A method and apparatus for determining residual axial forces of an engine turbine pump rotor system

Abstract

This invention discloses a method and apparatus for determining the residual axial force of an engine turbopump rotor system, relating to the field of engine turbopump technology, to solve the problem in the prior art that it is impossible to evaluate and predict the residual axial force of an engine turbopump during the design stage. The method includes: obtaining the structural parameters and target operating condition parameters of the target engine turbopump; performing one-dimensional simulation calculations on the target structure in the target engine turbopump based on the target structure and operating condition parameters to obtain the axial force of the target structure; determining the axial force of the balance cavity in the dual-clearance balancing system based on the initial axial clearance and the pressure within the balance cavity; and determining the residual axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance cavity in the dual-clearance balancing system. This achieves efficient and accurate evaluation and prediction of the residual axial force of the engine turbopump rotor system during the design stage.

Description

Technical Field

[0001] This invention relates to the field of engine turbopump technology, and in particular to a method and apparatus for determining the residual axial force of an engine turbopump rotor system. Background Technology

[0002] The axial force balancing problem in high-speed, high-pressure turbopumps is one of the key technologies for the research and development of high-performance liquid engine turbopumps. Modern liquid engine turbopumps employ various forms of axial force balancing devices, among which the dual-clearance balancing system, due to its high stiffness and strong adjustment capability, can be applied in high-speed, high-power liquid engine turbopumps. However, the presence of the dual clearances significantly increases the complexity of the flow field, generally requiring CFD simulation to calculate the residual axial force of the rotor system. However, CFD simulation requires substantial computational resources and a three-dimensional model. Since three-dimensional models are unavailable during the design phase of high-speed, high-pressure turbopumps, CFD methods cannot be used for turbopump axial force calculation and control, nor can the residual axial force of the turbopump be assessed and predicted, leading to increased design difficulty and reduced efficiency.

[0003] Therefore, there is an urgent need for a more advanced method for axial force assessment and prediction to address the problem that existing technologies cannot assess and predict the residual axial force of engine turbopumps during the design phase. Summary of the Invention

[0004] The purpose of this invention is to provide a method and apparatus for determining the residual axial force of an engine turbopump rotor system. This method is applicable to the calculation of the axial force of a dual-clearance balancing system of a high-speed, high-power liquid engine turbopump. It enables rapid and accurate assessment and prediction of the residual axial force of the engine turbopump rotor system during the design phase, and solves the problem that the existing technology cannot assess and predict the residual axial force of the engine turbopump during the design phase.

[0005] To achieve the above objectives, the present invention provides the following technical solution: In a first aspect, the present invention provides a method for determining the residual axial force of an engine turbopump rotor system, which may include: Obtain the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system. Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure; the target structure includes at least an inducer wheel, a centrifugal wheel, and a turbine disk. Based on the initial axial clearance and the pressure inside the balance cavity of the dual-gap balancing system, the axial force in the balance cavity of the dual-gap balancing system is determined. Based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system, the remaining axial force of the target engine turbopump rotor system is determined.

[0006] Preferably, the dual-gap balancing system of the turbopump may include: two target balancing gaps; The two target balancing gaps are used to enhance the axial force balancing stiffness and adjustability of the dual-gap balancing system.

[0007] Preferably, the step of performing a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure may include using the following formula: ; Calculate the axial force at the inlet of the inducer; where F1 represents the axial force at the inlet of the inducer, P 11 Indicates the inlet pressure of the inducer, D 11 Indicates the outer diameter of the inducer, D 12 This indicates the diameter of the inducer hub.

[0008] Preferably, the step of performing a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure may include using the following formula: ; Determine the axial force F from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. 21 Among them, F 21 P represents the axial force from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. 12 Indicates the outlet pressure of the induced wheel, D 21 Indicates the diameter of the front shoulder of the centrifugal impeller, D 11 Indicates the outer diameter of the inducer, P 11 H1 represents the inlet pressure of the inducer, n1 represents the static head of the inducer, n2 represents the design speed of the turbine pump, ρ represents the calculated density of the medium, and g represents the acceleration due to gravity.

[0009] Preferably, the step of performing a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure may include using the following formula: ; Determine the axial force F in the front leakage cavity channel 22 Among them, F 22 P represents the axial force in the front leakage cavity channel.21 Indicates the pressure in the pre-leakage chamber, P 22 Indicates the centrifugal impeller outlet pressure, D 23 Indicates the outer diameter of the centrifugal wheel, D 21 H2 represents the diameter of the front shoulder of the centrifugal impeller, H2 represents the static head of the centrifugal impeller, and P represents the static head of the centrifugal impeller. 12 ρ represents the outlet pressure of the inducer, g represents the gravitational acceleration, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, and r represents the radius of the turbine pump.

[0010] Preferably, the step of performing a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure may include using the following formula: ; Determine the axial force F from the centrifugal impeller outlet to the high-pressure gap annular surface. 23 Among them, F 23 P represents the axial force from the centrifugal impeller outlet to the high-pressure gap annular surface. 23 This indicates the pressure distribution from the centrifugal impeller outlet to the high-pressure gap annulus, D 23 Indicates the outer diameter of the centrifugal wheel, D 24 Indicates the diameter of the high-pressure gap annular surface, P 22 Indicates the centrifugal impeller outlet pressure, P 12 ρ represents the outlet pressure of the inducer, g represents the density of the medium, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, H2 represents the static head of the centrifugal impeller, and r represents the radius of the turbine pump.

[0011] Preferably, the step of performing a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure may include using the following formula: ; Determine the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim; where F 25 This indicates the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim, D. 25 Indicates the diameter of the low-pressure gap annular surface, D 26 Indicates the outer ring diameter of the adjustment pad, P 25 This indicates the pressure from the low-pressure gap annular surface to the outer annular surface of the adjusting pad.

[0012] Preferably, determining the axial force in the balance cavity of the dual-gap balance system based on the initial axial clearance and the pressure within the balance cavity can include using the following formula: ; Determine the axial force F in the balancing chamber of the dual-gap balancing system. 24Among them, F 24 P represents the axial force in the balancing chamber of the dual-gap balancing system. 24 This indicates the pressure within the balance chamber of the dual-gap balancing system, D. 24 Indicates the diameter of the high-pressure gap annular surface, D 25 Indicates the diameter of the low-pressure gap annular surface, P 241 ρ represents the pressure after the high-pressure gap, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, and r represents the radius of the turbine pump.

[0013] Preferably, determining the remaining axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance chamber in the dual-clearance balance system may include using the following formula: ; Determine the remaining axial force of the target engine turbopump rotor system; where F represents the remaining axial force of the rotor system, F1 represents the axial force at the inducer inlet, and F... 21 F represents the axial force from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. 22 The axial force F in the front leakage cavity channel represents the axial force. 23 F represents the axial force from the centrifugal impeller outlet to the high-pressure gap annular surface. 24 F represents the axial force in the balancing chamber of the dual-gap balancing system. 25 F3 represents the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting pad, and F4 represents the axial force of the turbine disk.

[0014] Compared with existing technologies, this invention provides a method for determining the residual axial force of an engine turbopump rotor system. First, it obtains the target structure and operating parameters of the target engine turbopump, including at least structural dimensional parameters, structural pressure parameters, and the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system. Based on these parameters, a one-dimensional simulation calculation is performed on the target structure to obtain its axial force. The target structure includes at least an inducer wheel, a centrifugal wheel, and a turbine disk. Then, based on the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system, the axial force of the balance chamber in the dual-clearance balancing system is determined. Finally, based on the axial force of the target structure and the axial force of the balance chamber in the dual-clearance balancing system, the residual axial force of the engine turbopump rotor system is determined. This allows for rapid and accurate assessment and prediction of the residual axial force of the engine turbopump rotor system during the design phase, even without a three-dimensional model. It also supports effective control of the residual axial force during the assembly process. This solves the problem in existing technologies where the residual axial force of engine turbopumps cannot be assessed and predicted during the design phase.

[0015] In a second aspect, the present invention provides an apparatus for determining the remaining axial force of an engine turbopump rotor system, which may include: The acquisition module is used to acquire the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system. The target structure axial force determination module is used to perform one-dimensional simulation calculations on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure; the target structure includes at least an inducer wheel, a centrifugal wheel, and a turbine disk. A balance cavity axial force determination module is used to determine the axial force of the balance cavity in the dual-gap balance system based on the initial axial gap and the pressure inside the balance cavity. The remaining axial force determination module is used to determine the remaining axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system.

[0016] Compared with the prior art, the device for determining the remaining axial force of the engine turbopump rotor system provided by the present invention has the same beneficial effects as the method for determining the remaining axial force of the engine turbopump rotor system provided in the first aspect, and will not be described in detail here. Attached Figure Description

[0017] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings: Figure 1 A schematic diagram of the main process of a method for determining the residual axial force of an engine turbopump rotor system provided by the present invention; Figure 2 This is a schematic diagram of the main structure of the engine turbopump rotor system in a method for determining the residual axial force of an engine turbopump rotor system provided by the present invention. Figure 3 A schematic diagram showing the marked dimensions of the main structures in the engine turbopump rotor system provided by the present invention; Figure 4 A schematic diagram of the axial clearance of the high-pressure clearance of the main structure in the engine turbopump rotor system provided by the present invention; Figure 5 A schematic diagram of the axial clearance of the low-pressure clearance of the main structure in the engine turbopump rotor system provided by the present invention; Figure 6This is a schematic diagram of a device for determining the residual axial force of an engine turbopump rotor system, provided by the present invention.

[0018] Reference numerals: 1-Pump housing, 2-Dual clearance balancing system, 3-Bearing housing, 4-Turbine housing, 5-Inducer wheel, 6-Centrifugal wheel, 7-Adjusting shim, 8-Shaft sleeve, 9-Turbine disc shaft, D 11 -Inducer wheel outer diameter, D 12 -Inducer wheel hub diameter, D 21 -Centrifugal impeller front shoulder diameter, D 22 - Centrifugal wheel inner diameter, D 23 - Centrifugal wheel outer diameter, D 24 - High-pressure gap annular diameter, D 25 - Low-pressure gap annular diameter, D 26 - Adjust the outer ring diameter of the pad. Detailed Implementation

[0019] To facilitate a clear description of the technical solutions in the embodiments of the present invention, the terms "first" and "second" are used to distinguish identical or similar items with essentially the same function and effect. For example, the first threshold and the second threshold are merely used to distinguish different thresholds and do not limit their order. Those skilled in the art will understand that the terms "first" and "second" do not limit the quantity or execution order, and the terms "first" and "second" are not necessarily different.

[0020] It should be noted that in this invention, the terms "exemplary" or "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described as "exemplary" or "for example" in this invention should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of terms such as "exemplary" or "for example" is intended to present the relevant concepts in a concrete manner.

[0021] In this invention, "at least one" refers to one or more, and "more than one" refers to two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A alone, A and B simultaneously, or B alone, where A and B can be singular or plural. The character " / " generally indicates that the preceding related objects have an "or" relationship. "At least one of the following" or similar expressions refer to any combination of these items, including any combination of single or plural items. For example, at least one of a, b, or c can represent: a, b, c, a combination of a and b, a combination of a and c, a combination of b and c, or a, b, and c, where a, b, and c can be single or multiple.

[0022] Computational Fluid Dynamics (CFD) is a technique that uses computers to simulate the flow of liquids and gases. It is based on mathematical models established by the laws of conservation of mass, momentum, and energy. Currently, CFD methods are commonly used to calculate the residual axial force of rotor systems. However, CFD requires a three-dimensional model to support its simulation calculations, and the CFD simulation method requires significant computational resources. Since three-dimensional models are not available in the design phase of high-speed, high-pressure turbopumps, CFD methods cannot be used to calculate and control the axial force of turbopumps, nor can the residual axial force of turbopumps be evaluated and predicted. This leads to increased design difficulty and lower efficiency of engine turbopumps.

[0023] Therefore, the present invention provides a method and apparatus for determining the remaining axial force of an engine turbopump rotor system, which can quickly and accurately assess and predict the remaining axial force of the engine turbopump rotor system in the design stage, solving the problem in the prior art that it is impossible to assess and predict the remaining axial force of the engine turbopump in the design stage.

[0024] The technical solution of the present invention will now be described in detail with reference to the accompanying drawings: In a first aspect, the present invention provides a method for determining the residual axial force of an engine turbopump rotor system; see also Figure 1 , Figure 1 This is a schematic diagram of the main flow of a method for determining the residual axial force of an engine turbopump rotor system provided by the present invention. The execution subject of the method is a server or terminal equipped with the method for determining the residual axial force of an engine turbopump rotor system provided by the present invention; such as an evaluation test platform or a testable laptop computer.

[0025] exist Figure 1 In this context, the method may include: Step 110: Obtain the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least the structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system.

[0026] In step 110, the target structure of the target engine turbopump may include major structures such as an inducer wheel, centrifugal wheel, adjusting shim, bearing, shaft, and turbine disc. The structural dimensional parameters are the corresponding external and local dimensions of these major structures, such as inner diameter, outer diameter, length, and width. The turbopump axial force balancing system is equipped with two balancing gaps, one for high pressure and one for low pressure, i.e., a dual-gap balancing system. This system is used to enhance the axial force balancing stiffness and adjustment capability of the balancing system.

[0027] Step 120: Based on the target structure and operating parameters, perform a one-dimensional simulation calculation on the target structure in the target engine turbopump to obtain the axial force of the target structure; the target structure includes at least an inducer wheel, a centrifugal wheel, and a turbine disk.

[0028] In step 120, after performing one-dimensional simulation calculations based on the target structure and operating parameters, the axial force of the target structure must include at least the axial force of the inducer, the axial force of the centrifugal wheel, and the axial force of the turbine disk. The inlet axial force generated by the inducer is determined by the inlet pressure, the outer diameter of the inducer, and the diameter of the inducer hub. The axial force generated by the centrifugal wheel includes the axial force from the inducer outlet blade tip to the front shoulder of the centrifugal wheel, the axial force of the front leakage cavity channel, the axial force from the centrifugal wheel outlet to the high-pressure gap annular surface, the axial force of the balance cavity of the dual-gap balancing system, and the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting pad. The axial force of the turbine disk can also be determined by a blowing test using a turbine hot air blowing device.

[0029] Step 130: Based on the initial axial clearance of the dual-gap balancing system and the pressure inside the balancing cavity, determine the axial force of the balancing cavity in the dual-gap balancing system.

[0030] In step 130, the axial force in the balancing cavity of the dual-gap balancing system can be determined by the pressure inside the balancing cavity and the initial axial gap of the dual-gap balancing system. The initial axial gap of the dual-gap balancing system represents the diameters of the high-pressure gap annulus and the low-pressure gap annulus. That is, the pressure distribution inside the balancing cavity of the dual-gap balancing system needs to take into account the throttling losses caused by the high-pressure gap and the low-pressure gap. The pressure inside the balancing cavity of the dual-gap balancing system can be calculated from the pressure after the high-pressure gap, the diameter of the high-pressure gap annulus, and the diameter of the low-pressure gap annulus based on the pressure distribution model of the small gap wheel disc.

[0031] Step 140: Based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system, determine the remaining axial force of the target engine turbopump rotor system.

[0032] In step 140, the direction pointing towards the turbine can be taken as positive, and the remaining axial force of the target engine turbopump rotor system can be determined based on the inlet axial force generated by the inducer wheel, the axial force generated by the centrifugal wheel, and the axial force generated by the turbine disk, which are confirmed in steps 120 and 130 respectively. Thus, the remaining axial force of the rotor system can be calculated during the design stage of the engine turbopump without the need to build a three-dimensional model, which solves the problem in the prior art that the remaining axial force of the engine turbopump during the design stage cannot be evaluated and predicted.

[0033] Based on this, the method for determining the residual axial force of an engine turbopump rotor system provided by the present invention obtains the target structure and operating parameters of the target engine turbopump, including at least structural dimensional parameters, structural pressure parameters, and the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system. Then, based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including at least the inducer wheel, centrifugal wheel, and turbine disk. Next, based on the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system, the axial force of the balance chamber in the dual-clearance balancing system is determined. Finally, based on the axial force of the target structure and the axial force of the balance chamber in the dual-clearance balancing system, the residual axial force of the target engine turbopump rotor system is determined. This method enables rapid and accurate evaluation and prediction of the residual axial force of the turbopump rotor system during the design phase through one-dimensional simulation calculation, without the need to construct a three-dimensional model. This solves the problem that the CFD method commonly used in the prior art cannot evaluate and predict the residual axial force of the engine turbopump during the design phase.

[0034] It should be noted that the method for determining the remaining axial force of an engine turbopump rotor system provided by this invention is particularly applicable to determining the axial force of a dual-clearance balancing system for a high-speed, high-power liquid engine turbopump. In practical applications, there are many types of engine turbopumps, too numerous to list. To more clearly illustrate the technical solution provided by this invention, the following will use… Figures 2 to 5 The pump structure corresponding to the engine turbopump shown in the figure provides a detailed description of the method for dealing with the residual axial force of the engine turbopump rotor system provided by the present invention.

[0035] Please see Figures 2 to 5 , Figure 2 This is a schematic diagram of the main structure of the engine turbopump rotor system in a method for determining the residual axial force of an engine turbopump rotor system provided by the present invention. Figure 3 A schematic diagram showing the marked dimensions of the main structures in the engine turbopump rotor system provided by the present invention; Figure 4 A schematic diagram of the axial clearance of the high-pressure clearance of the main structure in the engine turbopump rotor system provided by the present invention; Figure 5 A schematic diagram of the axial clearance of the low-pressure clearance of the main structure in the engine turbopump rotor system provided by the present invention.

[0036] exist Figure 2In this design, the engine turbopump may include at least the following structures: pump housing 1, dual-clearance balancing system 2, bearing housing 3, turbine housing 4, inducer 5, centrifugal wheel 6, adjusting shim 7, bushing 8, and turbine disc shaft 9. The inducer 5, centrifugal wheel 6, adjusting shim 7, bushing 8, and turbine disc shaft 9 constitute the rotor system of the turbopump. The dual-clearance balancing system 2 of the turbopump may include two target balancing clearances: a high-pressure axial clearance and a low-pressure axial clearance. The radial clearance of the two target balancing clearances is smaller than the target clearance. The two target balancing clearances are used to enhance the axial force balancing stiffness and adjustment capability of the dual-clearance balancing system 2.

[0037] Specifically, the high-pressure and low-pressure axial clearances in the dual-clearance balancing system 2 of the turbopump can be changed synchronously, but the total axial stroke is fixed and generally does not exceed 1 mm. To ensure the effectiveness of the balancing system structure, the radial clearance between the high-pressure and low-pressure axial clearances generally does not exceed 1 mm. Simultaneously, a small-clearance disc structure can be formed by the front shoulder leakage chamber of the centrifugal impeller 6 and the leakage chamber of the dual-clearance balancing system 22, where the average angular velocity of the internal medium rotation is equal to half the impeller's rotational angular velocity. Then, based on the theoretical derivation of the small-clearance disc pressure distribution model, one-dimensional calculations are performed on the axial forces of the inducer wheel 5, centrifugal impeller 6, and dual-clearance balancing system 2. The axial force of the turbine disc shaft 9 can be measured through methods such as hot air blowing tests, thereby obtaining the remaining axial force of the entire rotor system. Therefore, by changing the high and low pressure clearances of the balancing system and iteratively calculating with the expected remaining axial force, the required high and low pressure clearances can be obtained. Furthermore, by processing adjustment shims, the high and low pressure clearances during the assembly process can be precisely adjusted, achieving control of the turbopump's remaining axial force during assembly.

[0038] During the operation of the engine turbopump, its inducer wheel 5, centrifugal wheel 6, and turbine disk shaft 9 generate significant axial forces. These forces can be balanced by the dual-clearance balancing system 2. The remaining axial force in the rotor system is borne by the thrust bearing. To ensure the safe operation of the turbopump, the magnitude of the remaining axial force in the rotor system under different operating conditions must not exceed the bearing's load-bearing capacity. The dual-clearance balancing system 2 includes both high-pressure and low-pressure clearances, forming a balancing chamber. Both clearances include a fixed radial clearance and a variable axial clearance, with a fixed total axial clearance stroke. During operation, the axial force of the dual-clearance balancing system 2 is altered by changing the axial clearance, further changing the axial force generated by the centrifugal wheel 6, thereby adjusting the remaining axial force of the entire rotor system. In other words, the remaining axial force of the rotor is jointly determined by the inlet axial force generated by the inducer wheel 5, the axial force generated by the centrifugal wheel 6, and the axial force generated by the turbine disk shaft 9.

[0039] As an optional embodiment, in step 120, please refer to... Figures 3 to 5Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, which may include the use of the following formula: (1); Calculate the axial force at the inlet of inducer 5; where F1 represents the axial force at the inlet of inducer 5, P 11 Indicates the inlet pressure of inducer wheel 5, D 11 Indicates the outer diameter of the inducer wheel 5, D 12 This represents the hub diameter of inducer 5. This allows us to obtain the axial force at the inlet of inducer 5.

[0040] Further research revealed that the axial force generated by the centrifugal wheel 6 can include the axial force from the tip of the outlet blade of the inducer 5 to the front shoulder of the centrifugal wheel 6, the axial force from the front leakage cavity channel, the axial force from the outlet of the centrifugal wheel 6 to the high-pressure gap annular surface, the axial force from the balance cavity of the dual-gap balance system 2, and the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting pad.

[0041] As an optional embodiment, based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, which may include using the formula: (2); Determine the axial force from the tip of the inducer 5 outlet blade to the front shoulder of the centrifugal impeller 6; where F 21 P represents the axial force from the tip of the inducer 5 outlet blade to the front shoulder of the centrifugal impeller 6. 12 Indicates the outlet pressure of inducer wheel 5, D 21 Indicates the diameter of the front shoulder of the centrifugal wheel 6, D 11 Indicates the outer diameter of the inducer wheel 5, P 11 H1 represents the inlet pressure of inducer 5, n1 represents the static head of inducer 5, n2 represents the design speed of turbine pump, ρ represents the calculated density of medium, and g represents the acceleration due to gravity.

[0042] Further research revealed that the pressure P in the pre-leakage chamber... 21 The distribution of is related to the impeller's angular velocity ω. In the small-clearance disc model, is a variable related to the radius r, and the average angular velocity of the liquid rotation is equal to half the impeller's angular velocity. From the radial equilibrium equation in the small-clearance disc model, we can obtain: (3); Furthermore, the above formula can be derived from the diameter D of the front shoulder of the centrifugal wheel 6. 21 To the centrifugal wheel 6 outer diameter D 23 Integrating, we obtain the pressure P in the pre-leakage chamber. 21 The distribution with respect to diameter D is as follows, where P 22 The outlet pressure of centrifugal impeller 6; (4); Furthermore, the formula can be used: (5); Determine the outlet pressure of centrifugal impeller 6; where P 22 H1 represents the outlet pressure of centrifugal impeller 6, H2 represents the static head of centrifugal impeller 6, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, and P represents the outlet pressure of centrifugal impeller 6. 12 ρ represents the outlet pressure of the inducer wheel 5, ρ represents the density of the medium, and g represents the acceleration due to gravity.

[0043] Further research revealed that the pressure in the front leakage chamber channel can be integrated and rearranged from the diameter of the front shoulder of the centrifugal wheel 6 to the outer diameter of the centrifugal wheel 6 to obtain the axial force in the front leakage chamber channel.

[0044] As an optional embodiment, based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, which may include using the formula: (6); Determine the axial force in the front leakage cavity channel; where F 22 P represents the axial force in the front leakage cavity channel. 21 Indicates the pressure in the pre-leakage chamber, P 22 Indicates the outlet pressure of centrifugal impeller 6, D 23 Indicates the outer diameter of the centrifugal wheel 6, D 21 H2 represents the diameter of the front shoulder of centrifugal impeller 6, H2 represents the static head of centrifugal impeller 6, and P represents the diameter of the front shoulder of centrifugal impeller 6. 12 ρ represents the outlet pressure of the inducer 5, g represents the gravitational acceleration, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, and r represents the radius of the turbine pump.

[0045] Further research revealed that the axial force from the outlet of centrifugal wheel 6 to the high-pressure gap annulus can be determined by the pressure distribution from the outlet of centrifugal wheel 6 to the high-pressure gap annulus, the outer diameter of centrifugal wheel 6, and the diameter of the high-pressure gap annulus. The pressure distribution from the outlet of centrifugal wheel 6 to the high-pressure gap annulus can be calculated based on the small gap disc pressure distribution model, using the outlet pressure of centrifugal wheel 6 and the outer diameter of centrifugal wheel 6.

[0046] As an optional embodiment, based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, which may include using the formula: (7); Determine the axial force from the outlet of centrifugal impeller 6 to the high-pressure gap annular surface; where F 23 P represents the axial force from the outlet of centrifugal impeller 6 to the high-pressure gap annular surface.23 This indicates the pressure distribution from the outlet of centrifugal impeller 6 to the high-pressure gap annulus, D 23 Indicates the outer diameter of the centrifugal wheel 6, D 24 Indicates the diameter of the high-pressure gap annular surface, P 22 Indicates the outlet pressure of centrifugal impeller 6, P 12 The values ​​represent the outlet pressure of the inducer wheel 5, ρ represents the density of the medium, g represents the acceleration due to gravity, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, H2 represents the static head of the centrifugal wheel 6, and r represents the radius of the turbine pump.

[0047] Further research revealed that the axial force in the balancing chamber of the dual-gap balancing system 2 can be determined by the pressure within the balancing chamber, the diameter of the high-pressure gap annulus, and the diameter of the low-pressure gap annulus. Specifically, the pressure P within the balancing chamber of the dual-gap balancing system 2... 24 The distribution needs to consider the throttling losses caused by the high-pressure and low-pressure gaps. A dual-gap balancing system 2 balances the pressure P within the chamber. 24 Pressure P after the high-pressure gap 241 and the diameter D of the high-pressure gap ring 24 The pressure distribution model of the small-gap wheel disk was calculated.

[0048] As an optional embodiment, the formula can be used: (8); Calculate the pressure inside the equilibrium chamber; where P 24 Indicates the pressure inside the equilibrium chamber, D 24 n represents the diameter of the high-pressure gap annulus, n2 represents the actual speed of the turbine pump, D represents the diameter variable, ρ represents the medium density, and P represents the diameter of the high-pressure gap annulus. 241 This indicates the pressure after the high-pressure gap.

[0049] Further research revealed that the pressure after the high-pressure gap can be calculated from the pressure before the high-pressure gap and the throttling loss of the high-pressure gap; specifically, the pressure before the high-pressure gap can be calculated from the pressure distribution from the outlet of centrifugal wheel 6 to the annular surface of the high-pressure gap. The throttling loss of the low-pressure gap can be calculated from the pressure before the low-pressure gap and the pressure from the annular surface of the low-pressure gap to the outer annular surface of the adjusting pad. The flow coefficients of the high-pressure gap and the low-pressure gap are equal; therefore, the throttling losses of the high-pressure gap and the low-pressure gap are inversely proportional to the area of ​​the high-pressure gap and the square of the area of ​​the low-pressure gap, respectively. The pressure distribution within the balancing chamber of the dual-gap balancing system 2 also follows the small-gap wheel model. The total pressure difference before and after the balancing chamber of the dual-gap balancing system 2 can be determined by the pressure before the high-pressure gap, the pressure from the annular surface of the low-pressure gap to the outer annular surface of the adjusting pad, and is equal to the sum of the throttling losses of the high-pressure gap, the low-pressure gap, and the pressure difference within the balancing chamber of the dual-gap balancing system 2. From this, the following formula can be obtained: (9); Solving the above formulas simultaneously yields the following formula for calculating the pressure after the high-pressure gap: (10); High-pressure gap area S 241 It can be calculated from the axial clearance, radial clearance, and annular diameter of the high-pressure gap. The calculation formula is as follows: (11); The area of ​​the low-pressure gap can be calculated from the total axial clearance stroke, the axial clearance of the high-pressure gap, the radial clearance of the low-pressure gap, and the annular diameter of the low-pressure gap. The calculation formula is as follows: (12); In formulas (9) to (12), P 241 Indicates the pressure after the high-pressure gap, P 232 Indicates the pressure before the high-pressure gap, This represents the high-voltage gap throttling loss, dP 242 Indicates low-pressure gap throttling loss, P 242 Indicates the pressure before the low-pressure gap, P 25 This indicates the pressure from the low-pressure gap annular surface to the outer annular surface of the adjusting shim, S 241 Indicates the area of ​​the high-pressure gap, S 242 dP represents the area of ​​the low-pressure gap, dP represents the total pressure difference across the balancing chamber of the dual-gap balancing system, and P represents the total pressure difference across the balancing chamber. 232 The pressure before the high-pressure gap is represented by Xa1, the axial clearance of the high-pressure gap is represented by dY1, and the radial clearance of the high-pressure gap is represented by D. 24 The high-pressure clearance is represented by the toroidal diameter, Xa by the total axial clearance stroke, dY2 by the radial clearance of the low-pressure clearance, and D by the toroidal diameter. 25 This indicates the calculation of the diameter of the low-pressure gap annular surface.

[0050] Furthermore, after obtaining a certain axial clearance Xa1, one-dimensional simulation calculations can be performed to determine the axial force in the balancing cavity of the dual-clearance balancing system 2. That is, based on the initial axial clearance and the pressure inside the balancing cavity of the dual-clearance balancing system 2, the axial force in the balancing cavity of the dual-clearance balancing system 2 can be determined, which may include using the following formula: (13); Determine the axial force F in the balancing chamber of the dual-gap balancing system 2. 24 Among them, F 24 The axial force P in the balancing chamber of the dual-gap balancing system 2 represents the force. 24 This indicates the pressure within the balancing chamber of the dual-gap balancing system 2, D. 24 Indicates the diameter of the high-pressure gap annular surface, D 25 Indicates the diameter of the low-pressure gap annular surface, P 241ρ represents the pressure after the high-pressure gap, n1 represents the design speed of the turbine pump, n2 represents the actual speed of the turbine pump, and r represents the radius of the turbine pump.

[0051] Furthermore, the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim can be calculated from the diameter of the low-pressure gap annular surface, the diameter of the outer annular surface of the adjusting shim, and the pressure from the low-pressure gap annular surface to the outer annular surface of the adjusting shim; that is, based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the formula: (14); Determine the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim; where F 25 This indicates the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim, D. 25 Indicates the diameter of the low-pressure gap annular surface, D 26 Indicates the outer ring diameter of the adjustment pad, P 25 This indicates the pressure from the low-pressure gap annular surface to the outer annular surface of the adjusting pad.

[0052] In practical applications, the axial force F3 generated by the turbine wheel shaft 9 can be obtained by a blowing test using a turbine hot air blowing device.

[0053] Furthermore, a one-dimensional simulation calculation can be performed with the direction pointing towards the turbine as the positive direction to obtain the remaining axial force of the target engine turbopump rotor system. That is, based on the axial force of the target structure and the axial force of the balancing chamber in the dual-clearance balancing system 2, the remaining axial force of the target engine turbopump rotor system is determined, including using the formula: (15); Determine the remaining axial force of the target engine turbopump rotor system; where F represents the remaining axial force of the rotor system, F1 represents the axial force at the inlet of the inducer 5, and F... 21 F represents the axial force from the tip of the inducer 5 outlet blade to the front shoulder of the centrifugal impeller 6. 22 The axial force F in the front leakage cavity channel represents the axial force. 23 F represents the axial force from the outlet of centrifugal impeller 6 to the high-pressure gap annular surface. 24 The axial force F in the balancing chamber of the dual-gap balancing system 2 represents the force. 25 F3 represents the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting pad, and F3 represents the axial force of the turbine wheel shaft 9.

[0054] Furthermore, to better illustrate the effectiveness of the method provided by this invention for determining the residual axial force of an engine turbopump rotor system, in Figures 2 to 5 Based on this, the method of the present invention is verified by calculation using specific engine turbopump design parameters.

[0055] For example, the target structure and operating parameters (design parameters) of the target engine turbopump may include: the inlet pressure P of the inducer 5. 11 The pressure is 4MPa, and the outer diameter D of the inducer is 5. 11 400mm, idler wheel hub diameter D 12 The diameter is 200mm. Therefore, the axial force F1 at the inlet of the inducer wheel 5 can be calculated using formula (1): 376991.1N.

[0056] Furthermore, the target structure and operating parameters (design parameters) of the target engine turbopump may also include: the outlet pressure P of the inducer 5. 12 10MPa, centrifugal impeller with 6 front shoulder diameter D 21 The diameter is 450 mm. Therefore, the axial force F from the tip of the inducer 5 outlet blade to the front shoulder of the centrifugal wheel 6 can be calculated using formula (2). 21 The value is: 333794.2N.

[0057] Furthermore, the target structure and operating parameters (design parameters) of the target engine turbopump may also include: centrifugal impeller 6 outlet pressure P 22 The pressure is 50 MPa, and the outer diameter D of the centrifugal impeller is 6. 23 The diameter is 600mm, the actual speed of the turbine pump n2 is 30000r / min, and the density of the medium ρ is 1000kg / m³. 3 Therefore, the axial force F of the front leakage cavity channel can be calculated using formula (6). 22 The value is: 3180520.5N.

[0058] Furthermore, the target structure and operating parameters (design parameters) of the target engine turbopump may also include: the diameter D of the high-pressure clearance annular surface. 24 The diameter is 400 mm, so the axial force from the outlet of centrifugal wheel 6 to the high-pressure gap annulus can be calculated using formula (7). The value is: 3009251.0N.

[0059] Furthermore, the target structure and operating parameters (design parameters) of the target engine turbopump may also include: the diameter of the low-pressure clearance annular surface. 300mm, outer ring diameter of the adjusting shim The pressure from the 200mm low-pressure gap annular surface to the outer annular surface of the adjusting pad is... The pressure is 3.0 MPa, so the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting pad can be calculated using formula (14). The value is: 117809.7N.

[0060] Furthermore, the axial force of the turbine disk 9 of the target engine turbopump was determined to be 600,000 N through a hot air blowing test.

[0061] Furthermore, the target structure and operating parameters (design parameters) may also include: the radial clearance of the high-pressure gap. The radial clearance is 1mm, which is the low-pressure gap. The axial clearance is 1mm, and the total stroke Xa of the axial clearance is 1mm.

[0062] Furthermore, the expected residual axial force of the rotor system is set. Since the value is 0N, the axial force of the required double-gap balancing system 2 balancing cavity can be calculated using formula (13). The value is: 1364245.2N;

[0063] Furthermore, the axial clearance of the high-pressure gap is further examined. From 0~ The required axial clearance for high-pressure clearance is calculated by taking values ​​at 0.1 mm intervals and performing linear interpolation. The calculated value is 0.852 mm. By machining the corresponding adjustment shims during the assembly process, it can be ensured that the axial force of the turbopump rotor system in the working state is equal to the expected residual axial force. This enables the determination of the target axial clearance based on the target residual axial force, ensuring that the axial force of the turbopump rotor system in the working state is equal to the expected residual axial force. This achieves efficient prediction and control of the residual axial force of the engine turbopump rotor system in the design stage.

[0064] Therefore, the method for determining the remaining axial force of the engine turbopump rotor system provided by the present invention can also determine the target axial clearance of the dual-clearance balance system 2 corresponding to the target remaining axial force through S1 to S4.

[0065] S1: Obtain the remaining axial force of the target.

[0066] S2: Determine whether the remaining axial force of the target engine turbopump rotor system is equal to the target remaining axial force; if the remaining axial force of the target engine turbopump rotor system is equal to the target remaining axial force, then determine the initial axial clearance as the target axial clearance of the dual clearance balance system 2 corresponding to the target remaining axial force.

[0067] S3: If the remaining axial force of the target engine turbopump rotor system is not equal to the target remaining axial force, then adjust the initial axial clearance, and determine the intermediate axial force of the balance chamber in the dual-clearance balance system 2 based on the adjusted initial axial clearance and the dual-clearance throttling loss parameter.

[0068] S4: Based on the axial force of the target structure and the intermediate axial force, determine the second residual axial force of the target engine turbopump rotor system until the second residual axial force is equal to the target residual axial force, and determine the adjusted initial axial clearance as the target axial clearance of the dual clearance balance system 2 corresponding to the target residual axial force.

[0069] Based on this, the present invention can determine the target axial clearance of the dual-clearance balancing system 2 corresponding to the target residual axial force; similarly, by changing the axial clearance of the high-pressure clearance and the actual operating speed of the turbopump, the residual axial force of the rotor system under different axial clearances and operating conditions can be obtained. By interpolating with the expected residual axial force, the axial clearance of the high-pressure clearance of the dual-clearance balancing system 2 under the desired operating state can be obtained. During the assembly process, based on the actual dimensional measurements, the required shim thickness can be determined and processed, thereby controlling the residual axial force of the turbopump under the operating state during the assembly process and achieving bidirectional verification. This allows for rapid and accurate evaluation of the residual axial force of the rotor system under different operating conditions during the initial design phase, based on the influence of the dual-clearance balancing system 2 on the residual axial force of the rotor system, effectively shortening the design cycle; and solving the problem in the prior art that the residual axial force of the engine turbopump cannot be evaluated and predicted during the design phase.

[0070] Secondly, the present invention provides a device for determining the remaining axial force of an engine turbopump rotor system. (See also...) Figure 6 , Figure 6 This is a schematic diagram of a device for determining the residual axial force of an engine turbopump rotor system, provided by the present invention.

[0071] exist Figure 6 The device for determining the remaining axial force of the engine turbopump rotor system may include: The acquisition module 610 is used to acquire the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least the structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system.

[0072] The target structure axial force determination module 620 is used to perform one-dimensional simulation calculations on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure; the target structure includes at least an inducer wheel, a centrifugal wheel, and a turbine disk.

[0073] The axial force determination module 630 for the balancing cavity is used to determine the axial force of the balancing cavity in the dual-gap balancing system based on the initial axial gap and the pressure inside the balancing cavity.

[0074] The residual axial force determination module 640 is used to determine the residual axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system.

[0075] Compared with the prior art, the present invention provides a device for determining the residual axial force of an engine turbopump rotor system. First, the target structure and operating parameters of the target engine turbopump are acquired by the acquisition module 610. The target structure and operating parameters include at least structural dimensional parameters, structural pressure parameters, and the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system. Then, the target structure axial force determination module 620 performs a one-dimensional simulation calculation on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure. The target structure includes at least an inducer, a centrifugal impeller, and a turbine disk. Further, the balance chamber axial force determination module 63... Based on the initial axial clearance and pressure within the balance chamber of the dual-clearance balancing system, the axial force of the balance chamber in the dual-clearance balancing system is determined. Finally, the residual axial force determination module 640 determines the residual axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance chamber in the dual-clearance balancing system. Thus, considering the influence of the dual-clearance balancing system on the residual axial force of the rotor system, it is possible to quickly and accurately evaluate the residual axial force of the engine turbopump rotor system under different operating conditions during the initial design phase, effectively shortening the design cycle and solving the problem in the prior art that it is impossible to evaluate and predict the residual axial force of the engine turbopump during the design phase.

[0076] Although the invention has been described herein in conjunction with various embodiments, those skilled in the art will understand and implement other variations of the disclosed embodiments by reviewing the accompanying drawings, the disclosure, and the appended claims in carrying out the claimed invention. In the claims, the word "comprising" does not exclude other components or steps, and "a" or "an" does not exclude a plurality. A single processor or other unit can implement several functions listed in the claims. While different dependent claims may recite certain measures, this does not mean that these measures cannot be combined to produce good results.

[0077] Although the invention has been described in conjunction with specific features and embodiments, it is obvious that various modifications and combinations can be made therein without departing from the spirit and scope of the invention. Accordingly, this specification and drawings are merely exemplary descriptions of the invention as defined by the appended claims, and are considered to cover any and all modifications, variations, combinations, or equivalents within the scope of the invention. Clearly, those skilled in the art can make various alterations and modifications to the invention without departing from its spirit and scope. Thus, if such modifications and modifications of the invention fall within the scope of the claims and their equivalents, the invention is also intended to include such modifications and modifications.

Claims

1. A method for determining the residual axial force of an engine turbopump rotor system, characterized in that, include: Obtain the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system. Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure. The target structure includes at least an inducer, a centrifugal wheel, and a turbine disk; Based on the initial axial clearance and the pressure inside the balance cavity of the dual-gap balancing system, the axial force in the balance cavity of the dual-gap balancing system is determined. Based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system, the remaining axial force of the target engine turbopump rotor system is determined.

2. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, The dual-gap balancing system of the turbopump includes: two target balancing gaps; The two target balancing gaps are used to enhance the axial force balancing stiffness and adjustability of the dual-gap balancing system.

3. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the following formula: Calculate the axial force at the inlet of the inducer; where, Indicates the axial force at the inlet of the inducer. Indicates the inlet pressure of the inducer wheel, Indicates the outer diameter of the inducer, This indicates the diameter of the inducer hub.

4. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the following formula: Determine the axial force from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. ;in, This represents the axial force from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. Indicates the pressure at the outlet of the induced wheel, Indicates the diameter of the front shoulder of the centrifugal impeller, Indicates the outer diameter of the inducer, Indicates the inlet pressure of the inducer wheel, Indicates the static head of the induced wheel, Indicates the design speed of the turbopump, Indicates the actual speed of the turbopump, Indicates the density of the medium, It represents the acceleration due to gravity.

5. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the following formula: Determine the axial force in the front leakage cavity channel. ;in, P represents the axial force in the front leakage cavity channel. 21 Indicates the pressure in the pre-leakage chamber. Indicates centrifugal impeller outlet pressure, Indicates the outer diameter of the centrifugal wheel, Indicates the diameter of the front shoulder of the centrifugal impeller, Indicates the static head of the centrifugal impeller, Indicates the pressure at the outlet of the induced wheel, Indicates the density of the medium, Represents gravitational acceleration, Indicates the design speed of the turbopump, Indicates the actual speed of the turbopump, This indicates the radius of the turbopump.

6. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the following formula: Determine the axial force from the centrifugal impeller outlet to the high-pressure gap annular surface. ;in, This represents the axial force from the centrifugal impeller outlet to the high-pressure gap annular surface. This indicates the pressure distribution from the centrifugal impeller outlet to the high-pressure gap annulus. Indicates the outer diameter of the centrifugal wheel, Indicates the diameter of the high-pressure gap annular surface. Indicates centrifugal impeller outlet pressure, Indicates the pressure at the outlet of the induced wheel, Indicates the density of the medium, Represents gravitational acceleration, Indicates the design speed of the turbopump, Indicates the actual speed of the turbopump, Indicates the static head of the centrifugal impeller, This indicates the radius of the turbopump.

7. The method for determining the remaining axial force of an engine turbopump rotor system as described in claim 1, characterized in that, Based on the target structure and operating parameters, a one-dimensional simulation calculation is performed on the target structure in the target engine turbopump to obtain the axial force of the target structure, including using the following formula: Determine the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim; where, This indicates the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim. Indicates the diameter of the low-pressure gap annular surface, Indicates the diameter of the outer ring of the adjusting pad, This indicates the pressure from the low-pressure gap annular surface to the outer annular surface of the adjusting pad.

8. The method for determining the residual axial force of an engine turbopump rotor system as described in claim 1, characterized in that, The determination of the axial force in the balance cavity of the dual-gap balancing system based on the initial axial clearance and the pressure within the balance cavity includes using the following formula: Determine the axial force in the balancing chamber of the dual-gap balancing system ;in, This indicates the axial force in the balancing chamber of the dual-gap balancing system. This indicates the pressure within the balance chamber of the dual-gap balancing system, D. 24 Indicates the diameter of the high-pressure gap annular surface. Indicates the diameter of the low-pressure gap annular surface, Indicates the pressure after the high-pressure gap. Indicates the density of the medium, Indicates the design speed of the turbopump, Indicates the actual speed of the turbopump, This indicates the radius of the turbopump.

9. The method for determining the residual axial force of an engine turbopump rotor system as described in claim 1, characterized in that, The remaining axial force of the target engine turbopump rotor system is determined based on the axial force of the target structure and the axial force of the balance chamber in the dual-clearance balance system, including by using the following formula: Determine the remaining axial force of the target engine turbopump rotor system; where, Indicates the remaining axial force of the rotor system, Indicates the axial force at the inlet of the inducer. This represents the axial force from the tip of the inducer outlet blade to the front shoulder of the centrifugal impeller. Indicates the axial force in the front leakage cavity channel, This represents the axial force from the centrifugal impeller outlet to the high-pressure gap annular surface. This indicates the axial force in the balancing chamber of the dual-gap balancing system. This indicates the axial force from the low-pressure gap annular surface to the outer annular surface of the adjusting shim. This represents the axial force on the turbine disk.

10. A device for determining the residual axial force of an engine turbopump rotor system, characterized in that, include: The acquisition module is used to acquire the target structure and operating parameters of the target engine turbopump; the target structure and operating parameters include at least structural dimension parameters, structural pressure parameters, and the initial axial clearance and pressure inside the balance chamber of the dual clearance balancing system. The target structure axial force determination module is used to perform one-dimensional simulation calculations on the target structure in the target engine turbopump based on the target structure and operating parameters to obtain the axial force of the target structure. The target structure includes at least an inducer, a centrifugal wheel, and a turbine disk; A balance cavity axial force determination module is used to determine the axial force of the balance cavity in the dual-gap balance system based on the initial axial gap and the pressure inside the balance cavity. The remaining axial force determination module is used to determine the remaining axial force of the target engine turbopump rotor system based on the axial force of the target structure and the axial force of the balance chamber in the dual-gap balance system.

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