Control method, processor and engineering equipment for engineering equipment

Abstract

The present invention relates to the technical field of engineering machinery, and discloses a control method, a processor and engineering equipment 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, and the control method includes: determining the first effective output torque of the engine under the first working condition; determining the second effective output torque of the engine under the second working condition; determining the current effective output torque of the engine; determining 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; 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. The effective output torque of the engine can fully participate in the operation, improve the utilization rate of the effective torque of the engine, and improve work efficiency.

Description

Technical Field

[0001] The present invention relates to the technical field of engineering machinery, and in particular to a control method, a processor and engineering equipment for engineering equipment. Background Art

[0002] With the rapid development of construction machinery and the implementation of environmental protection policies, the power and torque of engines for construction machinery are gradually becoming smaller when designing and selecting to meet the requirements of driving and operation. In order to meet the requirements of various operating conditions and avoid engine flameout under heavy load conditions or excessive matching of engine power and torque, the construction machinery industry generally uses constant power variable piston pumps, which not only reduces energy consumption but also meets the requirements of various operating conditions.

[0003] Constant power variable piston pump: In order to prevent the engine (or motor) from exceeding its rated output torque, which will cause the engine to instantly shut down and fail to work normally, a control valve is designed for the piston pump. When 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 M of the oil pump = P*q = C (constant), and the torque of the oil pump remains unchanged. A variable piston pump with this type of constant torque control device is called a constant power variable piston pump.

[0004] Under heavy load conditions, the constant power control valve continues to work. 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 a part of the displacement of the plunger pump is involved in the work, and the corresponding actuator of 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 be used to do work. Summary of the invention

[0005] In order to overcome the deficiencies in the prior art, an embodiment of the present invention provides a control method, a processor and engineering equipment for engineering equipment.

[0006] 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, and the control method includes:

[0007] determining a first effective output torque of the engine under a first operating condition;

[0008] determining a second effective output torque of the engine under a second operating condition;

[0009] determining a current effective output torque of the engine;

[0010] Determine an 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, so as to determine an output pressure of the proportional pressure reducing valve;

[0011] 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.

[0012] In the embodiment of the present invention, 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 maximum, and the displacement of the plunger pump is maximum.

[0013] In the embodiment of the present invention, the input current of the proportional pressure reducing valve satisfies the following formula (1):

[0014] I=(M-M1) / (M2-M1)*100% Formula (1)

[0015] 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 to 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 conditions, and M2 represents the effective output torque of the engine under the second condition.

[0016] In an embodiment of the present invention, 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:

[0017] In the process of changing from the first operating condition to the second operating 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 increases, and the variable pressure of the control valve is increased, so that the torque control value of the control valve increases, thereby increasing the displacement of the plunger pump and increasing the working speed of the actuator.

[0018] In an embodiment of the present invention, increasing the variable pressure of the control valve includes:

[0019] Increasing the variable pressure of the control valve according to the increase in the output pressure of the proportional pressure reducing valve; and / or

[0020] The variable pressure of the control valve is increased according to the increase in the current of the proportional pressure reducing valve.

[0021] In an embodiment of the present invention, the engineering equipment further 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, and the control method further includes:

[0022] 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, and then the working speed of the actuator increases.

[0023] In an embodiment of the present invention, 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):

[0024] M3=P*q=C Formula (2)

[0025] 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, and C is a constant corresponding to the torque control value of the control valve, and C increases when the torque control value increases.

[0026] In the embodiment of the present invention, during the process of changing from the first operating condition to the second operating condition, the speed of the engine increases and the effective output torque of the engine increases.

[0027] A second aspect of the present invention provides a processor configured to execute the above-mentioned control method for engineering equipment.

[0028] A third aspect of the present invention provides an engineering device, comprising the above-mentioned processor.

[0029] In an 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 increases, the torque control value of the constant power control valve is increased, and the displacement of the plunger pump is increased accordingly. In this way, the working speed of the actuator under heavy load conditions is effectively improved, and the working efficiency is improved. By detecting the effective output torque of the engine, the output pressure of the proportional pressure reducing valve 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, reducing torque waste. Under heavy load conditions, the utilization rate of the effective torque of the engine is improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The accompanying drawings are used to provide a further understanding of the embodiments of the present invention and constitute a part of the specification. Together with the following specific implementations, they are used to explain the embodiments of the present invention, but do not constitute a limitation on the embodiments of the present invention. In the accompanying drawings:

[0031] Figure 1 One of the hardware connection diagrams of the engineering equipment is schematically shown;

[0032] Figure 2 A flow chart of a control method for engineering equipment according to an embodiment of the present invention is schematically shown;

[0033] Figure 3 Schematically shows a hardware connection diagram of an engineering device according to an embodiment of the present invention;

[0034] Figure 4 A curve diagram schematically showing the output torque of an engine and the current of a proportional pressure reducing valve according to an embodiment of the present invention;

[0035] Figure 5 A graph schematically shows current and pressure of a proportional pressure reducing valve according to an embodiment of the present invention.

[0036] Description of Reference Numerals

[0037] 10-main valve throttle; 11-damping;

[0038] 12-Solenoid valve; 13-Load sensing control valve;

[0039] 14-pressure cut-off control valve; 15-constant power control valve;

[0040] 16- small control piston; 17- rocker;

[0041] 18- plunger pump; 19- large control piston;

[0042] 20-Oil tank; 21-Proportional pressure reducing valve. DETAILED DESCRIPTION

[0043] The specific implementation of the embodiment of the present invention is described in detail below in conjunction with the accompanying drawings. It should be understood that the specific implementation described here is only used to illustrate and explain the embodiment of the present invention, and is not used to limit the embodiment of the present invention.

[0044] It should be noted that if the implementation methods of the present application involve directional indications (such as up, down, left, right, front, back...), such directional indications are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0045] In addition, if there are descriptions involving "first", "second", etc. in the implementation methods of this application, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or suggesting their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the technical solutions between the various implementation methods can be combined with each other, but they must be based on the ability of ordinary technicians in the field to implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by this application.

[0046] In order to facilitate understanding of the specific implementation details and advantages of using a proportional control valve for control in the embodiment of the present invention, first of all, Figure 1 To describe the control scheme using solenoid valves, Figure 1 One of the hardware connection diagrams of the engineering equipment is schematically shown.

[0047] Constant power variable piston pump: In order to prevent the engine (or motor) from exceeding its rated output torque, which will cause the engine to instantly shut down and fail to work normally, a control valve is designed for the piston pump. The displacement q of the oil pump is inversely proportional to the working pressure P. When 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), and the torque M of the oil pump remains unchanged. A variable piston pump with this type of constant torque control device is called a constant power variable piston pump.

[0048] With the rapid development of construction machinery and the implementation of environmental protection policies, the power and torque of engines used in construction equipment are gradually becoming smaller when designing and selecting to meet the requirements of driving and operation. In order to meet the requirements of various operating conditions and avoid engine flameout under heavy load conditions or excessive matching of engine power and torque, constant power variable piston pumps are widely used in the construction machinery industry, which not only reduces energy consumption but also meets the requirements of various operating conditions.

[0049] Figure 1 The figure shows the control system of a constant power variable displacement piston pump using a solenoid valve. Figure 1 As shown, the control system of the constant power variable piston pump involves: a main valve throttle 10, a damper 11, a solenoid valve 12, a load sensing control valve 13, a pressure cut-off control valve 14, a constant power control valve 15, a small control piston 16, a rocker 17, a piston pump 18, a large control piston 19 and an oil tank 20.

[0050] exist Figure 1 In the system shown, in the non-working state, the corresponding actuators of the engine do not work, the system pressure is at a low state, and under the action of the spring force, the large control piston 19 quickly resets and the plunger pump 18 is converted to the minimum displacement, reducing the power loss and heat generation of the system.

[0051] Introduce the working condition of load sensing control valve 13: Figure 1 In the system shown, 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 throttle port 10. The pressure difference across the main valve throttle port 10 is ΔP = P1-P LS ; P1 acts on the left end of the valve core of the load sensing control valve 13, P LSWith preset spring pressure P K (fixed value) act together on the right end of the valve core of the load sensing control valve 13. When the load sensing 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 be greater or less than P K At this time, in order to restore the valve core of the load-sensing control valve 13 to a force-balanced state, the load-sensing 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-enables ΔP=P K =fixed value.

[0052] Introduce the working condition of the pressure cut-off control valve 14: Figure 1 In the system shown, 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 valve core of the pressure cut-off control valve 14 to the right, so that the pressure P enters 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 to prevent overload. 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.

[0053] Introduce the working condition of constant power control valve 15: Figure 1 In the system shown, 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), and the increase in working pressure P is proportional to the decrease in displacement q, so that P*q=C (constant), achieving the purpose of constant power variable control.

[0054] 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, q max is the maximum displacement of the plunger pump. At this time, the solenoid valve 12 is energized, the constant power control valve 15 is cut off, and the constant power control valve 15 does not work. The full displacement of the plunger pump 18 is used to drive the actuator, and the corresponding actuator of the engine works faster, thereby improving work efficiency.

[0055] Under heavy load conditions (system pressure is greater than the spring setting force P2), the constant power control valve 15 continues to work. max ) to engine speed n2, output torque M fmax stage, because at this time the effective output torque of the engine is less than M fmax , the solenoid valve 12 loses power, and the constant power control valve 15 takes effect. 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, which affects the work efficiency; the engine is in a state of abundant power, and the excess torque cannot participate in work.

[0056] From the above content, it can be known that if the solenoid valve 12 is set in the system for control, the above defects exist. 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.

[0057] 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 The flowchart of the control method for engineering equipment according to an embodiment of the present invention is schematically shown. Figure 2 As shown, in one embodiment of the present invention, a control method for engineering equipment is provided, comprising the following steps:

[0058] Step 201, determining a first effective output torque of the engine under a first operating condition;

[0059] Step 202, determining a second effective output torque of the engine under a second operating condition;

[0060] Step 203, determining the current effective output torque of the engine;

[0061] Step 204, determining 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, so as to determine the output pressure of the proportional pressure reducing valve 21;

[0062] 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 keeps the power of the plunger pump 18 constant based on the torque control value.

[0063] In an 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 increases, the torque control value of the constant power control valve 15 is increased, and the displacement of the plunger pump 18 is increased accordingly. In this way, the working speed of the actuator under heavy load conditions is effectively improved, and the working efficiency is improved. By detecting the effective output torque of the engine, the output pressure of the proportional pressure reducing valve 21 increases proportionally with the effective output torque of the engine, so that the effective output torque of the engine can fully participate in the operation, reducing torque waste. Under heavy load conditions, the utilization rate of the effective torque of the engine is improved.

[0064] The control method for engineering equipment according to an embodiment of the present invention is described in detail below with reference to a specific embodiment.

[0065] Figure 3 The hardware connection diagram of the engineering equipment according to the embodiment of the present invention is schematically shown.

[0066] The present invention discloses a plunger pump constant power variable automatic adjustment control method. Figure 2 . The first working condition (e.g., idling condition): the variable starting pressure P1 of the constant power control valve corresponds to the engine speed n1 and the effective output torque M1 of the engine. The second working condition: the maximum working pressure P2 of the system corresponds to the 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 by the following formula (1):

[0067]

[0068] The output current I is sent to the pilot pressure reducing valve 21, the output pressure of the pressure reducing valve 21 is P', and the pressure variable point of the constant power control valve 15 is increased to P', pushing the small control piston 16 to move right, and the small control piston 16 drives the rocker 17 to move right, the displacement of the plunger pump 18 is increased, the output flow rate is increased, and the working speed of the corresponding actuator of the engine is improved, which effectively improves the working efficiency of the actuator.

[0069] In the formula M=P*q=C (constant), M is torque, P is working pressure, and q is displacement. When 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.

[0070] In the control logic of the 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, the starting point of the constant power control valve 15 increases, and the displacement of the plunger pump 18 increases.

[0071] Figure 4 The output torque of the engine and the current of the proportional pressure reducing valve according to the embodiment of the present invention are schematically shown. Constant power variable point parameters: pressure P1, engine speed n1, torque M1 of the constant power variable control valve 15 = P1*q max , the current of proportional pressure reducing valve 21 is zero. Maximum load torque parameter: 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%, and the current percentage is the percentage of the input current of the proportional pressure reducing valve 21 to the maximum allowable current of the proportional pressure reducing valve 21.

[0072] 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 .

[0073] Figure 5 The current and pressure curve of the proportional pressure reducing valve according to the embodiment of the present invention is schematically shown. 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. 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:

[0074]

[0075] The variable pressure of the constant power control valve 15 is increased to P', pushing the small control piston 16 to move right, and the small control piston 16 drives the rocker 17 to move right, and the displacement of the plunger pump 18 increases. Until the engine speed rises to n2 and the effective output torque reaches the maximum value M2, the variable pressure of the constant power control valve 15 is increased to P max , the full displacement of the plunger pump 18 is involved in the work, and the corresponding actuator of the engine works at the maximum speed.

[0076] In the embodiment of the present invention, under heavy-load conditions and when the engine is not turned off, the effective output torque of the engine is maximized by adding a new control method of an electric proportional pressure reducing valve, so that the displacement of the plunger pump 18 is increased, and the working efficiency of the actuator is effectively improved. In the embodiment of the present invention, by detecting the effective output torque of the engine, the displacement of the plunger pump 18 under heavy-load conditions increases with the increase of the effective output torque of the engine, and the working speed of the actuator is increased accordingly, which effectively improves the working efficiency of the actuator.

[0077] 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 torque waste. Under heavy load conditions, the utilization rate of the effective torque of the engine is improved.

[0078] In one embodiment, the current of the electric proportional pressure reducing valve 21 may also be related to the engine speed signal. fmax Previously, the engine speed and the effective output torque were approximately linearly related, so it was feasible to use the engine speed signal as the control signal. As 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.

[0079] In an 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 current of the electric proportional pressure reducing valve 21 is increased by controlling the effective output torque signal of the engine, so that the output pressure of the electric proportional pressure reducing valve 21 is increased, and the torque control value of the constant power control valve 15 is increased, thereby increasing the displacement of the plunger pump 18, thereby effectively increasing the working speed of the actuator under heavy load conditions and improving work efficiency.

[0080] An embodiment of the present invention provides a processor, which is configured to execute any one of the control methods for engineering equipment in the above embodiments.

[0081] 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 pump respectively.

[0082] Specifically, the processor may be configured to:

[0083] determining a first effective output torque of the engine under a first operating condition;

[0084] determining a second effective output torque of the engine under a second operating condition;

[0085] determining a current effective output torque of the engine;

[0086] Determine an 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, so as to determine an output pressure of the proportional pressure reducing valve;

[0087] 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.

[0088] In an embodiment of the present invention, the processor is configured to:

[0089] 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 maximum, and the displacement of the plunger pump is maximum.

[0090] In an embodiment of the present invention, the processor is configured to:

[0091] The input current of the proportional pressure reducing valve satisfies the following formula (1):

[0092] I=(M-M1) / (M2-M1)*100% Formula (1)

[0093] 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 to 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 conditions, and M2 represents the effective output torque of the engine under the second condition.

[0094] In an embodiment of the present invention, the processor is configured to:

[0095] 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, including:

[0096] In the process of changing from the first operating condition to the second operating 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 increases, and the variable pressure of the control valve is increased, so that the torque control value of the control valve increases, thereby increasing the displacement of the plunger pump and increasing the working speed of the actuator.

[0097] In an embodiment of the present invention, the processor is configured to:

[0098] Increasing the variable pressure of the control valve includes:

[0099] 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.

[0100] In an embodiment of the present invention, the engineering equipment further 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, and the processor is configured as follows:

[0101] 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, and then the working speed of the actuator increases.

[0102] In an embodiment of the present invention, the actuator includes an oil pump, and the processor is configured to:

[0103] When the power of the plunger pump is constant, the torque of the oil pump satisfies the following formula (2):

[0104] M3=P*q=C Formula (2)

[0105] 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, and C is a constant corresponding to the torque control value of the control valve, and C increases when the torque control value increases.

[0106] In an embodiment of the present invention, the processor is configured to:

[0107] In the process of changing from the first operating condition to the second operating condition, the engine speed increases and the effective output torque of the engine increases.

[0108] An embodiment of the present invention provides an engineering device, including the above-mentioned processor.

[0109] Those skilled in the art will appreciate that the embodiments of the present application may be provided as methods, systems, or computer program products. Therefore, the present application may adopt the form of a complete hardware embodiment, a complete software embodiment, or an embodiment in combination with software and hardware. Moreover, the present application may adopt the form of a computer program product implemented in one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) that include computer-usable program code.

[0110] The present application is described with reference to the flowcharts and / or block diagrams of the methods, devices (systems), and computer program products according to the embodiments of the present application. It should be understood that each process and / or box in the flowchart and / or block diagram, as well as the combination of the processes and / or boxes in the flowchart and / or block diagram, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing device to generate a machine, so that the instructions executed by the processor of the computer or other programmable data processing device generate instructions for implementing the processes in the flowchart and / or block diagram. Figure 1 A process or multiple processes and / or boxes Figure 1 A device that provides the functions specified in a block or multiple blocks.

[0111] These computer program instructions may also be stored in a computer-readable memory capable of directing a computer or other programmable data processing device to operate in a specific manner, so that the instructions stored in the computer-readable memory produce an article of manufacture comprising an instruction device, which implements the process Figure 1 A process or multiple processes and / or boxes Figure 1 A function specified in one or more boxes.

[0112] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operating steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing instructions for implementing the process. Figure 1 A process or multiple processes and / or boxes Figure 1 A step that specifies a function in one or more boxes.

[0113] In a typical configuration, a computing device includes one or more processors (CPU), input / output interfaces, network interfaces, and memory.

[0114] The memory may include non-permanent memory in a computer-readable medium, random access memory (RAM) and / or non-volatile memory in the form of read-only memory (ROM) or flash RAM. The memory is an example of a computer-readable medium.

[0115] Computer readable media include permanent and non-permanent, removable and non-removable media that can be implemented by any method or technology to store information. Information can be computer readable instructions, data structures, program modules or other data. Examples of computer storage media include, but are not limited to, phase change memory (PRAM), static random access memory (SRAM), dynamic random access memory (DRAM), other types of random access memory (RAM), read-only memory (ROM), electrically erasable programmable read-only memory (EEPROM), flash memory or other memory technology, compact disk read-only memory (CD-ROM), digital versatile disk (DVD) or other optical storage, magnetic cassettes, magnetic tape magnetic disk storage or other magnetic storage devices or any other non-transmission media that can be used to store information that can be accessed by a computing device. As defined herein, computer readable media does not include temporary computer readable media (transitory media), such as modulated data signals and carrier waves.

[0116] It should also be noted that the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, commodity or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, commodity or device. In the absence of more restrictions, the elements defined by the sentence "comprises a ..." do not exclude the existence of other identical elements in the process, method, commodity or device including the elements.

[0117] The above are only embodiments of the present application and are not intended to limit the present application. For those skilled in the art, the present application may have various changes and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included within the scope of the claims of the present application.

Claims

1. 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, wherein the control valve is connected to the proportional pressure reducing valve and the plunger pump respectively, and the control method includes: Determining a first effective output torque of the engine under a first operating condition, wherein the first operating condition includes an idle operating condition; Determining a second effective output torque of the engine under a second working condition, wherein the second working condition includes: a load pressure of a corresponding actuator of the engine is maximum, and a displacement of the plunger pump is maximum; determining a current effective output torque of the engine; According to the first effective output torque, the second effective output torque and the current effective output torque, the input current of the proportional pressure reducing valve is determined to determine the output pressure of the proportional pressure reducing valve, wherein 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, the current percentage is the percentage of the input current to the maximum allowable current of the proportional pressure reducing valve, M represents the current effective output torque of the engine, M1 represents the first effective output torque of the engine under the idle condition, and M2 represents the second effective output torque of the engine under the second condition; 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 keeps the power of the plunger pump constant based on the torque control value.

2. The control method according to claim 1, characterized in that: The method of 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 process of changing from the first operating condition to the second operating 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 increases, and the variable pressure of the control valve is increased, so that the torque control value of the control valve increases, thereby increasing the displacement of the plunger pump and increasing the working speed of the actuator.

3. The control method according to claim 2, characterized in that: Increasing the variable pressure of the control valve comprises: Increasing 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 value of the current of the proportional pressure reducing valve.

4. The control method according to claim 2, characterized in that: The engineering equipment further includes a control piston and a rocker, wherein the control piston is connected to the control valve and the rocker respectively, and the rocker is connected to the plunger pump. The control method further includes: When the variable pressure of the control valve increases, the control piston is pushed to move, and the rocker arm is driven to move, so that the displacement of the plunger pump increases, thereby increasing the working speed of the actuator.

5. The control method according to claim 1, characterized in that: 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, and C is a constant corresponding to the torque control value of the control valve, and C increases when the torque control value increases.

6. The control method according to claim 1, characterized in that: During the process of changing from the first operating condition to the second operating condition, the rotation speed of the engine increases and the effective output torque of the engine increases.

7. A processor, characterized in that: The method is configured to execute the control method for engineering equipment according to any one of claims 1 to 6.

8. An engineering equipment, characterized in that: Comprising a processor according to claim 7.

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