Double-end fuel centrifugal pump system power optimization method based on flow matching

Abstract

The invention relates to an aero-engine fuel centrifugal pump, in particular to a power optimization method for a double-end fuel centrifugal pump, and aims to optimize power consumption of the double-end fuel centrifugal pump according to actual demand matching flow, so that efficient fuel conveying is realized, and energy waste is reduced. According to the technical scheme, the method comprises the following steps: (1) establishing a flow-lift polynomial fitting equation of each parallel pump unit; (2) calculating the maximum allowable flow of each parallel pump unit of the fuel centrifugal pump; (3) introducing a quantitative evaluation model Si, and selecting an optimal pump as a high-flow working unit; (4) determining a safety threshold value of the low-flow working unit; (5) designing at least five groups of flow distribution schemes of the fuel centrifugal pump system under different flow distribution ratios; (6) carrying out numerical simulation to obtain the power of the whole pump system of different flow distribution schemes; and (7) taking the flow corresponding to the minimum value point of the power of the Qa-Pt curve graph as a flow distribution value Qa of the high-flow working unit, and obtaining a distribution scheme of the flow corresponding to the minimum power.

Description

Technical Field

[0001] The present invention relates to a fuel centrifugal pump for an aeroengine, particularly to a method for optimizing the power of a double-end fuel centrifugal pump. Background Art

[0002] As a key component in modern fuel systems, the double-end fuel centrifugal pump is widely used in fields such as aerospace and automotive engines, and its performance directly affects the efficiency, reliability, and stability of the entire fuel system. The main function of the double-end fuel centrifugal pump is to provide sufficient pressure and flow rate for the fuel system to meet the fuel requirements of the engine under various operating conditions.

[0003] However, in actual operation, due to the large variations in the requirements for flow rate and pressure under different operating conditions, how to achieve a reasonable matching of the flow rates at the two inlet ends has become a key issue. On the one hand, if good flow rate matching cannot be achieved between the pump units, it may lead to power waste, a decrease in system efficiency, and even equipment damage; on the other hand, unreasonable operating conditions may also cause adverse phenomena such as high temperature, high pressure, or cavitation, thus affecting the safety and lifespan of the entire system.

[0004] Currently, there are still certain deficiencies in the power optimization of double-end fuel centrifugal pumps. Traditional methods usually adopt fixed speeds or simple adjustment strategies, making it difficult to balance flow rate matching and power optimization under multiple operating conditions. While some existing methods based on model prediction or control algorithms can improve the system performance to a certain extent, they are highly complex and lack real-time performance. Existing research is still insufficient in coordinating the collaborative work between different pump units and optimizing the overall power distribution. Therefore, there is an urgent need to propose a method for optimizing the power system of a double-end fuel centrifugal pump based on flow rate matching. Summary of the Invention

[0005] The objective of the present invention is to overcome the deficiencies in the above background art and provide a method for optimizing the power of a double-end fuel centrifugal pump based on flow rate matching, so as to optimize the power consumption of the double-end fuel centrifugal pump by matching the flow rate according to actual requirements, thereby achieving efficient fuel delivery and reducing energy waste.

[0006] To achieve the above objective, the technical solution provided by the present invention is as follows:

[0007] A method for optimizing the power of a double-end fuel centrifugal pump based on flow rate matching, comprising the following steps:

[0008] 1. Through hydraulic performance experiments of the fuel centrifugal pump, obtain the test sample data of the flow rate Q and head H of each pump unit respectively, and establish the flow rate-head polynomial fitting equations for each parallel pump unit;

[0009] Furthermore, the flow rate-head polynomial fitting equation is:

[0010]

[0011] 2. Calculate the maximum allowable flow rate \(Q\) of each parallel pump unit of the fuel centrifugal pump according to the operating condition design parameters of the double-end fuel centrifugal pump system and the pipeline resistance characteristics i,max ;

[0012] Furthermore, the calculation steps for the maximum allowable flow rate \(Q\) of each parallel pump unit of the fuel centrifugal pump are as follows: i,max :

[0013] 21) In the actual pipeline system, the head loss includes not only the frictional loss \(\Delta H\) along the path f , but also the local resistance loss \(\Delta H\) at the elbow j . Therefore, the total head loss can be expressed by Equation (3):

[0014] \(\Delta H=\Delta H\) f +\(\Delta H\) j (3)

[0015] 22) The frictional loss of the pipeline in the pump system can be expressed by the Darcy-Weisbach equation as:

[0016]

[0017] where \(f\) is the friction factor; \(L\) is the length of the pipeline; \(D\) is the hydraulic diameter of the pipeline; is the average velocity of the fluid; \(g\) is the acceleration due to gravity.

[0018] 23) The average velocity of the fluid in the pipeline can be obtained from the flow rate and hydraulic radius in the pipeline:

[0019]

[0020] where \(Q\) is the flow rate of the pipeline.

[0021] 24) Substitute Equation (5) into Equation (4), then the frictional head loss along the path can be derived as:

[0022]

[0023] 25) The local resistance loss at the elbow is expressed as shown in Equation (7):

[0024]

[0025] In the formula, \(D\) i is the radius of the elbow pipeline; \(R\) i is the radius of the center of the elbow; \(\theta\) i is the central angle corresponding to the bent part of the elbow, representing the bending degree of the elbow.

[0026] 26) Substituting equations (6) and (7) into equation (3), the expression for the total head loss of the pipeline can be obtained as shown in equation (8):

[0027]

[0028] Where: s is the resistance coefficient.

[0029] 27) Substituting equation (8) into equation (2), equation (9) can be obtained:

[0030]

[0031] Where: a i is the loss coefficient related to the square of the flow rate, b i is the loss coefficient related to the linear flow rate, c i is the shut-off head, i.e., the head at zero flow rate; s i is the resistance coefficient of the branch; s d is the resistance coefficient of the main path; Q d is the required flow rate at the low-pressure outlet.

[0032] 28) The calculation formula for the maximum allowable flow rate Q i,max of each parallel pump unit can be derived as follows:

[0033]

[0034] 3. Introduce the quantitative scoring model S i , and select the optimal pump as the high-flow working unit;

[0035] The quantitative evaluation model S i is as follows:

[0036]

[0037] Where, η i is the efficiency value of the pump at the best efficiency point, reflecting its theoretical maximum energy efficiency; s is the resistance coefficient; Q d is the required flow rate at the low-pressure outlet.

[0038] 4. Determine the safety threshold of the low-flow working unit according to the sample data of the hydraulic performance test;

[0039] The method for determining the safety threshold of the low-flow working unit is as follows:

[0040] 41) Determine the temperature rise in the low-flow working unit through equation (12):

[0041]

[0042] Where, C is the specific heat capacity of the medium, with the unit of KJ / (kg·℃).

[0043] 42) Substitute the data obtained from the hydraulic performance experiment into Equation (12) to calculate ΔT for the corresponding working conditions i , and screen out those that satisfy ΔT i <ΔT req and the specific working condition point with the value closest to ΔT req . The flow rate corresponding to this working condition point is established as the minimum flow rate Q at which the pump can maintain safe and stable operation without causing cavitation i,min . Among them, ΔT req is the allowable temperature rise of the pump

[0044] 43) Since the total flow rate of the pump at both ends of the inlet remains unchanged, the flow rate Q of the high-flow working unit can be obtained from the minimum flow rate of the low-flow working unit L0 and needs to satisfy Equation (13):

[0045] Q L0 ≤Q total -Q i,min (13)

[0046] where: Q total is the total flow rate output by the system, and Q h is the flow rate on the high-pressure outlet side

[0047] 44) By comparing the values of Q i,max and Q Lo , take the smaller value as the maximum supply flow rate Q L of the high-flow working unit

[0048] 5. Design at least five flow distribution schemes of the fuel centrifugal pump system under different flow distribution ratios

[0049] The design method of the at least five flow distribution schemes is: control the total inlet flow rate to be unchanged, evenly distribute the total inlet flow rate to the two inlet ends of the pump system, and start from 50% for the flow rate ratio at the high-flow working unit end, gradually increase the flow distribution, increase by 1% each time, and increase to the maximum supply flow rate Q L of the high-flow working unit

[0050] 6. Conduct numerical simulation according to the flow distribution scheme to obtain the power P of the entire pump system under different flow distribution schemes t ;

[0051] 7. Fit the power points of the entire pump system corresponding to different flow rates of the high-flow working unit to obtain the Q a -P t curve graph; take the flow rate corresponding to the minimum power point as the flow distribution value Q a; thus obtaining the flow distribution scheme corresponding to the minimum power.

[0052] The described Q a -P t The curve graph is obtained by taking the flow rate of the high-flow working unit as the abscissa and the power corresponding to the pump system as the ordinate.

[0053] Furthermore, the fluid calculation software used is FLUENT or CFX.

[0054] The beneficial effects of the present invention are as follows: The two-stage double-ended oil supply pump can adapt to the oil supply requirements under various working conditions and has high flexibility at the same time. The optimization method of the power system of the double-ended fuel centrifugal pump based on flow matching can not only optimize the power consumption of the double-ended fuel centrifugal pump by matching the flow rate according to actual needs, achieve efficient fuel delivery, improve system efficiency, but also effectively reduce energy consumption, providing a better solution for complex fuel supply systems. BRIEF DESCRIPTION OF THE DRAWINGS

[0055] Figure 1 is the working flow chart of the embodiment of the present invention.

[0056] Figure 2 is the two-dimensional structure schematic diagram of the embodiment scheme of the present invention.

[0057] Figure 3 is the Q in the calculation example of the present invention a -P t curve graph.

[0058] Figure 4 is the low-pressure outlet head value in the calculation example of the present invention. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0059] The principles and features of the present invention are described below in conjunction with the embodiments shown in the drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0060] Figure 2 The shown double-ended fuel centrifugal pump system (prior art) is composed of two pump units with different characteristic curves connected in parallel, which are respectively located at two inlet ends. After confluence, the fuel flows out from two outlets. A centrifugal pump is configured on the high-pressure outlet side to boost the fluid and provide fuel with a constant pressure and flow rate to the engine; while the other side is defined as the low-pressure outlet side. All three pump units are installed on the same shaft and operate at the same speed.

[0061] In a double-end fuel supply centrifugal pump system, due to the different performance curves of the pumps at both ends, the flow distribution will be uneven. Currently, no invention has considered the impact of the power of the pump system on the power of the entire pump from the perspective of flow distribution at both ends. Therefore, the present invention proposes a method for power distribution and optimization of a double-end fuel supply pump. First, by analyzing the characteristics of the pump system, the research route of the present invention is determined, and the specific content is as follows:

[0062] 1. Through the hydraulic performance experiment of the fuel centrifugal pump, obtain the test sample data of the flow rate Q, head H, and shaft power P of each pump unit, and establish the flow-head polynomial fitting equation of each parallel pump unit as shown in formula (1):

[0063]

[0064] Among them, a i is the loss coefficient related to the square of the flow rate, b i is the loss coefficient related to the linear flow rate, c i is the shut-off head, that is, the head at zero flow rate; H i is the head of the fitted pump; Q i is the flow rate of the fitted pump.

[0065] 2. Taking the middle confluence section as the node, the pressure balance equation of the double-pump parallel system is shown in formula (2):

[0066] H i -ΔH i =H d +ΔH d (2)

[0067] Among them, H i is the head of a single pump; ΔH i is the total head loss of the branch pipe; H d is the required head at the low-pressure outlet; ΔH d is the head loss of the pipeline on the low-pressure outlet side.

[0068] In an actual pipeline system, the head loss not only includes the frictional loss along the way ΔH f , but also includes the local resistance loss ΔH j at the elbow. Therefore, the total head loss can be expressed by formula (3):

[0069] ΔH=ΔH f +ΔH j (3)

[0070] The frictional loss of the pump system pipeline can be expressed by the Darcy-Weisbach equation as:

[0071]

[0072] Among them, f is the friction factor; L is the length of the pipeline; D is the hydraulic diameter of the pipeline; is the average velocity of the fluid; g is the acceleration due to gravity.

[0073] The average velocity of the fluid in the pipeline can be obtained from the flow rate and hydraulic radius in the pipeline:

[0074]

[0075] Among them, Q is the flow rate of the pipeline.

[0076] Substitute Equation (5) into Equation (4), then the head loss along the way can be deduced as:

[0077]

[0078] The local resistance loss at the elbow is expressed as shown in Equation (7):

[0079]

[0080] In the formula, D i is the radius of the elbow pipeline; R i is the radius of the center of the elbow pair; θ i is the central angle corresponding to the bent part of the elbow, which characterizes the bending degree of the elbow.

[0081] Therefore, substituting Equation (6) and Equation (7) into Equation (3), the expression of the total head loss of the pipeline can be obtained as shown in Equation (8):

[0082]

[0083] Among them: s is the resistance coefficient.

[0084] Substitute Equation (8) into Equation (2), and Equation (9) can be obtained:

[0085]

[0086] Among them: s i is the resistance coefficient of the branch; s d is the resistance coefficient of the main road; Q d is the required flow rate at the low-pressure outlet.

[0087] In the formula:

[0088] (1) The friction factor, the length of the pipeline, the hydraulic diameter of the pipeline and the acceleration due to gravity are all constants greater than 0;

[0089] (2) As the flow rate of the pump increases, the head of the pump will correspondingly decrease; therefore, as the flow rate of a certain branch increases, the value on the left side of the equal sign will decrease. The right side of the equal sign is the required value at the low-pressure outlet of the pump system. When the total flow rate remains unchanged, the minimum value H of the pump's low-pressure outlet is taken. d,min When it is, the maximum allowable flow rate that the pump on the branch can provide can be obtained.

[0090] It can be deduced that the maximum allowable flow rate Q that the pump on the branch can provide i,max Calculation formula:

[0091]

[0092] 3. However, for the pumps at both ends, it is also necessary to determine one end as the high-flow inlet. The selection of the high-flow working unit needs to consider:

[0093] (1) The pump with a high efficiency peak has better performance under ideal conditions;

[0094] (2) The pump with a slower decay of head with flow rate has stronger adaptability;

[0095] (3) The pump with a smaller total resistance in the branch is more suitable for undertaking high flow rates.

[0096] To achieve the above purpose, the present invention provides a quantitative evaluation model S for ensuring the selection of the optimal pump as the main flow rate bearing unit under complex working conditions i , and its scoring formula is as shown in Equation (11):

[0097]

[0098] Among them, η i is the efficiency value of the pump at the best efficiency point, reflecting its theoretical highest energy efficiency; s is the resistance coefficient; Q d is the flow rate required at the low-pressure outlet.

[0099] 4. Determine the safety threshold of the low-flow working unit;

[0100] After evaluation, the side with a high score is the high-flow working unit, and the end with a low score is the low-flow working unit. However, as the flow rate in the pump decreases, the temperature rise in the pump is higher, and the pump is more likely to cavitate. The temperature rise in the low-flow working unit can be determined by Equation (12):

[0101]

[0102] Among them, C is the specific heat capacity of the medium.

[0103] Substitute the data obtained from the hydraulic performance experiment into Equation (12) to calculate ΔT corresponding to the working condition i , and screen out those that satisfy ΔT i <ΔT reqand the specific operating condition point with the value closest to ΔT req The flow rate corresponding to this operating condition point is established as the minimum flow rate Q at which the pump can maintain safe and stable operation without cavitation i,min . Among them, ΔT req is the allowable temperature rise of the pump

[0104] Since the total flow rate of the inlet pump unit is constant, the flow rate Q of the high-flow working unit can be obtained from the minimum flow rate of the low-flow working unit L0 It needs to satisfy Equation (13):

[0105] Q L0 ≤Q total -Q i,min (13)

[0106] Among them: Q total is the total flow rate output by the system, and Q h is the flow rate on the high-pressure outlet side

[0107] By comparing the values of Q i,max and Q Lo , the smaller value is taken as the maximum supply flow rate Q of the high-flow working unit L .

[0108] 5. Design at least five flow rate distribution schemes; that is, keep the total inlet flow rate constant, evenly distribute the total system flow rate Q total to the two inlet ends, and let the proportion of the flow rate of the high-flow working unit start from 50% and gradually increase the flow rate distribution, increasing by 1% each time until the maximum supply flow rate Q L ;

[0109] 6. Conduct numerical simulation according to the described flow rate distribution scheme to obtain the power P of the entire pump system t ;

[0110] 7. Fit the power points of the entire pump system corresponding to different flow rates of the high-flow working unit to obtain the Q a -P t curve graph

[0111] Take the flow rate corresponding to the minimum power point as the flow rate distribution value Q of the high-flow working unit a ;

[0112] The flow rate Q of the high-flow working unit a corresponding to the power of the entire pump system of the system, that is, the optimal power P of the entire pump system of the system is obtained t,min , thus realizing the power optimization of the two-stage double-end fuel centrifugal pump

[0113] Example:

[0114] Table 1: Design Parameters of Fuel Centrifugal Pump Operating Conditions

[0115]

[0116] Table 2: Design Parameters of Fuel Centrifugal Pump System

[0117]

[0118] Step 1: Through the hydraulic performance experiment of the fuel centrifugal pump, obtain the test sample data of the flow rate Q, head H, and efficiency η of each pump at both ends of the branch. The efficiency value of Pump 1 at the best efficiency point is 72.5%, and the efficiency value of Pump 2 at the best efficiency point is 70.5%. Establish the flow rate-head polynomial fitting equations for the two fuel centrifugal pumps as shown in Formula (1):

[0119]

[0120] Step 2: According to the operating conditions design parameters of the double-end fuel centrifugal pump system and the pipeline resistance characteristics, calculate the maximum allowable flow rate Q of each parallel pump unit of the fuel centrifugal pump i,max ;

[0121] Among them, the resistance coefficient s1 of Branch 1 is:

[0122]

[0123] Through Equation (9), the calculation formula for the maximum allowable flow rate Q that the pump in the branch can provide can be derived i,max of the calculation formula

[0124]

[0125] Perform the calculation and discard the negative value and take the positive value to obtain:

[0126]

[0127] Step 3: Introduce the quantitative scoring model S i , select the optimal pump as the high-flow working unit;

[0128] Combined with the relationship between the pump characteristics, pipeline resistance loss, and system demand pressure, obtain its performance comprehensive scoring formula, as shown in Equation (7), the larger the S i value, the more suitable it is as the high-flow working unit:

[0129]

[0130] Through calculation, it can be obtained:

[0131]

[0132] Therefore, pump 1 is selected as the high-flow working unit, and pump 2 is the low-flow working unit.

[0133] Step 4: Determine the safety threshold of the low-flow working unit; that is, based on the sample data of the hydraulic performance test, calculate the minimum flow rate at which cavitation does not occur in the low-flow working unit, so as to determine the maximum supply flow rate of the high-flow working unit; the specific steps are as follows:

[0134] Through the hydraulic performance experiment, obtain the sample data of the flow rate Q and efficiency η of the low-flow working unit, as shown in Table 3:

[0135] Table 3 Sample data of the experiment

[0136]

[0137] Determine the temperature rise in the low-flow working unit through Equation (12):

[0138]

[0139] The temperature rise ΔT corresponding to the working conditions inside the pump can be obtained, as shown in Table 4:

[0140] Table 4 Temperature rise corresponding to the working conditions inside the pump

[0141]

[0142] It is found through investigation that the allowable temperature rise ΔT of the liquid hydrocarbon pump req is 1°C. Therefore, when the flow rate is 0.02 m 3 / s, ΔT2 < ΔT req and the value is closest to ΔT req , then the minimum flow rate Q 2,min at which the pump can maintain safe and stable operation is 0.02 m 3 / s.

[0143] Obtain the flow rate Q of the high-flow working unit from the minimum flow rate of the low-flow working unit L0 which needs to satisfy Equation (13):

[0144] Q L0 ≤Q total -Q 2,min = 0.08 - 0.02 = 0.06 (m 3 / s) (13)

[0145] By comparing the values of Q 1,max and Q Lo , take the smaller value as the maximum supply flow rate Q L of the high-flow working unit, which is 0.06 m 3 / s.

[0146] Step 5: Design at least five flow distribution schemes of the fuel centrifugal pump system under different flow distribution ratios; specifically, evenly distribute the total inlet flow to the two inlet ends of the pump system, and let the flow ratio of the high-flow working unit end start from 50%, gradually increase the flow distribution, increase by 1% each time, and increase to the maximum supply flow Q of the high-flow working unit L , to obtain the distribution schemes shown in Table 5:

[0147] Table 5 Distribution schemes calculated from flow distribution

[0148]

[0149]

[0150] Step 6: Conduct numerical simulation according to the described flow distribution scheme to obtain the power P of the entire pump system t , as shown in Table 6:

[0151] Table 6 Powers corresponding to different schemes

[0152]

[0153] Step 7: Fit the power points of the entire pump system corresponding to different flows of the high-flow working unit to obtain the Q Figure 3 shown a -P t curve graph;

[0154] Take the flow corresponding to the minimum power point as the flow distribution value Qa of the high-flow working unit;

[0155] When the flow Qa of the high-flow working unit is 0.052 m3 / s, the corresponding optimal system total pump power Pt,min is 17.46 kw (see Figure 3 ,), thus realizing the optimization of the power of the double-end fuel centrifugal pump system.

Claims

1. A power optimization method for a double - end fuel centrifugal pump system based on flow matching, characterized in that, The method includes the following steps: (1) Through the hydraulic performance experiment of the fuel centrifugal pump, obtain the flow rate Q and head H test sample data of each pump unit, and establish the flow-head polynomial fitting equation of each parallel pump unit; (2) According to the operating condition design parameters of the double-end fuel centrifugal pump system and the pipeline resistance characteristics, calculate the maximum allowable flow rate of each parallel pump unit of the fuel centrifugal pump; (3) Introduce the quantitative evaluation model S i , and select the optimal pump as the high-flow working unit; (4) Determine the safety threshold of the low-flow working unit; (5) Design at least five flow distribution schemes of the fuel centrifugal pump system under different flow distribution ratios; (6) Conduct numerical simulation according to the described flow distribution scheme, so as to obtain the power of the whole pump system under different flow distribution schemes; (7) Fit the power points of each integral pump system corresponding to different flow rates of the high-flow working unit to obtain Q a -P t curve graph, and take the flow rate corresponding to the minimum power point as the flow rate allocation value Q a ; thus obtaining the allocation scheme of the flow rate corresponding to the minimum power.

2. The power optimization method of the double-end fuel centrifugal pump system based on flow matching according to claim 1, characterized in that: The flow-head polynomial fitting equation of each parallel pump unit described in step (1) is: Among them, a i is the loss coefficient related to the square of the flow rate, b i is the loss coefficient linearly related to the flow rate, c i is the shut-off head, that is, the head at zero flow rate; H i is the head of the fitted pump; Q i is the flow rate of the fitted pump.

3. The power optimization method of the double-end fuel centrifugal pump system based on flow matching according to claim 2, characterized in that: The maximum allowable flow rate Q of each parallel pump unit of the fuel centrifugal pump described in step (2) i,max is calculated by the formula: where: a i , b i , c i are the coefficients after fitting, H d,ming is the minimum value of the low-pressure outlet of the pump, s i is the resistance coefficient of the branch; s d is the resistance coefficient of the main road; Q d is the required flow rate of the low-pressure outlet.

4. The power optimization method for the double-end fuel centrifugal pump system based on flow matching according to claim 3, characterized in that: The quantization evaluation model S described in step (3) i is as follows: Among them, η i is the efficiency value of the pump at the best efficiency point, reflecting its theoretical maximum energy efficiency; s is the resistance coefficient; Q d is the flow rate required at the low-pressure outlet.

5. The power optimization method of the double-end fuel centrifugal pump system based on flow matching according to claim 4, wherein: The method for determining the safety threshold of the low-flow working unit described in step (4) is: 41) Determine the temperature rise in the low-flow working unit through formula (12): where C is the specific heat capacity of the medium, with the unit of KJ / (kg·°C), g is the acceleration due to gravity, and η is the efficiency value of the pump; 42) Substitute the data obtained from the hydraulic performance experiment into Equation (12) to calculate ΔT corresponding to the working condition i , and filter out those that satisfy ΔT i <ΔT req and the value is closest to ΔT req of the specific working condition point. The flow rate corresponding to this working condition point is established as the minimum flow rate Q at which the pump can maintain safe and stable operation on the premise of ensuring no cavitation phenomenon i,min； where ΔT req is the allowable temperature rise of the pump; 43) Since the total flow rate of the two pumps at the inlet is constant, the flow rate Q of the high-flow working unit is obtained by finding the minimum flow rate through the low-flow working unit L0 It is necessary to satisfy Equation (13): Q L0 ≤Q total -Q i,min (13) Where: Q total is the total flow output by the system, and Q h is the flow rate on the high-pressure outlet side; 44) By comparing Q i,max with Q Lo values, take the smaller value as the maximum supply flow rate Q L of the high-flow working unit.

6. The power optimization method of the dual-end fuel centrifugal pump system based on flow matching according to claim 5, characterized in that, The design method of the at least five groups of flow distribution schemes described in step (5) is as follows: Keeping the total inlet flow unchanged, evenly distribute the total inlet flow to the two inlet ends of the pump system, and starting from 50%, gradually increase the flow distribution of the high-flow working unit end by 1% each time until the maximum supply flow Q of the high-flow working unit is reached. L 。 7. The power optimization method of the double-end fuel centrifugal pump system based on flow matching according to claim 6, characterized in that: Q as described in step (7) a -P t The curve graph is a curve graph obtained by taking the flow rate of the high-flow working unit as the abscissa and the corresponding power of the pump system as the ordinate.

8. The power optimization method of the dual-end fuel centrifugal pump system based on flow matching according to any one of claims 1-6, characterized in that: The fluid calculation software used is FLUENT or CFX.

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