Hydrostatic loader fuel consumption reduction control method, apparatus, and medium

Abstract

The embodiment of the application discloses a kind of static hydraulic loader control method of reducing oil consumption, equipment and medium.It belongs to the technical field of loader, solve the problem of large oil consumption in static hydraulic loader market due to complex working condition demand in prior art.The method comprises, after static hydraulic loader vehicle ignition starts, determine the average of engine actual target speed and the average of hydraulic system pump end pressure in preset time period;The average of engine actual target speed and the average of hydraulic system pump end pressure are compared with the preset working condition threshold value respectively to determine the market working condition of static hydraulic loader;The hydraulic system motor efficiency corresponding to the static hydraulic loader is obtained, and different motor flow distribution schemes are constructed based on the hydraulic system motor efficiency;The market working condition of static hydraulic loader is matched with different motor flow distribution schemes, to control the oil consumption of static hydraulic loader based on the matched scheme.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of loaders, and particularly relates to a hydrostatic loader oil consumption reduction control method, equipment and medium. BACKGROUND

[0002] The loader is a kind of earthwork construction machinery widely used in highway, railway, building, water and electricity, port and mine construction engineering, which is mainly used for shoveling soil, sand, lime, coal and other bulk materials, and can also be used for light digging of ore and hard soil. By replacing different auxiliary working devices, the loader can also be used for pushing soil, lifting and unloading other materials such as wood.

[0003] The working system and the running system of the hydrostatic loader in the prior art are both hydraulic drive loaders. The running system is mainly composed of pumps and motors, and the forward movement, backward movement and speed regulation of the loader in the running process are realized by controlling the pressure, flow and direction of hydraulic oil.

[0004] The overall economy of the hydrostatic loader is mainly affected by the engine, the hydraulic system matching and the overall vehicle. Due to the complex working condition requirements of the hydrostatic loader market, the high efficiency area of the hydraulic components is difficult to be truly and effectively utilized, so that the oil consumption of the hydrostatic loader is large. SUMMARY

[0005] The embodiments of the present application provide a hydrostatic loader oil consumption reduction control method, equipment and medium, which are used to solve the following technical problem: due to the complex working condition requirements of the hydrostatic loader market, the high efficiency area of the hydraulic components is difficult to be truly and effectively utilized, so that the oil consumption of the hydrostatic loader is large.

[0006] The embodiments of the present application adopt the following technical solutions:

[0007] The embodiments of the present application provide a hydrostatic loader oil consumption reduction control method. After the overall vehicle of the hydrostatic loader is ignited and started, the average value of the actual target speed of the engine and the average value of the pump end pressure of the hydraulic system in a preset time period are determined; the average value of the actual target speed of the engine and the average value of the pump end pressure of the hydraulic system are compared with the preset working condition threshold value respectively to determine the market working condition of the hydrostatic loader; the motor efficiency of the hydraulic system corresponding to the hydrostatic loader is obtained, and different motor flow distribution schemes are constructed based on the motor efficiency of the hydraulic system; the market working condition of the hydrostatic loader is matched with the different motor flow distribution schemes, and the oil consumption of the hydrostatic loader is controlled based on the matched scheme.

[0008] The embodiment of the application identifies the market working condition road spectrum based on the target rotating speed and the hydraulic system pressure average value, realizes the hydrostatic working condition identification, truly and timely reflects the driver's intention, and avoids the trouble of installing a large number of sensors. Secondly, the embodiment of the application formulates an efficient and reasonable motor flow distribution scheme based on the motor bench efficiency, and then switches the efficient hydraulic control strategy based on the target working condition, so that the motor works in the optimal efficient area and improves the economy of the loader.

[0009] In an implementation manner of the application, after the whole vehicle of the hydrostatic loader is ignited and started, the engine actual target rotating speed average value and the hydraulic system pump end pressure average value in a preset time period are determined, specifically including: after the whole vehicle of the hydrostatic loader is ignited and started, the first engine actual target rotating speed and the first hydraulic system pump end pressure absolute value are obtained in a continuous first time period, so as to determine the first engine actual target rotating speed average value and the first hydraulic system pump end pressure average value corresponding to the continuous first time period; and the second engine actual target rotating speed and the second hydraulic system pump end pressure absolute value are obtained in a continuous second time period, so as to determine the second engine actual target rotating speed average value and the second hydraulic system pump end pressure average value corresponding to the continuous second time period; wherein the continuous first time period contains the continuous second time period.

[0010] In an implementation manner of the application, the engine actual target rotating speed average value and the hydraulic system pump end pressure average value are compared with the preset working condition threshold value respectively, so as to determine the market working condition of the hydrostatic loader, specifically including: in the case that the first engine actual target rotating speed average value is not greater than the first rotating speed threshold value, and the first hydraulic system pump end pressure average value is not greater than the first pressure threshold value, it is determined that the hydrostatic loader is in the grinding work condition; in the case that the first engine actual target rotating speed average value is greater than the first rotating speed threshold value and not greater than the second rotating speed threshold value, and the first hydraulic system pump end pressure average value is greater than the first pressure threshold value and not greater than the second pressure threshold value, it is determined that the hydrostatic loader is in the constant efficiency working condition; in the case that the second engine actual target rotating speed average value is greater than the second rotating speed threshold value and not greater than the third rotating speed threshold value, and the second hydraulic system pump end pressure average value is greater than the second pressure threshold value and not greater than the third pressure threshold value, it is determined that the hydrostatic loader is in the maximum efficiency working condition.

[0011] In an implementation form of the present application, based on the hydraulic system motor efficiency, different motor flow distribution schemes are constructed, specifically including: based on the hydraulic system motor efficiency, under the condition that the whole vehicle hydraulic system pressure is determined to be not less than a preset pressure threshold and the motor speed is determined to be not less than a preset speed threshold, a first motor flow distribution scheme is constructed; wherein the first motor flow distribution scheme is that different motors synchronously perform displacement change adjustment; under the condition that the whole vehicle hydraulic system pressure is determined to be less than the preset pressure threshold and the motor speed is determined to be less than the preset speed threshold, a second motor flow distribution scheme is constructed; wherein the second motor flow distribution scheme is that the first motor is within a preset full displacement range, and the second motor is adjusted in displacement change based on the whole vehicle demand speed and demand traction.

[0012] In an implementation form of the present application, the market conditions of the hydrostatic loader are matched with different motor flow distribution schemes, specifically including: under the condition that the market conditions of the hydrostatic loader are in the constant efficiency condition, the first motor flow distribution scheme is matched; under the condition that the market conditions of the hydrostatic loader are in the grinding work condition, the second motor flow distribution scheme is matched.

[0013] In an implementation form of the present application, based on the matched scheme, the fuel consumption of the hydrostatic loader is controlled, specifically including: based on the pump end running data of the hydrostatic loader, the motor running data of the hydrostatic loader, the vehicle speed of the hydrostatic loader, the engine speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio, a motor displacement adjustment function group is constructed; under the condition of the first motor flow distribution scheme, based on the motor displacement adjustment function group, the motor running data is adjusted for multiple times to filter out the motor displacement data with the highest efficiency; under the condition of the second motor flow distribution scheme, based on the motor displacement adjustment function group, the first motor displacement is set within the preset full displacement range, and the second motor displacement is determined based on the whole vehicle demand speed and demand traction.

[0014] In an implementation form of the present application, based on the pump end running data of the hydrostatic loader, the motor running data of the hydrostatic loader, the vehicle speed of the hydrostatic loader, the engine speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio, a motor displacement adjustment function group is constructed, specifically including: based on the pump end running data of the hydrostatic loader and the motor running data of the hydrostatic loader, a first function is constructed:

[0015]

[0016] Based on the vehicle speed of the hydrostatic loader, the engine speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio, a second function is constructed:

[0017]

[0018] Based on the first function and the second function, a motor displacement adjustment function group is constructed; wherein, n p is the pump speed; v p is the pump displacement; η pv is the pump volumetric efficiency; η mv is the pump mechanical efficiency; n m1 is the first motor speed; v m1 is the first motor displacement; η m1 is the first motor mechanical efficiency; n m2 is the second motor speed; v m2 is the second motor displacement; η m2 is the second motor mechanical efficiency; v is the static hydraulic loader vehicle speed; n is the engine speed, r is the tire radius, is the transmission speed ratio; is the rear axle speed ratio.

[0019] In an implementation manner of the present application, after the oil consumption of the static hydraulic loader is controlled based on the matched scheme, the method further comprises: in the case that the market working condition of the static hydraulic loader triggers the maximum efficiency working condition, exiting the current static hydraulic loader oil consumption reduction control and switching to a default state control strategy.

[0020] The embodiment of the present application provides a static hydraulic loader oil consumption reduction control device, which comprises: at least one processor; and a memory in communication connection with the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to: after the static hydraulic loader is started by ignition, determine an average of an actual target engine speed and an average of a hydraulic system pump end pressure in a preset time period; compare the average of the actual target engine speed and the average of the hydraulic system pump end pressure with preset working condition thresholds respectively to determine a market working condition of the static hydraulic loader; acquire a hydraulic system motor efficiency corresponding to the static hydraulic loader, construct different motor flow distribution schemes based on the hydraulic system motor efficiency, and match the market working condition of the static hydraulic loader with the different motor flow distribution schemes to control oil consumption of the static hydraulic loader based on the matched scheme.

[0021] The nonvolatile computer storage medium provided by the embodiment of the application stores computer executable instructions, and the computer executable instructions are configured to: after the whole vehicle of the hydrostatic loader is ignited and started, determine the average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system in a preset time period; compare the average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system with preset working condition thresholds respectively, to determine the market working condition of the hydrostatic loader; obtain the hydraulic system motor efficiency corresponding to the hydrostatic loader, and based on the hydraulic system motor efficiency, construct different motor flow distribution schemes; and match the market working condition of the hydrostatic loader with the different motor flow distribution schemes, to control the fuel consumption of the hydrostatic loader based on the matched schemes.

[0022] The above at least one technical solution adopted by the embodiment of the application can achieve the following beneficial effects: the embodiment of the application identifies the market working condition road spectrum based on the target speed and the average of the hydraulic system pressure, realizes hydrostatic working condition identification, truly and timely reflects the intention of the driver, and avoids the trouble of installing a large number of sensors. Secondly, the embodiment of the application formulates an efficient and reasonable motor flow distribution scheme based on the motor bench efficiency, and then switches an efficient hydraulic control strategy based on the target working condition, so that the motor works in the optimal efficient zone, and the economy of the loader is improved. BRIEF DESCRIPTION OF DRAWINGS

[0023] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed to be used in the embodiment or prior art description will be briefly introduced as follows. Obviously, the drawings in the following description are only some embodiments described in the present application, and other drawings can also be obtained according to these drawings without creative labor. In the drawings:

[0024] Figure 1 A hydrostatic loader fuel consumption reduction control method flow chart is provided for the embodiment of the present application;

[0025] Figure 2 A first motor flow distribution scheme schematic diagram is provided for the embodiment of the present application;

[0026] Figure 3 A second motor flow distribution scheme schematic diagram is provided for the embodiment of the present application;

[0027] Figure 4 A first motor flow distribution scheme corresponding motor end efficiency comparison schematic diagram is provided for the embodiment of the present application;

[0028] Figure 5 A second motor flow distribution scheme corresponding motor end efficiency comparison schematic diagram is provided for the embodiment of the present application;

[0029] Figure 6 A schematic diagram of a static hydraulic loader oil consumption control structure is provided for an embodiment of the present application.

[0030] Figure 7 A schematic diagram of a static hydraulic loader oil consumption control device structure is provided for an embodiment of the present application. DETAILED DESCRIPTION

[0031] The present application provides a static hydraulic loader oil consumption control method, device and medium.

[0032] In order to enable those skilled in the art to better understand the technical solutions in the present application, the technical solutions in the embodiments of the present application will be described clearly and completely in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, not all. Based on the embodiments of the present application, all other embodiments obtained by those skilled in the art without creative labor should be within the scope of protection of the present application.

[0033] The technical solutions provided by the embodiments of the present application will be described in detail below with reference to the drawings.

[0034] Figure 1 A static hydraulic loader oil consumption control method flow chart is provided for an embodiment of the present application, as shown in Figure 1 The static hydraulic loader oil consumption control method includes the following steps:

[0035] S101, after the static hydraulic loader is started by ignition, the average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system in the preset time period are determined.

[0036] In an embodiment of the present application, after the static hydraulic loader is started by ignition, in a continuous first time period, the absolute value of the first engine actual target speed and the first hydraulic system pump end pressure are obtained to determine the first engine actual target speed average and the first hydraulic system pump end pressure average corresponding to the continuous first time period. And in a continuous second time period, the absolute value of the second engine actual target speed and the second hydraulic system pump end pressure are obtained to determine the second engine actual target speed average and the second hydraulic system pump end pressure average corresponding to the continuous second time period. Wherein, the continuous first time period contains the continuous second time period.

[0037] Specifically, after the static hydraulic loader is started by ignition, the absolute value of the engine actual target speed and the hydraulic system pump end pressure in the continuous first time period, such as the continuous A second time, is counted. Based on the counted data and the length of the A second time period, the first engine actual target speed average n0 in the A second time period is determined, and the hydraulic system pump end pressure average P0 is determined. △ P0.

[0038] Further, the engine actual target speed and the absolute value of the pump end pressure of the hydraulic system in a continuous second time period, such as a continuous B-second time period, are counted, and based on the counted data and the length of the B-second time period, a second engine actual target speed average n0 in the continuous B-second time period is determined, and a hydraulic system pump end pressure average ΔP0 is determined.

[0039] In the embodiment of the application, the continuous first time period includes the continuous second time period, A seconds can be 60s, and B seconds can be 10s. In application, they can also be changed according to actual needs, and the embodiment of the application does not limit this.

[0040] It should be noted that the static hydraulic loader is a loader that uses hydraulic driving for both the working system and the running system. The running system is mainly composed of pumps and motors, and the forward movement, backward movement and speed regulation during running of the loader are realized by controlling the pressure, flow and direction of hydraulic oil (the number of pumps and motors is different for different overall tonnages and requirements).

[0041] S102, the engine actual target speed average and the hydraulic system pump end pressure average are compared with the preset working condition threshold values respectively to determine the market working condition of the static hydraulic loader.

[0042] In one embodiment of the application, in the case that the first engine actual target speed average is not greater than the first speed threshold value and the first hydraulic system pump end pressure average is not greater than the first pressure threshold value, it is determined that the static hydraulic loader is in the grinding work condition. In the case that the first engine actual target speed average is greater than the first speed threshold value and not greater than the second speed threshold value, and the first hydraulic system pump end pressure average is greater than the first pressure threshold value and not greater than the second pressure threshold value, it is determined that the static hydraulic loader is in the constant efficiency working condition. In the case that the second engine actual target speed average is greater than the second speed threshold value and not greater than the third speed threshold value, and the second hydraulic system pump end pressure average is greater than the second pressure threshold value and not greater than the third pressure threshold value, it is determined that the static hydraulic loader is in the maximum efficiency working condition.

[0043] Specifically, the relationship between the engine actual target speed, the hydraulic system pump end pressure average and the threshold value is judged. The working conditions of the static hydraulic loader are divided into the grinding work condition, the constant efficiency working condition and the maximum efficiency working condition in the embodiment of the application, and the threshold values triggering these working conditions are determined respectively.

[0044] Further, the first engine actual target speed average and the first hydraulic system pump end pressure average in a continuous A-second time period are counted as conditions for identifying the grinding work condition and the constant efficiency working condition. The second engine actual target speed average and the second hydraulic system pump end pressure average in a continuous B-second time period are counted as conditions for identifying the maximum efficiency working condition.

[0045] Table 1 is a different working condition threshold table:

[0046] Table 1

[0047]

[0048] As shown in Table 1, first, the actual target speed, system pressure and threshold size are judged, when n0≤n1 and △P0≤△P1, it is identified that the vehicle is in the grinding work condition; when n1

[0049] Table 2

[0050] Operating condition Threshold value Cheating operating condition [n0 < n1 and ΔP0 < ΔP1] Fixed efficiency operating condition [n1 < n0 < n2 and ΔP1 < ΔP0 < ΔP2] Maximum efficiency operating condition [n2 < n0 < n3 or ΔP2 < ΔP0 < ΔP3]

[0051] S103, the hydraulic system motor efficiency corresponding to the static hydraulic loader is acquired, and based on the hydraulic system motor efficiency, different motor flow distribution schemes are constructed.

[0052] In an embodiment of the present application, based on the hydraulic system motor efficiency, in the case where it is determined that the vehicle hydraulic system pressure is not less than the preset pressure threshold value and the motor speed is not less than the preset speed threshold value, a first motor flow distribution scheme is constructed. Wherein, the first motor flow distribution scheme is that different motors synchronously change the displacement adjustment, in the case where it is determined that the vehicle hydraulic system pressure is less than the preset pressure threshold value and the motor speed is less than the preset speed threshold value, a second motor flow distribution scheme is constructed. Wherein, the second motor flow distribution scheme is that the first motor is in the preset full displacement range, and the second motor is adjusted in displacement based on the vehicle demand speed and demand traction.

[0053] Specifically, the motor flow distribution scheme in the embodiment of the present application is mainly divided into two kinds, Figure 2 The first motor flow distribution scheme provided by the embodiment of the present application is shown in the figure, two motors synchronously change the displacement adjustment to meet the vehicle speed and traction demand. Figure 3 The second motor flow distribution scheme provided by the embodiment of the present application is shown in the figure, one motor is preferentially ensured to be close to full displacement (high efficiency), and the other motor is adjusted in displacement based on the vehicle demand speed and demand traction.

[0054] Further, the rationality of the two motor flow distribution schemes is determined by the motor efficiency map on the test bench, the actual vehicle speed, and the hydraulic system pressure demand of the whole vehicle. For example, the motor efficiency map measured on the test bench shows that: in state 1, when the pressure is low and the motor speed is low, for example, when the hydraulic system pressure of the whole vehicle is less than the preset pressure threshold and the motor speed is less than the preset speed threshold, the total efficiency of motor 1 is much higher than that of motor 2 when the displacement is large. In state 2, when the pressure is high and the motor speed is high, for example, when the hydraulic system pressure of the whole vehicle is not less than the preset pressure threshold and the motor speed is not less than the preset speed threshold, the efficiency of motor 1 and motor 2 is low when the displacement is large. Therefore, state 1 adopts the second motor flow distribution scheme, and state 2 adopts the first motor flow distribution scheme.

[0055] wherein the motor efficiency map is a motor efficiency change diagram measured on a test bench under the control of the hydraulic motor element displacement, speed, and pressure.

[0056] S104, match the market working conditions of the hydrostatic loader with different motor flow distribution schemes to control the fuel consumption of the hydrostatic loader based on the matched schemes.

[0057] In an embodiment of the present application, when the market working conditions of the hydrostatic loader are in the constant efficiency working condition, the first motor flow distribution scheme is matched. When the market working conditions of the hydrostatic loader are in the grinding working condition, the second motor flow distribution scheme is matched.

[0058] Specifically, when the hydrostatic loader identifies the target working condition (grinding working condition, constant efficiency working condition), a reasonable hydraulic motor flow distribution strategy is selected. For example, when the target working condition is identified as the grinding working condition, the second hydraulic control strategy is selected, and the whole vehicle hydraulic walking system controller is executed; when the target working condition is identified as the constant efficiency working condition, the first hydraulic control strategy is selected.

[0059] In an embodiment of the present application, a motor displacement adjustment function group is constructed according to the pump end operation data of the hydrostatic loader, the motor operation data of the hydrostatic loader, the vehicle speed of the hydrostatic loader, the engine speed, the tire radius, the gearbox speed ratio, and the rear axle speed ratio. In the case of the first motor flow distribution scheme, the motor operation data is adjusted multiple times based on the motor displacement adjustment function group to filter out the motor displacement data with the highest efficiency. In the case of the second motor flow distribution scheme, the first motor displacement is set within the preset full displacement range, and the second motor displacement is determined based on the demand vehicle speed and the demand traction of the whole vehicle based on the motor displacement adjustment function group.

[0060] Specifically, based on the static hydraulic loader pump end operation data and the static hydraulic loader motor operation data, a first function is constructed:

[0061]

[0062] Based on the static hydraulic loader vehicle speed, the engine speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio, a second function is constructed:

[0063]

[0064] Based on the first function and the second function, a motor displacement adjustment function group is constructed. Because the pump speed and the engine speed are equal or have a certain speed ratio relationship, the two functions are combined. Wherein, n p is the pump speed; v p is the pump displacement; η pv is the pump volumetric efficiency; η mv is the pump mechanical efficiency; n m1 is the first motor speed; v m1 is the first motor displacement; η m1 is the first motor mechanical efficiency; n m2 is the second motor speed; v m2 is the second motor displacement; η m2 is the second motor mechanical efficiency; v is the static hydraulic loader vehicle speed; n is the engine speed, r is the tire radius, is the gearbox speed ratio; is the rear axle speed ratio.

[0065] Further, in the case of the first motor flow distribution scheme, according to the motor displacement adjustment function group, the motor displacement is adjusted multiple times to screen out the motor displacement data with the highest efficiency. In the case of the second motor flow distribution scheme, one motor is preferentially ensured to be close to full displacement (high efficiency), and the other motor is adjusted in displacement based on the vehicle demand speed and the demand traction.

[0066] Figure 4 The first motor flow distribution scheme provided by the embodiment of the application corresponds to a motor end efficiency comparison schematic diagram, which can be seen that in the first motor flow distribution scheme, the displacements of different motors are adjusted synchronously, and the efficiencies of the first motor and the second motor are similar. Figure 5 The second motor flow distribution scheme provided by the embodiment of the application corresponds to a motor end efficiency comparison schematic diagram, which can be seen that in the second motor flow distribution scheme, the first motor is in a preset full displacement range, and the second motor is adjusted in displacement, the first motor has a higher efficiency, and the second motor is in a high efficiency stage as much as possible under control.

[0067] In an embodiment of the present application, in the case that the market working condition of the hydrostatic loader triggers the maximum efficiency working condition, the current hydrostatic loader fuel consumption control is exited, and the default state control strategy is switched.

[0068] Specifically, if the maximum efficiency working condition is triggered, the hydraulic system exits the current hydraulic strategy, and switches to the original vehicle default state control strategy, to ensure that the vehicle power meets the demand.

[0069] The embodiment of the present application identifies the market working condition based on the target speed and the hydraulic system pressure average, realizes the hydrostatic working condition identification, formulates a high-efficiency and reasonable motor flow distribution scheme based on the motor bench efficiency, and then switches the efficient hydraulic control strategy based on the target working condition, so that the motor works in the optimal high-efficiency zone, and improves the economy of the loader.

[0070] Figure 6 A hydraulic loader fuel consumption control structure schematic diagram provided by the embodiment of the present application is shown in Figure 6 First, the hydrostatic loader is in the default hydraulic strategy, and second, the hydrostatic loader market working condition is identified based on the engine target speed and the hydraulic system pump end pressure. The embodiment of the present application divides the hydrostatic loader working condition into the grinding working condition, the constant efficiency working condition and the maximum efficiency working condition. A reasonable motor flow distribution scheme is formulated based on the hydraulic system motor efficiency. When the hydrostatic loader identifies the target working condition (grinding working condition, constant efficiency working condition), a reasonable motor flow distribution scheme is selected. If the maximum efficiency working condition is triggered, the hydraulic system exits the current hydraulic strategy, and switches to the original vehicle default state control strategy.

[0071] Figure 7 A hydraulic loader fuel consumption control device structure schematic diagram provided by the embodiment of the present application is shown in Figure 7 The hydrostatic loader fuel consumption control device includes at least one processor and a memory in communication connection with the at least one processor. The memory stores instructions executable by the at least one processor. The instructions are executed by the at least one processor to enable the at least one processor to determine the engine actual target speed average and the hydraulic system pump end pressure average within a preset time period after the hydrostatic loader vehicle ignition starts, compare the engine actual target speed average and the hydraulic system pump end pressure average with the preset working condition threshold value respectively to determine the market working condition of the hydrostatic loader, obtain the hydraulic system motor efficiency corresponding to the hydrostatic loader, construct different motor flow distribution schemes based on the hydraulic system motor efficiency, match the market working condition of the hydrostatic loader with the different motor flow distribution schemes, and control the fuel consumption of the hydrostatic loader based on the matched scheme.

[0072] The embodiment of the application further provides a nonvolatile computer storage medium, which stores computer executable instructions, and the computer executable instructions are configured to: determine the average of the actual target engine speed and the average of the pump end pressure of the hydraulic system in a preset time period after the whole vehicle of the hydrostatic loader is started by ignition; compare the average of the actual target engine speed and the average of the pump end pressure of the hydraulic system with preset working condition thresholds respectively to determine the market working condition of the hydrostatic loader; acquire the motor efficiency of the hydraulic system corresponding to the hydrostatic loader, construct different motor flow distribution schemes based on the motor efficiency of the hydraulic system; and match the market working condition of the hydrostatic loader with the different motor flow distribution schemes to control the fuel consumption of the hydrostatic loader based on the matched schemes.

[0073] The embodiments in the application are described in a progressive manner, and the same or similar parts of each embodiment can be referred to each other, and each embodiment mainly describes the difference from other embodiments. Especially, the device, equipment and nonvolatile computer storage medium embodiments are basically similar to the method embodiments, so the description is relatively simple, and the related parts can be referred to the part of the method embodiment.

[0074] The above only describes the embodiments of the application and is not used to limit the application. The embodiments of the application can be variously changed and modified by those skilled in the art. The modification or replacement does not make the corresponding technical solution deviate from the spirit and scope of the technical solution of the embodiments of the application.

Claims

1. A method of hydrostatic loader fuel consumption reduction control, characterized by, The method comprises: After the static hydraulic loader is started, the average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system in a preset time period are determined; The average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system are compared with preset working condition thresholds respectively to determine the market working condition of the static hydraulic loader; The motor efficiency of the hydraulic system corresponding to the static hydraulic loader is obtained, and different motor flow distribution schemes are constructed based on the motor efficiency of the hydraulic system; The market working condition of the static hydraulic loader is matched with the different motor flow distribution schemes to control the fuel consumption of the static hydraulic loader based on the matched schemes; After the static hydraulic loader is started, the average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system in a preset time period are determined, specifically comprising: After the static hydraulic loader is started, the absolute values of the first actual target speed of the engine and the first pump end pressure of the hydraulic system are obtained in a continuous first time period to determine the average of the first actual target speed of the engine and the average of the first pump end pressure of the hydraulic system corresponding to the continuous first time period; and The absolute values of the second actual target speed of the engine and the second pump end pressure of the hydraulic system are obtained in a continuous second time period to determine the average of the second actual target speed of the engine and the average of the second pump end pressure of the hydraulic system corresponding to the continuous second time period; The continuous first time period contains the continuous second time period; The average of the actual target speed of the engine and the average of the pump end pressure of the hydraulic system are compared with preset working condition thresholds respectively to determine the market working condition of the static hydraulic loader, specifically comprising: In the case that the average of the first actual target speed of the engine is not greater than a first speed threshold and the average of the first pump end pressure of the hydraulic system is not greater than a first pressure threshold, it is determined that the static hydraulic loader is in a grinding working condition; In the case that the average of the first actual target speed of the engine is greater than the first speed threshold and not greater than a second speed threshold, and the average of the first pump end pressure of the hydraulic system is greater than the first pressure threshold and not greater than a second pressure threshold, it is determined that the static hydraulic loader is in a constant efficiency working condition; In the case that the average of the second actual target speed of the engine is greater than the second speed threshold and not greater than a third speed threshold, and the average of the second pump end pressure of the hydraulic system is greater than the second pressure threshold and not greater than a third pressure threshold, it is determined that the static hydraulic loader is in a maximum efficiency working condition.

2. A method of reducing fuel consumption in a hydrostatic loader according to claim 1, characterized in that, Based on the motor efficiency of the hydraulic system, a first motor flow distribution scheme is constructed in the case that the hydraulic system pressure of the whole vehicle is not less than a preset pressure threshold and the motor speed is not less than a preset speed threshold; wherein the first motor flow distribution scheme is a synchronous displacement change adjustment of different motors. ​ In a case where it is determined that the whole vehicle hydraulic system pressure is less than the preset pressure threshold value and the motor rotation speed is less than the preset rotation speed threshold value, a second motor flow distribution scheme is constructed; wherein the second motor flow distribution scheme is that the first motor is in a preset full discharge range, and the second motor is adjusted in displacement based on the whole vehicle demand speed and demand traction.

3. A method of reducing fuel consumption in a hydrostatic loader according to claim 2, characterized in that, The matching of the market working condition of the hydrostatic loader with the different motor flow distribution schemes specifically includes: In a case where the market working condition of the hydrostatic loader is in a constant efficiency working condition, a first motor flow distribution scheme is matched; In a case where the market working condition of the hydrostatic loader is in a grinding working condition, a second motor flow distribution scheme is matched.

4. A method of reducing fuel consumption in a hydrostatic loader according to claim 3, characterized in that, The control of the oil consumption of the hydrostatic loader based on the matched scheme specifically includes: A motor displacement adjustment function group is constructed based on the hydrostatic loader pump end running data, the hydrostatic loader motor running data, the hydrostatic loader speed, the engine rotation speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio; In a case where the first motor flow distribution scheme is implemented, the motor running data is adjusted multiple times based on the motor displacement adjustment function group to filter out the motor displacement data with the highest efficiency; In a case where the second motor flow distribution scheme is implemented, the first motor displacement is set in the preset full discharge range, and the second motor displacement is determined based on the whole vehicle demand speed and demand traction.

5. A method of reducing fuel consumption in a hydrostatic loader according to claim 4, characterized in that, The construction of the motor displacement adjustment function group based on the hydrostatic loader pump end running data, the hydrostatic loader motor running data, the hydrostatic loader speed, the engine rotation speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio specifically includes: A first function is constructed based on the hydrostatic loader pump end running data and the hydrostatic loader motor running data: ； A second function is constructed based on the hydrostatic loader speed, the engine rotation speed, the tire radius, the gearbox speed ratio and the rear axle speed ratio: ； The motor displacement adjustment function group is constructed based on the first function and the second function; wherein, is the pump rotational speed; is the pump displacement; is the pump volumetric efficiency; is the pump mechanical efficiency; is the first motor rotational speed; is the first motor displacement; is the first motor mechanical efficiency; is the second motor rotational speed; is the second motor displacement; is the second motor mechanical efficiency; is the hydrostatic loader vehicle speed; is the engine rotational speed, is the tire radius, is the transmission speed ratio; is the rear axle speed ratio.

6. The method of hydraulic efficiency control of a hydrostatic loader according to claim 1, characterized in that, After the control of the oil consumption of the hydrostatic loader based on the matched scheme, the method further includes: In a case where the market working condition of the hydrostatic loader triggers a maximum efficiency working condition, the current hydrostatic loader oil consumption control is exited, and a default state control strategy is switched.

7. A hydrostatic loader fuel consumption reduction control apparatus characterized by, The device includes: at least one processor; and a memory connected with the at least one processor in communication; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to: After the whole vehicle of the hydrostatic loader is started, the average of the actual target rotation speed of the engine and the average of the pump end pressure of the hydraulic system in a preset time period are determined; The average of the actual target rotation speed of the engine and the average of the pump end pressure of the hydraulic system are compared with a preset working condition threshold value respectively to determine the market working condition of the hydrostatic loader; The hydraulic system motor efficiency corresponding to the hydrostatic loader is obtained, and different motor flow distribution schemes are constructed based on the hydraulic system motor efficiency; In a case where the first motor flow distribution scheme is implemented, the motor running data is adjusted multiple times based on the motor displacement adjustment function group to filter out the motor displacement data with the highest efficiency; The market working condition of the hydrostatic loader is matched with the different motor flow distribution schemes, so as to control the fuel consumption of the hydrostatic loader based on the matched scheme; The average engine actual target speed and the average hydraulic system pump end pressure in a preset time period after the whole vehicle of the hydrostatic loader is started are determined, specifically including: After the whole vehicle of the hydrostatic loader is started, the first engine actual target speed and the first hydraulic system pump end pressure absolute value in a continuous first time period are obtained, so as to determine the first engine actual target speed average and the first hydraulic system pump end pressure average corresponding to the continuous first time period; and The second engine actual target speed and the second hydraulic system pump end pressure absolute value in a continuous second time period are obtained, so as to determine the second engine actual target speed average and the second hydraulic system pump end pressure average corresponding to the continuous second time period; The continuous first time period contains the continuous second time period; The average engine actual target speed and the average hydraulic system pump end pressure are compared with preset working condition thresholds respectively, so as to determine the market working condition of the hydrostatic loader, specifically including: In the case that the first engine actual target speed average is not greater than a first speed threshold and the first hydraulic system pump end pressure average is not greater than a first pressure threshold, it is determined that the hydrostatic loader is in a grinding working condition; In the case that the first engine actual target speed average is greater than the first speed threshold and not greater than a second speed threshold, and the first hydraulic system pump end pressure average is greater than the first pressure threshold and not greater than a second pressure threshold, it is determined that the hydrostatic loader is in a constant efficiency working condition; In the case that the second engine actual target speed average is greater than the second speed threshold and not greater than a third speed threshold, and the second hydraulic system pump end pressure average is greater than the second pressure threshold and not greater than a third pressure threshold, it is determined that the hydrostatic loader is in a maximum efficiency working condition.

8. A non-transitory computer storage medium storing computer-executable instructions that, when executed, cause a computer to: The computer executable instructions are set as: ​ After the whole vehicle of the hydrostatic loader is started, the average engine actual target speed and the average hydraulic system pump end pressure in a preset time period are determined; The average engine actual target speed and the average hydraulic system pump end pressure are compared with preset working condition thresholds respectively, so as to determine the market working condition of the hydrostatic loader; The hydraulic system motor efficiency corresponding to the hydrostatic loader is obtained, and different motor flow distribution schemes are constructed based on the hydraulic system motor efficiency; The market working condition of the hydrostatic loader is matched with the different motor flow distribution schemes, so as to control the fuel consumption of the hydrostatic loader based on the matched scheme; The average engine actual target speed and the average hydraulic system pump end pressure in a preset time period after the whole vehicle of the hydrostatic loader is started are determined, specifically including: The first engine actual target speed and the first hydraulic system pump end pressure absolute value are obtained in a continuous first time period after the whole vehicle of the hydrostatic loader is ignited and started, so as to determine the first engine actual target speed average value and the first hydraulic system pump end pressure average value corresponding to the continuous first time period; and The second engine actual target speed and the second hydraulic system pump end pressure absolute value are obtained in a continuous second time period, so as to determine the second engine actual target speed average value and the second hydraulic system pump end pressure average value corresponding to the continuous second time period. The continuous first time period contains the continuous second time period. The engine actual target speed average value and the hydraulic system pump end pressure average value are compared with preset working condition thresholds respectively, so as to determine the market working condition of the hydrostatic loader, and specifically comprising: In the case that the first engine actual target speed average value is not greater than a first speed threshold and the first hydraulic system pump end pressure average value is not greater than a first pressure threshold, it is determined that the hydrostatic loader is in a grinding work condition; In the case that the first engine actual target speed average value is greater than the first speed threshold and not greater than a second speed threshold, and the first hydraulic system pump end pressure average value is greater than the first pressure threshold and not greater than a second pressure threshold, it is determined that the hydrostatic loader is in a constant efficiency working condition; In the case that the second engine actual target speed average value is greater than the second speed threshold and not greater than a third speed threshold, and the second hydraulic system pump end pressure average value is greater than the second pressure threshold and not greater than a third pressure threshold, it is determined that the hydrostatic loader is in a maximum efficiency working condition.

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