Impeller machinery flow simulation calculation method and system

Abstract

The present invention relates to the field of numerical research on impeller machinery flow with interlaced moving parts and stationary parts, such as aircraft engines, gas turbines and steam turbines, and specifically to a calculation method and system for impeller machinery flow simulation. The method obtains the calculation domain of the impeller machinery moving parts and the calculation domain of the impeller machinery static parts; then, assigns motion parameters to them respectively; finally, performs numerical calculation of the impeller machinery simulation based on the assigned parameters. The method can ensure that the coordinates of the numerical nodes in the calculation domain of the impeller machinery moving parts do not change with the sweeping process, improve the post-processing accuracy for the impeller machinery moving parts, facilitate the data transmission of the impeller machinery moving parts and the docking with other solvers, and has strong applicability. It solves the problem of low accuracy of impeller machinery flow simulation due to changes in blade position in the existing technology.

Description

Technical Field

[0001] The present invention relates to the field of numerical research on turbomachinery flow with interlaced moving and stationary parts, such as aircraft engines, gas turbines and steam turbines, and in particular to a calculation method and system for turbomachinery flow simulation. Background Art

[0002] Thanks to the development of computer hardware and numerical calculation methods, computational fluid dynamics is now widely used in the study of specific flow patterns in various turbomachinery. The usual calculation process is to discretize the fluid computational domain of the object being studied, then set boundary conditions and perform a numerical solution.

[0003] In flow simulations of these turbomachinery systems, frame motion (moving frame, frozen rotor) or meshmotion (sliding mesh) methods are typically used to simulate the motion of the computational domain for high-speed rotating blades. This allows for consideration of centrifugal and Coriolis forces in the fluid in a non-inertial reference frame. Furthermore, in numerical simulations of the turbomachinery stage, comprised of both stationary and rotating blades, the moving mesh method enables the motion of the computational domain within the computational space, enabling detailed simulation of the interplay between static and dynamic components.

[0004] However, for moving blades, the position of the blades changes during the calculation process, which has caused problems in some numerical calculation studies. For example, the moving calculation domain will cause the coordinate values ​​of its grid nodes in the calculation space to change, and the parameters of a certain point on the blade extracted in post-processing will become inaccurate or difficult to achieve. When combining structural mechanics software for fluid-structure coupling analysis, the overall displacement of the blade surface nodes at each time step causes the aerodynamic load to be unable to be transmitted normally. The displacement caused by blade rotation and deformation has a large difference in magnitude, which will cause the blade deformation to be distorted during numerical calculation. The method of using a moving coordinate system will keep the relative position of the moving and stationary blades unchanged, and it is impossible to simulate the process of the moving blade sweeping over the stationary parts. As a result, the post-processing accuracy of the moving blade simulation is low and cannot meet the accuracy requirements of the flow simulation of the impeller machinery.

[0005] Therefore, there is an urgent need for a flow simulation method for turbomachinery with high accuracy and strong applicability to meet the requirements of the current field of numerical research on turbomachinery flow. Summary of the Invention

[0006] In view of the problem that the flow simulation of impeller machinery in the existing technology has low accuracy due to the change of blade position, which cannot meet the accuracy requirements of the field of numerical research on impeller machinery flow, the present invention provides an impeller machinery flow simulation calculation method and system.

[0007] In order to achieve the above object, the present invention adopts the following technical solutions:

[0008] The present invention provides a turbomachinery flow simulation calculation method, comprising the following steps:

[0009] Obtain the computational domain of the impeller machinery dynamic components and the computational domain of the impeller machinery static components;

[0010] Assigning a motion law for the rotor to the calculation domain of the impeller machinery moving parts, wherein the motion law for the rotor is a motion of a moving coordinate system;

[0011] Assigning a motion law for the stator to the computational domain of the impeller machine static component, wherein the motion law for the stator is a combination of the motion of the moving coordinate system and the motion of the grid;

[0012] Numerical calculations of turbomachinery simulation are performed based on the motion laws of the rotor and the stator.

[0013] Preferably, the calculation domain of the impeller machinery moving parts and the calculation domain of the impeller machinery static parts are both independent discrete domains.

[0014] Furthermore, the specific operation of assigning the motion law of the rotor to the computational domain of the impeller machinery moving parts is as follows:

[0015] The motion law of the rotor is set as the motion of the moving coordinate system;

[0016] The moving coordinate system motion parameters are set for the moving coordinate system motion of the rotor.

[0017] Furthermore, the motion parameters of the dynamic coordinate system include the rotation axis and rotation speed of the calculation domain of the impeller machinery moving component or the equivalent translational motion direction and speed of the calculation domain of the impeller machinery moving component.

[0018] Furthermore, the method for setting the motion parameters of the moving coordinate system is:

[0019] For rotational motion: make the rotation axis and rotation speed of the computational domain of the impeller machinery moving parts the same as the rotation axis and rotation speed of the impeller machinery moving parts under the actual research conditions, that is:

[0020]

[0021] Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the impeller machinery moving parts are made the same as the motion direction and linear velocity of the impeller machinery moving parts under the actual research conditions, that is:

[0022]

[0023] in, is the set angular velocity of the impeller mechanical moving parts, is the actual angular velocity of the impeller machine moving parts; The linear velocity of the coordinate system set for the equivalent impeller machine moving parts, is the true linear velocity of the impeller mechanical moving parts.

[0024] Furthermore, the specific operation of assigning the motion law of the stator to the computational domain of the impeller machine static components is as follows:

[0025] The motion law for the stator is set as a motion combining the motion of the moving coordinate system and the motion of the moving grid;

[0026] Setting the moving coordinate system motion parameters for the moving coordinate system motion of the stator;

[0027] Set the dynamic mesh motion parameters for the dynamic mesh motion of the stator.

[0028] Furthermore, the motion parameters set for the dynamic coordinate system of the stator include the rotation axis and rotation speed of the dynamic coordinate system of the static component calculation domain or the equivalent translational motion direction and speed; the parameters set for the dynamic grid motion of the stator include the rotation axis and rotation speed of the dynamic grid motion of the static component calculation domain or the equivalent translational motion direction and speed.

[0029] Furthermore, the specific operation of setting the moving coordinate system motion parameters for the moving coordinate system motion of the stator is:

[0030] For rotational motion: make the rotation axis and rotation speed of the computational domain of the static parts of the impeller machinery the same as the rotation axis and rotation speed of the dynamic parts of the impeller machinery under the actual research conditions, that is:

[0031]

[0032] Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the impeller machinery moving parts are made the same as the motion direction and linear velocity of the impeller machinery moving parts under the actual research conditions, that is:

[0033]

[0034] in, is the angular velocity of the stator calculation domain coordinate system, is the linear velocity of the stator in the calculation domain coordinate system.

[0035] Furthermore, the specific operation of setting the dynamic mesh motion parameters for the static dynamic mesh motion is:

[0036] For rotational motion: the rotation axis of the computational domain mesh assigned to the stationary part of the impeller machinery is made the same as the rotation axis of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, and the rotation speed of the computational domain mesh of the stationary part is opposite to the rotation speed of the dynamic part of the impeller machinery under the actual research working conditions, that is:

[0037]

[0038] Or for equivalent translational motion, the translational motion velocity of the static components of the impeller machinery in the computational domain is made opposite to the equivalent translational motion velocity of the dynamic components of the impeller machinery under the actual research conditions, that is:

[0039]

[0040] The final momentum equation of the computational domain of the impeller machinery static parts after simultaneously assigning the motion law in the rotating coordinate system and the grid motion law is:

[0041]

[0042] Where ρ is the fluid density, is the composite velocity of the working fluid under the two motion laws, t is time, p is pressure, is the shear force, To strengthen your physical strength.

[0043] A turbomachinery flow simulation calculation system, comprising:

[0044] Computational domain acquisition module: used to obtain the computational domain of the impeller machinery dynamic components and the computational domain of the impeller machinery static components;

[0045] Rotor motion law assignment module: used to assign the motion law for the rotor to the calculation domain of the impeller machinery moving parts. The motion law for the rotor is the motion of the moving coordinate system.

[0046] Stator motion law assignment module: used to assign the motion law for the stator to the computational domain of the impeller machinery static components. The motion law for the stator is a combination of the motion of the moving coordinate system and the grid motion.

[0047] Numerical calculation module: used to perform numerical calculations of impeller machinery simulation based on the motion laws of the rotor and the motion laws of the stator.

[0048] Compared with the prior art, the present invention has the following beneficial effects:

[0049] The present invention provides a method for flow simulation calculation of an impeller machinery. The method obtains a calculation domain of an impeller machinery moving part and a calculation domain of an impeller machinery static part; then, the calculation domain of the impeller machinery moving part and the calculation domain of the impeller machinery static part are respectively assigned motion laws for the rotor and motion laws for the stator; finally, the impeller machinery simulation numerical calculation is performed according to the motion laws for the rotor and the motion laws for the stator. The method sets the motion law for the rotor as a moving coordinate system motion and the motion law for the stator as a combination of moving coordinate system motion and grid motion. Under the condition that the physical laws remain unchanged, the displacement of the impeller machinery moving part in the calculation space during the sweeping process can be replaced on the impeller machinery static part, thereby ensuring that the numerical node coordinates of the impeller machinery moving part calculation domain do not change with the sweeping process, improving the post-processing accuracy for the impeller machinery moving part, facilitating the data transmission of the impeller machinery moving part and the docking with other solvers, and improving the applicability of the method.

[0050] Furthermore, the calculation domain of the impeller machinery dynamic parts and the calculation domain of the impeller machinery static parts in the simulation method provided by the present invention are both independent discrete domains, that is, the required discretization method of the dynamic and static calculation domains and the numerical solution within each time step are consistent with the traditional numerical calculation requirements, that is, after the traditional numerical calculation pre-processing, the impeller machinery flow simulation method provided by the present invention can be seamlessly integrated, and the numerical calculation has strong applicability and portability.

[0051] Furthermore, in the impeller machinery flow simulation calculation method provided by the present invention, the parameters of the boundary conditions are set in an absolutely stationary coordinate system, and there is no need to convert relative motion variables, and the overall numerical calculation amount is the same as the traditional calculation amount, that is, it maintains good computational versatility compared with the traditional dynamic-static interference numerical simulation, avoids the manual conversion of relative variables and possible errors, and does not add additional computational burden to the numerical solution.

[0052] The present invention also provides a turbomachinery flow simulation calculation system, comprising a calculation domain acquisition module, a rotor motion law assignment module, a stator motion law assignment module and a numerical calculation module. The system can realize the acquisition of the impeller machinery moving parts calculation domain and the impeller machinery static parts calculation domain, assign the motion law for the rotor to the impeller machinery moving parts calculation domain, assign the motion law for the stator to the impeller machinery static parts calculation domain, and perform the impeller machinery simulation numerical calculation process according to the motion law for the rotor and the motion law for the stator. The system has a simple structure and can be applied to the field of turbomachinery flow simulation calculation. The numerical calculation results are highly accurate and can meet the current requirements for calculation accuracy in the field of numerical research on turbomachinery flow with interlaced moving parts and stationary parts, such as aircraft engines, gas turbines and steam turbines. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] Figure 1 The figure is a flow chart of a turbomachinery flow simulation calculation method of the present invention.

[0054] Figure 2 An example of a three-dimensional impeller machine moving blade calculation domain and an impeller machine stationary blade calculation domain simulated using the impeller machine flow simulation calculation method provided by the present invention:

[0055] Figure 3 The figures are a comparison of the position changes of the calculation domain of the dynamic components of the turbomachinery and the calculation domain of the static components of the turbomachinery in the numerical calculation space under different calculation methods. Among them, a is the traditional dynamic coordinate system method; b is the traditional dynamic mesh method; c is the turbomachinery flow simulation calculation method of the present invention.

[0056] Figure 4 is the calculation range of the impeller machinery flow simulation calculation method of the present invention, wherein a is the two-dimensional calculation of the impeller machinery section rotational motion; b is the three-dimensional calculation of the impeller machinery rotational motion; c is the two-dimensional calculation of the impeller machinery section translational motion; d is the three-dimensional calculation of the impeller machinery upright blade translational motion.

[0057] Figure 5 This is a schematic diagram of an impeller machinery flow simulation calculation system of the present invention.

[0058] Among them, 1- impeller machinery static blade calculation domain, 2- impeller machinery static blade, 3- static and dynamic calculation domain interface, 4- impeller machinery moving blade calculation domain, 5- impeller machinery moving blade, 6- impeller machinery moving blade calculation domain after movement, 7- impeller machinery moving blade after movement, 8- impeller machinery stage static blade calculation domain after displacement movement, 9- impeller machinery stage static blade after displacement movement. DETAILED DESCRIPTION

[0059] To make the objectives, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions of the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings herein can be arranged and designed in various different configurations.

[0060] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention as claimed, but rather merely represents selected embodiments of the present invention. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without creative effort shall fall within the scope of protection of the present invention.

[0061] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined or explained in subsequent drawings.

[0062] In the description of the embodiments of the present invention, it should be noted that if the terms "upper," "lower," "horizontal," "inner," etc. appear, the orientation or positional relationship indicated is based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship in which the inventive product is typically placed when in use. These terms are merely for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or component referred to must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention. In addition, the terms "first," "second," etc. are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0063] In addition, if the term "horizontal" appears, it does not mean that the component must be absolutely horizontal, but can be slightly tilted. For example, "horizontal" only means that its direction is more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0064] In the description of the embodiments of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "disposed," "installed," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0065] The present invention will be further described in detail below with reference to specific embodiments, which are intended to explain the present invention rather than to limit it.

[0066] See also Figure 1 The present invention provides a turbomachinery flow simulation calculation method, comprising the following steps:

[0067] S1: Obtain a calculation domain of the impeller machinery moving parts and a calculation domain of the impeller machinery static parts, wherein the calculation domain of the impeller machinery moving parts and the calculation domain of the impeller machinery static parts are both independent discrete domains.

[0068] S2: Assign the motion law for the rotor to the calculation domain of the impeller machinery moving parts. The motion law for the rotor is the motion of the moving coordinate system. The specific operations are:

[0069] The motion law of the rotor is set as the motion of the moving coordinate system;

[0070] The dynamic coordinate system motion parameters are set for the dynamic coordinate system motion of the rotor. The dynamic coordinate system motion parameters include the rotation axis and rotation speed of the impeller mechanical moving parts or the equivalent translational motion direction and speed of the impeller mechanical moving parts. The specific method is as follows:

[0071] For rotational motion: make the rotation axis and rotation speed of the computational domain of the impeller machinery moving parts the same as the rotation axis and rotation speed of the impeller machinery moving parts under the actual research conditions, that is:

[0072]

[0073] Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the impeller machinery moving parts are made the same as the motion direction and linear velocity of the impeller machinery moving parts under the actual research conditions, that is:

[0074]

[0075] in, is the set angular velocity of the impeller mechanical moving parts, is the actual angular velocity of the impeller machine moving parts; The linear velocity of the coordinate system set for the equivalent impeller machine moving parts, is the true linear velocity of the impeller mechanical moving parts.

[0076] S3: Assign the motion law for the stator to the computational domain of the impeller machine static component. The motion law for the stator is a combination of the motion of the moving coordinate system and the motion of the grid. The specific operations are as follows:

[0077] The motion law of the stator is set as a motion that combines the motion of the moving coordinate system and the motion of the moving grid; wherein the motion parameters set for the moving coordinate system of the stator include the rotation axis and rotation speed of the motion of the moving coordinate system of the static component calculation domain or the equivalent translation motion direction and speed; the parameters set for the dynamic grid motion of the stator include the rotation axis and rotation speed of the motion of the dynamic grid of the static component calculation domain or the equivalent translation motion direction and speed;

[0078] Set the moving coordinate system motion parameters for the moving coordinate system motion of the stator. The specific operations are as follows:

[0079] For rotational motion: make the rotation axis and rotation speed of the computational domain of the static parts of the impeller machinery the same as the rotation axis and rotation speed of the dynamic parts of the impeller machinery under the actual research conditions, that is:

[0080]

[0081] Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the impeller machinery moving parts are made the same as the motion direction and linear velocity of the impeller machinery moving parts under the actual research conditions, that is:

[0082]

[0083] in, is the angular velocity of the stator calculation domain coordinate system, is the linear velocity of the stator in the calculation domain coordinate system.

[0084] Set the dynamic mesh motion parameters for the static mesh motion. The specific operations are as follows:

[0085] For rotational motion: the rotation axis of the computational domain mesh assigned to the stationary part of the impeller machinery is made the same as the rotation axis of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, and the rotation speed of the computational domain mesh of the stationary part is opposite to the rotation speed of the dynamic part of the impeller machinery under the actual research working conditions, that is:

[0086]

[0087] Or for equivalent translational motion, the translational motion velocity of the static components of the impeller machinery in the computational domain is made opposite to the equivalent translational motion velocity of the dynamic components of the impeller machinery under the actual research conditions, that is:

[0088]

[0089] The final momentum equation of the computational domain of the impeller machinery static parts after simultaneously assigning the motion law in the rotating coordinate system and the grid motion law is:

[0090]

[0091] Where ρ is the fluid density, is the composite velocity of the working fluid under the two motion laws, t is time, p is pressure, is the shear force, To strengthen your physical strength.

[0092] By setting the parameters of the turbine-stage stator fluid computational domain in this step, the displacement of the impeller machinery's moving components within the computational space during the sweep process is displaced onto the impeller machinery's stationary components, while ensuring that the final physical quantities and computational format of the turbine-stage stator fluid computational domain are equal to those of the absolutely stationary computational domain.

[0093] S4: Perform numerical calculations for turbomachinery simulation based on the motion laws of the rotor and the stator.

[0094] Take the flow simulation of the moving and stationary blades in the impeller machinery as an example, see Figure 2First, the impeller machine stationary blade calculation domain 1 of the impeller machine stationary blade 2 and the impeller machine moving blade calculation domain 4 of the impeller machine moving blade 5 are obtained. The static-dynamic calculation domain interface 3 is located between the impeller machine stationary blade 2 and the impeller machine moving blade 5. The impeller machine stationary blade calculation domain 1 and the impeller machine moving blade calculation domain 4 are two independent discrete domains with attributes assigned to them respectively.

[0095] The calculation domain 4 of the impeller machine moving blade is given a coordinate system rotation motion law, the rotation axis is set to the Z axis, the direction is the negative direction of the Z axis, the speed value is the speed of the impeller machine rotor under the study working condition, and the dynamic coordinate system motion parameters of the rotor are set using formulas (1)-(2).

[0096] The motion law for the stator is assigned to the impeller mechanical stator blade calculation domain 1. The motion law for the stator is a combination of the dynamic coordinate system motion and the grid motion. The Z axis is set as the rotation axis, the direction is the negative direction of the Z axis, the speed value is the speed of the impeller mechanical rotor under the research working condition, and the motion parameters are consistent with the parameters of the impeller mechanical moving blade calculation domain 4. The dynamic coordinate system motion parameters of the stator are set using formulas (3)-(4); the dynamic grid motion parameters of the stator are set using formulas (5)-(7); finally, the impeller mechanical simulation numerical calculation is performed according to the motion law for the rotor and the motion law for the stator.

[0097] The formats of the physical quantities and equations are consistent with the computational domain of coordinate-free and mesh-free motion. That is, the physical laws in the computational domain of the stationary components after applying two motion modes simultaneously in this process are consistent with the actual situation.

[0098] See also Figure 3 and Figure 4 Compared with traditional methods, the impeller machinery flow simulation method provided by the present invention has obvious advantages. In the traditional moving coordinate system method / frozen rotor method (frame motion, moving frame, frozen rotor), a moving coordinate system is imposed on the moving blade calculation domain to simulate the flow of fluid in the high-speed rotating moving blade cascade. However, in actual calculations, the coordinate system movement does not affect the position of the calculation domain in the numerical calculation space. Therefore, at different times, the relative position of the impeller machinery moving blade calculation domain 4 and the impeller machinery stationary blade calculation domain 1 and their respective coordinates in space remain unchanged. This makes it impossible to simulate the relative motion process of the moving blade sweeping over the stationary blade in numerical calculations.

[0099] In traditional mesh motion / sliding mesh methods, a mesh motion is applied to the impeller blade computational domain 4 to simulate the high-speed rotation of the impeller blade 5 and the flow within the impeller blade cascade. Over time, the impeller blade 5 and its computational domain rotate from their original spatial position about the negative z-axis to their new positions, namely the positions of the impeller blade computational domain 6 and the impeller blade 7 after the motion. This allows for the blade sweep process, but the node coordinates of the impeller blade computational domain change, hindering observation and post-processing of the blade and resulting in low accuracy.

[0100] See also Figure 3 c and Figure 4 In the impeller flow simulation calculation method provided by the present invention, the impeller blades 2 and the impeller blade calculation domain 1 are simultaneously subjected to coordinate system motion and reverse grid motion. Here, only the grid motion can represent the position change of the calculation domain in the numerical calculation space. Therefore, as time progresses during the calculation process, the impeller blades 2 and the impeller blade calculation domain 1 rotate around the positive direction of the z-axis in the opposite direction to the actual impeller blade motion. After a period of time, the positions of the impeller blade calculation domain 8 and the impeller blade calculation domain 9 after the displacement motion are updated. However, since only the coordinate system motion is applied to the impeller blades 5 and the impeller blade calculation domain 4, the coordinate system motion does not affect the position of the calculation domain in the numerical calculation space. Therefore, the impeller blades 5 and the impeller blade calculation domain 4 remain stationary in space. Therefore, the interweaving process of the moving and stationary blades is realized, and the spatial discrete point coordinates of the moving blades and their calculation domains remain unchanged, which facilitates data observation and exchange.

[0101] Finally, according to traditional turbomachinery numerical calculation methods, the corresponding boundary conditions and parameters such as the working fluid and material properties are set. The inlet parameters of the stationary components are those in the absolute stationary coordinate system, and the initial field is imported. The time step and number of steps are set, and the conventional numerical calculation begins. At this time, the coordinates of the grid nodes in the calculation domain of the moving blades will not change within the numerical calculation space. The calculation results can be output according to the corresponding coordinates, or data can be connected with other solvers for data exchange, and further research on the moving blades can be carried out to complete the numerical calculation of the turbomachinery simulation.

[0102] See also Figure 5 The present invention also provides a turbomachinery flow simulation calculation system, comprising:

[0103] Computational domain acquisition module: used to obtain the computational domain of the impeller machinery dynamic components and the computational domain of the impeller machinery static components;

[0104] Rotor motion law assignment module: Assigns the motion law for the rotor to the calculation domain of the impeller machinery moving parts. The motion law for the rotor is the motion of the moving coordinate system.

[0105] Stator motion law assignment module: Assigns the motion law for the stator to the computational domain of the impeller machinery static components. The motion law for the stator is a combination of the motion of the moving coordinate system and the grid motion.

[0106] Numerical calculation module: performs numerical calculations for turbomachinery simulation based on the motion laws of the rotor and the stator.

[0107] The system has a simple structure and can be applied to the field of turbomachinery flow simulation calculation. The numerical calculation results are highly accurate and can meet the current requirements for calculation accuracy in the field of numerical research on turbomachinery flow with interlaced moving and stationary parts, such as aircraft engines, gas turbines and steam turbines.

[0108] The above description is merely a preferred embodiment of the present invention and is not intended to impose any limitation on the technical solution of the present invention. Those skilled in the art should understand that, without departing from the spirit and principles of the present invention, the technical solution can also be subjected to several simple modifications and replacements, and these modifications and replacements are also within the scope of protection covered by the claims.

Claims

1. A turbomachinery flow simulation calculation method, characterized in that: The following steps are involved: Obtain the computational domain of the impeller machinery dynamic components and the computational domain of the impeller machinery static components; Assigning a motion law for the rotor to the calculation domain of the impeller machinery moving parts, wherein the motion law for the rotor is a motion of a moving coordinate system; The motion law for the stator is assigned to the computational domain of the static components of the turbomachinery. The motion law for the stator is a combination of the motion of the moving coordinate system and the motion of the grid, specifically: The motion law for the stator is set as a motion combining the motion of the moving coordinate system and the motion of the moving grid; The moving coordinate system motion parameters are set for the moving coordinate system motion of the stator as follows: For rotational motion: the rotation axis and rotation speed of the computational domain of the static parts of the impeller machinery are made the same as the rotation axis and rotation speed of the dynamic parts of the impeller machinery under the actual research conditions, that is: Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the static components of the turbomachinery are made the same as the motion direction and linear velocity of the dynamic components of the turbomachinery under the actual research conditions, that is: The dynamic mesh motion parameters are set for the dynamic mesh motion of the stator as follows: For rotational motion: the rotation axis of the computational domain mesh assigned to the static part of the impeller machinery is made the same as the rotation axis of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, and the rotation speed of the computational domain mesh of the static part is opposite to the rotation speed of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, that is: Or for equivalent translational motion, the translational motion velocity of the static components of the impeller machinery in the computational domain is made opposite to the equivalent translational motion velocity of the dynamic components of the impeller machinery under the actual research conditions, that is: The final momentum equation of the calculation domain of the static parts of the impeller machinery after simultaneously assigning the motion law in the moving coordinate system and the grid motion law is: in, The angular velocity of the static component calculation domain coordinate system is: Calculate the linear velocity of the domain coordinate system for the static component; is the fluid density, is the composite velocity of the working fluid under the two motion laws, t For time, p is the pressure, is the shear force, To strengthen the body; The angular velocity of the domain mesh rotation is calculated for the static component, is the actual angular velocity of the impeller machine moving parts; is the linear velocity of the translation motion of the computational domain mesh of the equivalent impeller machinery static component, is the true linear velocity of the impeller mechanical moving parts; Numerical calculations of turbomachinery simulation are performed based on the motion laws of the rotor and the stator.

2. The impeller machinery flow simulation calculation method according to claim 1, characterized in that: The calculation domain of the impeller machinery dynamic parts and the calculation domain of the impeller machinery static parts are both independent discrete domains.

3. The impeller machinery flow simulation calculation method according to claim 1, characterized in that: The specific operations for assigning the motion law of the rotor to the computational domain of the impeller machinery moving parts are as follows: The motion law of the rotor is set as the motion of the moving coordinate system; The moving coordinate system motion parameters are set for the moving coordinate system motion of the rotor.

4. The impeller machinery flow simulation calculation method according to claim 3, characterized in that: The motion parameters of the dynamic coordinate system include the rotation axis and rotation speed of the calculation domain of the impeller machinery moving part or the equivalent translation motion direction and speed of the calculation domain of the impeller machinery moving part.

5. The impeller machinery flow simulation calculation method according to claim 3, characterized in that: The method for setting the motion parameters of the moving coordinate system is: For rotational motion: make the rotation axis and rotation speed of the computational domain of the impeller machinery moving parts the same as the rotation axis and rotation speed of the impeller machinery moving parts under the actual research conditions, that is: Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the impeller machinery moving parts are made the same as the motion direction and linear velocity of the impeller machinery moving parts under the actual research conditions, that is: in, is the set angular velocity of the impeller mechanical moving parts, is the actual angular velocity of the impeller machine moving parts; The linear velocity of the coordinate system set for the equivalent impeller machine moving parts, is the true linear velocity of the impeller mechanical moving parts.

6. The turbomachinery flow simulation calculation method according to claim 1, characterized in that: The motion parameters set for the dynamic coordinate system of the stator include the rotation axis and rotation speed of the dynamic coordinate system of the static component calculation domain or the equivalent translation motion direction and speed; the parameters set for the dynamic mesh motion of the stator include the rotation axis and rotation speed of the dynamic mesh motion of the static component calculation domain or the equivalent translation motion direction and speed.

7. A turbomachinery flow simulation calculation system, characterized in that: include: Computational domain acquisition module: used to obtain the computational domain of the impeller machinery dynamic components and the computational domain of the impeller machinery static components; Rotor motion law assignment module: used to assign the motion law for the rotor to the calculation domain of the impeller machinery moving parts. The motion law for the rotor is the motion of the moving coordinate system. Stator motion law assignment module: used to assign the stator motion law to the computational domain of the impeller machinery static components. The stator motion law is a combination of the moving coordinate system motion and the grid motion, specifically: The motion law for the stator is set as a motion combining the motion of the moving coordinate system and the motion of the moving grid; The moving coordinate system motion parameters are set for the moving coordinate system motion of the stator as follows: For rotational motion: the rotation axis and rotation speed of the computational domain of the static parts of the impeller machinery are made the same as the rotation axis and rotation speed of the dynamic parts of the impeller machinery under the actual research conditions, that is: Or for equivalent translational motion, the translational motion direction and velocity assigned to the computational domain of the static components of the turbomachinery are made the same as the motion direction and linear velocity of the dynamic components of the turbomachinery under the actual research conditions, that is: The dynamic mesh motion parameters are set for the dynamic mesh motion of the stator as follows: For rotational motion: the rotation axis of the computational domain mesh assigned to the static part of the impeller machinery is made the same as the rotation axis of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, and the rotation speed of the computational domain mesh of the static part is opposite to the rotation speed of the rotational motion of the dynamic part of the impeller machinery under the actual research working conditions, that is: Or for equivalent translational motion, the translational motion velocity of the static components of the impeller machinery in the computational domain is made opposite to the equivalent translational motion velocity of the dynamic components of the impeller machinery under the actual research conditions, that is: The final momentum equation of the calculation domain of the static parts of the impeller machinery after simultaneously assigning the motion law in the moving coordinate system and the grid motion law is: in, The angular velocity of the static component calculation domain coordinate system is: Calculate the linear velocity of the domain coordinate system for the static component; is the fluid density, is the composite velocity of the working fluid under the two motion laws, t For time, p is the pressure, is the shear force, To strengthen the body; The angular velocity of the domain mesh rotation is calculated for the static component, is the actual angular velocity of the impeller machine moving parts; is the linear velocity of the translation motion of the computational domain mesh of the equivalent impeller machinery static component, is the true linear velocity of the impeller mechanical moving parts; Numerical calculation module: used to perform numerical calculations of impeller machinery simulation based on the motion laws of the rotor and the motion laws of the stator.

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