunger pump using a solenoid valve. As shown in Figure 1, the control system of the constant power variable plunger pump involves: main valve throttle 10, damping 11, solenoid valve 12, load sensitive control valve 13, pressure cut-off control valve 14, constant power control valve 15, small Control piston 16, rocker 17, plunger pump 18, large control piston 19 and oil tank 20.

In the system shown in Figure 1, in the non-working state, the corresponding actuator of the engine does not work, and the system pressure is in a low state. Under the action of the spring force, the large control piston 19 quickly resets, and the plunger pump 18 switches to the minimum Displacement, reducing system power loss and heat generation.

Introducing the working conditions of the load-sensitive control valve 13: In the system shown in Figure 1, the outlet pressure of the plunger pump 18 is P1, and the load pressure of the corresponding actuator of the engine is P _LS . The flow rate Q1 output by the plunger pump drives the actuator through the main valve orifice 10. The pressure difference between the two ends of the main valve orifice 10 is ΔP = P1-P _LS ; P1 acts on the left end of the spool of the load-sensitive control valve 13, P _LS and the preset spring pressure P _K (fixed value) act together on the right end of the spool of the load-sensitive control valve 13. When the force of the load-sensitive control valve 13 is balanced, P _K =P1-P _LS =ΔP, the plunger pump 18 maintains a stable displacement; if the opening of the main valve throttle 10 changes, the dynamic ΔP will is greater than or less than P _K , at this time, in order to restore the valve core of the load-sensitive control valve 13 to the force balance state, the load-sensitive control valve 13 automatically adjusts the displacement q of the plunger pump 18, changes the output flow Q of the plunger pump 18, and re- Let ΔP=P _K =constant value.

Introducing the working condition of the pressure cut-off control valve 14: In the system shown in Figure 1, when the system working pressure exceeds the spring force of the pressure cut-off control valve 14, the pressure P acts on the left end of the valve core of the pressure cut-off control valve 14, pushing the pressure cut-off The spool of the control valve 14 moves to the right, causing the pressure P to enter the small control piston 16 through the pressure cut-off control valve 14, pushing the small control piston 16 to the left, converting the plunger pump 18 to the minimum displacement, and stopping the corresponding actuator of the engine. work to prevent overloading. At this time, only a small amount of oil overflows through the pressure cut-off control valve 14, and the system pressure is maintained at the set pressure of the pressure cut-off control valve 14, which minimizes the power loss and heat generation of the system.

Introducing the working situation of the constant power control valve 15: In the system shown in Figure 1, the working pressure acts on the rocker 17 through the constant power control valve 15, and the external adjustable spring force offsets this, which determines the constant power variable pressure setting P2 . If the working pressure exceeds the setting force P2 of the spring, the constant power control valve 15 drives the rocker 17, and the rocker 17 drives the plunger pump 18 to turn the pump back (towards qgmin). The increase in the working pressure P is proportional to the decrease in the displacement q. , so that P*q=C (constant), to achieve the purpose of constant power variable control.

When the engine speed increases, the effective output torque of the engine is greater than M _fmax , where M _fmax = p _max *q _max , p _max is the maximum working pressure of the system, and q _max is the maximum displacement of the plunger pump. At this time, the solenoid valve 12 is powered, the constant power control valve 15 is cut off, and the constant power control valve 15 is inactive. The entire displacement of the plunger pump 18 participates in driving the actuator, and the working speed of the corresponding actuator of the engine is increased, thereby improving the work efficiency.

Under heavy load conditions (system pressure is greater than spring setting force P2), the constant power control valve 15 continues to function. In the stage from engine speed n1 (generally referred to as idle speed) and output torque M1 (M ₁ =P2*q _max ) to engine speed n2 and output torque M _fmax , because the effective output torque of the engine is less than M _fmax at this time, the solenoid valve 12 fails. Electrically, the constant power control valve 15 works. In order to prevent the engine from stalling, the constant power control valve 15 puts the system in a constant torque state. Only part of the displacement of the plunger pump 18 is involved in the work, and the corresponding actuator of the engine cannot work at the maximum speed, and the work efficiency is affected; the engine is in a power-rich state, and the excess torque cannot participate in doing work.

It can be seen from the above that if the solenoid valve 12 is provided in the system for control, there are the above defects. Further, the specific implementation details and advantages of using the proportional pressure reducing valve 21 for control in the embodiment of the present invention are introduced below.

The engineering equipment includes an engine, a proportional pressure reducing valve 21, a plunger pump 18 and a constant power control valve 15. The constant power control valve 15 is connected to the proportional pressure reducing valve 21 and the plunger pump 18 respectively. Figure 2 schematically shows a flow chart of a control method for engineering equipment according to an embodiment of the present invention. As shown in Figure 2, in one embodiment of the present invention, a control method for engineering equipment is provided, including the following steps:

Step 201, determine the first effective output torque of the engine under the first working condition;

Step 202, determine the second effective output torque of the engine under the second operating condition;

Step 203, determine the current effective output torque of the engine;

Step 204, determine the input current of the proportional pressure reducing valve 21 according to the first effective output torque, the second effective output torque and the current effective output torque to determine the output pressure of the proportional pressure reducing valve 21;

Step 205, adjust the torque control value of the constant power control valve 15 according to the output pressure of the proportional pressure reducing valve 21 to adjust the displacement of the plunger pump 18, thereby adjusting the working speed of the corresponding actuator of the engine. The control valve 15 is controlled based on torque. value to keep the power of the plunger pump 18 constant.

In the embodiment of the present invention, the effective output torque of the engine is detected, and the input current of the proportional pressure reducing valve 21 is controlled according to the effective output torque of the engine. Specifically, when the effective output torque of the engine increases, the input current of the proportional pressure reducing valve 21 is increased, so that the output pressure of the proportional pressure reducing valve 21 is increased, and the torque control value of the constant power control valve 15 is increased. As a result, the displacement of the plunger pump 18 is increased. In this way, the working speed of the actuator under heavy load conditions is effectively increased and the work efficiency is improved. By detecting the effective output torque of the engine, the output pressure of the proportional pressure reducing valve 21 increases in proportion to the effective output torque of the engine, so that the effective output torque of the engine can fully participate in the operation and reduce torque waste. Under heavy load conditions, the utilization of the engine's effective torque is improved.

The control method for engineering equipment according to the embodiment of the present invention will be specifically described below with a specific embodiment.

Figure 3 schematically shows a hardware connection diagram of engineering equipment according to an embodiment of the present invention.

The invention discloses a constant power variable automatic adjustment control method of a plunger pump. Can be combined with Figure 2. The first working condition (such as idling condition): the variable starting point pressure P1 of the constant power control valve, corresponding to the engine speed n1 and the effective output torque M1 of the engine. The second working condition: the highest working pressure of the system P2, which corresponds to the normal operating engine speed n2 of the maximum displacement and the effective output torque M2 of the engine. Under heavy load conditions, the engine speed increases to n, and the current effective output torque of the engine is M. Compared with the reference torque M1, the input current of the proportional pressure reducing valve 21 can be obtained through the following formula (1):

Output current I to the pilot pressure reducing valve 21, the output pressure P' of the pressure reducing valve 21, the pressure variable point of the constant power control valve 15 is raised to P', pushing the small control piston 16 to move to the right, and the small control piston 16 drives the rocker 17 By moving to the right, the displacement of the plunger pump 18 increases, the output flow rate increases, and the working speed of the corresponding actuator of the engine increases, effectively improving the working efficiency of the actuator.

In the formula M=P*q=C (constant), M is torque, P is working pressure, and q is displacement. After the pressure variable point of the constant power control valve 15 is increased, the torque control value of the constant power control valve will also be increased, so that the displacement will increase.

In the control logic of constant power control automatic adjustment, after the engine torque increases, the current of the electric proportional pressure reducing valve 21 increases, the output pressure of the electric proportional pressure reducing valve 21 increases, and the starting point of the constant power control valve 15 increases. The displacement of plug pump 18 is increased.

FIG. 4 schematically shows a graph of the output torque of the engine and the current of the proportional pressure reducing valve according to an embodiment of the present invention. Constant power variable point parameters: pressure P1, engine speed n1, torque M ₁ =P ₁ *q _max of the constant power variable control valve 15, and the current of the proportional pressure reducing valve 21 is zero. Maximum load torque parameters: pressure P _max , engine speed n2, load maximum torque M2 = P _max *q _max , the current of the proportional pressure reducing valve 21 is the maximum value, the current percentage is 100%, the current percentage is the proportional pressure reducing valve 21 The input current is a percentage of the maximum allowable current of the proportional pressure reducing valve 21.

The current of the electric proportional pressure reducing valve 21 is related to the change value of the effective output torque of the engine. When the effective output torque of the engine is M1, the current of the proportional pressure reducing valve 21 is zero, and the variable pressure of the constant power control valve 15 is P1. When the effective output torque of the engine is M2, the current percentage of the proportional pressure reducing valve 21 is 100%, and the variable pressure of the constant power control valve 15 is increased to P _max .

FIG. 5 schematically shows a graph of current and pressure of a proportional pressure reducing valve according to an embodiment of the present invention. As the output torque of the engine increases, the current of the electric proportional pressure reducing valve 21 increases linearly, and the output pressure of the pressure reducing valve 21 increases proportionally. The constant power control valve 15 drives the rocker 17 to increase the output displacement of the plunger pump 18 Increase. When the engine speed increases from n1 to n, the output torque of the engine is M, and the current of the proportional pressure reducing valve 21 is:

The variable pressure of the constant power control valve 15 increases to P', pushing the small control piston 16 to move to the right. The small control piston 16 drives the rocker 17 to move to the right, and the displacement of the plunger pump 18 increases. Until the engine speed rises to n2, the effective output torque reaches the maximum value M2, the variable pressure of the constant power control valve 15 increases to P _max , the entire displacement of the plunger pump 18 participates in the work, and the corresponding actuator of the engine works at the maximum speed.

In the embodiment of the present invention, under heavy load conditions and the engine does not stall, by adding a new control method of an electric proportional pressure reducing valve, the effective output torque of the engine is maximized, so that the displacement of the plunger pump 18 is increased, and the displacement of the plunger pump 18 is effectively increased. improve the working efficiency of the actuator. In the embodiment of the present invention, by detecting the effective output torque of the engine, the displacement of the plunger pump 18 increases with the increase of the effective output torque of the engine under heavy load conditions, and the working speed of the actuator increases accordingly, effectively improving the execution efficiency. Component efficiency.

In the embodiment of the present invention, by detecting the effective output torque of the engine, the output pressure of the electric proportional pressure reducing valve 21 is increased in proportion to the effective output torque of the engine, so that the effective output torque of the engine can fully participate in the operation without wasting torque. Under heavy load conditions, the utilization of the engine's effective torque is improved.

In one embodiment, the current of the electric proportional pressure reducing valve 21 may also be related to the engine speed signal. Since the engine speed has an approximately linear relationship with the effective output torque before reaching the maximum effective output torque M _fmax of the engine, it is feasible to use the engine speed signal as the control signal. The engine speed increases, the current of the electric proportional pressure reducing valve 21 increases, the output pressure of the proportional pressure reducing valve 21 increases, and the constant power control valve 15 drives the rocker 17 to increase the output displacement of the plunger pump 18.

In the embodiment of the present invention, under heavy load conditions, if the effective output torque M of the engine exceeds the torque setting value M1 of the constant power control valve 15, the effective output torque signal of the engine controls the electric proportional pressure reducing valve 21. The increase in current increases the output pressure of the electric proportional pressure reducing valve 21, increases the torque control value of the constant power control valve 15, and subsequently increases the displacement of the plunger pump 18, effectively improving the work of the actuator under heavy load conditions. speed, improving work efficiency.

An embodiment of the present invention provides a processor configured to execute any one of the control methods for engineering equipment in the above embodiments.

The engineering equipment includes an engine, a proportional pressure reducing valve, a plunger pump and a control valve. The control valve is connected to the proportional pressure reducing valve and the plunger pump respectively.

Specifically, the processor can be configured to:

Determine the current effective output torque of the engine;

In this embodiment of the invention, the processor is configured to:

The first working condition includes the idling condition; the second working condition includes: the load pressure of the corresponding actuator of the engine is the largest and the displacement of the plunger pump is the largest.

In this embodiment of the invention, the processor is configured to:

The input current of the proportional pressure reducing valve satisfies the following formula (1):

I＝(M-M1)/(M2-M1)*100% Formula (1)

I represents the current percentage of the proportional pressure reducing valve when the effective output torque of the engine is M. The current percentage is the percentage of the input current and the maximum allowable current of the proportional pressure reducing valve. M represents the current effective output torque of the engine. M1 represents the engine. The effective output torque under idling conditions, M2 represents the effective output torque of the engine under the second operating condition.

In this embodiment of the invention, the processor is configured to:

Adjust the torque control value of the control valve according to the output pressure of the proportional pressure reducing valve to adjust the displacement of the plunger pump, thereby adjusting the working speed of the corresponding actuator of the engine, including:

In this embodiment of the invention, the processor is configured to:

Increasing the variable pressure of the control valve includes:

The variable pressure of the control valve is increased according to the increase in the output pressure of the proportional pressure reducing valve; and/or the variable pressure of the control valve is increased according to the increase in the current of the proportional pressure reducing valve.

In the embodiment of the present invention, the engineering equipment also includes a control piston and a rocker. The control piston is connected to the control valve and the rocker respectively. The rocker is connected to the plunger pump. The processor is configured to:

In this embodiment of the invention, the execution element includes an oil pump, and the processor is configured to:

When the power of the plunger pump is constant, the torque of the oil pump satisfies the following formula (2):

M3＝P*q＝C Formula (2)

M3 represents the torque of the oil pump, P represents the working pressure of the oil pump, q represents the displacement of the oil pump, C is the constant corresponding to the torque control value of the control valve, and C increases when the torque control value increases.

In this embodiment of the invention, the processor is configured to:

During the change from the first working condition to the second working condition, the engine speed increases and the effective output torque of the engine increases.

An embodiment of the present invention provides engineering equipment, including the above-mentioned processor.

The preferred embodiments of the present invention are described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the specific details of the above embodiments. Within the scope of the technical concept of the present invention, various simple modifications can be made to the technical solution of the present invention. These simple modifications all belong to the protection scope of the present invention.

In addition, it should be noted that the specific technical features described in the above-mentioned specific embodiments can be combined in any suitable manner as long as there is no contradiction. In order to avoid unnecessary repetition, various possible combinations are not further described in the present invention.

In addition, any combination of various embodiments of the present invention can also be carried out. As long as they do not violate the idea of the present invention, they should also be regarded as the disclosed content of the present invention.

Claims

A control method for engineering equipment, characterized in that the engineering equipment includes an engine, a proportional pressure reducing valve, a plunger pump and a control valve, and the control valve is connected to the proportional pressure reducing valve and the plunger respectively. Pump connection, the control method includes:

Determine the first effective output torque of the engine under the first operating condition;

Determine the second effective output torque of the engine under the second operating condition;

Determining the current effective output torque of the engine;

Determine the input current of the proportional pressure reducing valve according to the first effective output torque, the second effective output torque and the current effective output torque to determine the output pressure of the proportional pressure reducing valve;

The torque control value of the control valve is adjusted according to the output pressure of the proportional pressure reducing valve to adjust the displacement of the plunger pump, thereby adjusting the working speed of the corresponding actuator of the engine, wherein the control valve is based on The torque control value is used to keep the power of the plunger pump constant.
The control method according to claim 1, characterized in that the first operating condition includes an idle operating condition; the second operating condition includes: the load pressure of the corresponding actuator of the engine is the largest, and the plunger pump has the largest displacement.
The control method according to claim 2, characterized in that the input current of the proportional pressure reducing valve satisfies the following formula (1):

I＝(M-M1)/(M2-M1)*100% Formula (1)

Wherein, I represents the current percentage of the proportional pressure reducing valve when the effective output torque of the engine is M, and the current percentage is the percentage of the input current and the maximum allowable current of the proportional pressure reducing valve, M represents the current effective output torque of the engine, M1 represents the effective output torque of the engine under idle speed, and M2 represents the effective output torque of the engine under the second operating condition.
The control method according to claim 2, characterized in that the torque control value of the control valve is adjusted according to the output pressure of the proportional pressure reducing valve to adjust the displacement of the plunger pump, thereby adjusting the Describe the working speed of the corresponding actuators of the engine, including:

During the change from the first working condition to the second working condition, when the effective output torque of the engine increases, the current of the proportional pressure reducing valve is increased, so that the proportional pressure reducing valve The output pressure of the valve increases, which increases the variable pressure of the control valve, causing the torque control value of the control valve to increase, thereby increasing the displacement of the plunger pump, causing the working speed of the actuator to increase. big.
The control method according to claim 4, characterized in that said increasing the variable pressure of the control valve includes:

Increase the variable pressure of the control valve according to the increase in the output pressure of the proportional pressure reducing valve; and/or

The variable pressure of the control valve is increased according to the increased value of the current of the proportional pressure reducing valve.
The control method according to claim 4, wherein the engineering equipment further includes a control piston and a rocker, the control piston is connected to the control valve and the rocker respectively, and the rocker is connected to the rocker. The plunger pump is connected, and the control method also includes:

When the variable pressure of the control valve increases, the control piston is pushed to move and the rocker is driven to move, so that the displacement of the plunger pump increases, thereby increasing the working speed of the actuator. big.
The control method according to claim 1, wherein the actuator includes an oil pump, and when the power of the plunger pump is constant, the torque of the oil pump satisfies the following formula (2):

M3＝P*q＝C Formula (2)

Among them, M3 represents the torque of the oil pump, P represents the working pressure of the oil pump, q represents the displacement of the oil pump, C is the constant corresponding to the torque control value of the control valve, and when the torque control value increases When the value is large, C increases.
The control method according to claim 1, characterized in that during the change from the first working condition to the second working condition, the rotation speed of the engine increases and the effective output torque of the engine increases.
A processor, characterized in that it is configured to execute the control method for engineering equipment according to any one of claims 1 to 8.
Engineering equipment, characterized by comprising the processor according to claim 9.