CN114218818B - Design method of heat exchange compression device - Google Patents
Design method of heat exchange compression device Download PDFInfo
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- CN114218818B CN114218818B CN202111351666.8A CN202111351666A CN114218818B CN 114218818 B CN114218818 B CN 114218818B CN 202111351666 A CN202111351666 A CN 202111351666A CN 114218818 B CN114218818 B CN 114218818B
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- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
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Abstract
The invention relates to a design method of a heat exchange compression device, which comprises the steps of S1, determining the shape of a blade through a given pneumatic parameter of the blade and through a basic flow equation and a flow equation, S2, carrying out simulation calculation on an impeller shaft system through dynamics simulation software to design the impeller shaft system, S3, designing a sealing assembly through establishing a three-dimensional model of the sealing assembly, S4, establishing a dynamics model of the impeller shaft, and analyzing dynamics response of a volute under the action of load. The heat exchange compression device designed by the method can realize high efficiency and energy saving, and the temperature crossing is higher as the energy efficiency is smaller. The space occupation rate and the weight of the heat exchange compression device are reduced, and the adverse effect of a high-temperature environment on heating devices is overcome.
Description
Technical Field
The invention belongs to the field of mechanical engineering, and particularly relates to a design method of a heat exchange compression device.
Background
Aiming at the outstanding heat control demands of high-power heat transmission and dissipation of future nuclear power spacecrafts, lunar bases, laser weapons, high-power antennas, microwave loads and the like, the compressor research is developed, the demands of upgrading and updating the future heat control system are met, and technical support is provided for product autonomy in the aerospace heat control system. The compressor consumes input work and transfers low-level source heat to high-level heat sources. In the prior art, the heat exchange compression device has the defects of high energy consumption, heavy weight, high space occupation rate and the like.
Disclosure of Invention
The invention aims to solve the problems and provide a design method of a heat exchange compression device, the heat exchange compression device comprises a volute, a cylinder, an impeller, blades and an impeller shafting, wherein the impeller shafting comprises an impeller shaft, a sealing assembly and a bearing, the volute is connected with the cylinder, the impeller is arranged in the volute and integrally processed with the impeller shaft, the blades are arranged on the impeller, the sealing assembly and the bearing are arranged in the cylinder and are sequentially arranged on the impeller shaft along the direction far away from the impeller, and the design method comprises the following steps:
S1, determining the shape of the blade through a given aerodynamic parameter of the blade and a flow continuous equation;
S2, simulating calculation is carried out on the impeller shaft system through dynamics simulation software, and the impeller shaft system is designed;
s3, designing the sealing assembly by establishing a three-dimensional model of the sealing assembly;
s4, establishing a dynamic model of the impeller shaft, and analyzing dynamic response of the volute under the action of load.
According to one aspect of the present invention, in the step S1, the blade designing method includes:
A) Firstly, establishing a ternary flow calculation model through a continuity equation, a motion equation, an energy equation and a state equation;
b) Then, a streamline curvature method is adopted, according to the assumed streamline shape, the streamline curvature and the slope are adopted as parameters, a normal or quasi-normal velocity gradient equation along the streamline is integrated along the gas through flow section, and a new streamline shape is obtained according to a flow equation;
C) Repeating the iteration until a convergence solution is obtained, and obtaining the shape of the blade;
d) Finally, the shape of the blade is finally determined through three-dimensional CFD numerical analysis.
According to one aspect of the invention, in the step a), the impeller flow calculation model is constructed according to the theoretical work W th performed by the impeller on the unit mass of gas:
Wth＝c2uu2-c1uu1
Where c 2u is the radial component speed (m/s) of the impeller blade outlet absolute speed c 2, u 2 is the impeller blade outlet linear speed (m/s), c 1u is the radial component speed (m/s) of the impeller blade outlet absolute speed c 1, and u 1 is the impeller blade inlet linear speed (m/s).
According to one aspect of the present invention, in the step B), the flow equation is:
Wherein d m is the flow mass passing through the unit time d t, q m is the mass flow (kg/s) and the energy equation
Wtot＝Wth+hL+hdf
Where W tot is the total power consumption (J/kg) of the impeller on the unit mass of gas, h L is the internal leakage loss (J/kg), and h df is the wheel drag loss (J/kg).
According to one aspect of the present invention, in the step S3, the method for designing the seal assembly includes:
a) Firstly, establishing a three-dimensional model of a sealing assembly, defining boundary conditions, and carrying out dry film contact analysis on the sealing assembly;
b) Analyzing factors affecting the sealing performance of the seal assembly;
C) Then analyzing the contact stress distribution of the sealing assembly in the idle state and the loading state, determining the initial contact stress of the sealing assembly by using a specific pressure criterion, and constructing reasonable geometric parameters;
d) And (5) completing the design of the sealing assembly.
According to one aspect of the invention, the sealing assembly comprises a sealing framework and a sealing member, wherein a groove is formed in the sealing framework, the sealing framework is connected with the cylinder body, one end of the sealing member is installed in the groove and tightly fits the shape of the groove, and the other end of the sealing member is tightly attached to the impeller shaft.
According to one aspect of the invention, the seal is polytetrafluoroethylene or high molecular weight polyethylene.
According to one aspect of the invention, in the step S4, the method for analyzing the dynamic response of the volute under load is as follows:
A) Firstly, establishing a dynamic model of the impeller shaft;
B) Carrying out finite element model analysis on the impeller and the volute by utilizing a finite element method and a multi-body dynamics theory to obtain the inherent frequency, the vibration mode and other modal characteristic parameters of the impeller shaft and the volute;
c) The relevant parameters such as gas force load, main and auxiliary bearing load born by the volute are obtained through multi-body dynamics analysis of the impeller shaft;
D) And finally, completing dynamic response analysis of the volute under the load.
The heat exchange compression device designed by the method can realize high efficiency and energy conservation, the higher the temperature crossing small energy efficiency is, the space occupation rate and the weight of the heat exchange compression device are reduced, and the adverse effect of a high-temperature environment on heating devices is overcome.
Drawings
FIG. 1 schematically illustrates a cross-sectional view of the heat exchange compression device;
Fig. 2 schematically shows a perspective view of the volute;
FIG. 3 schematically illustrates a cross-sectional view of the volute;
FIG. 4 schematically illustrates a perspective view of an impeller and blades;
fig. 5 schematically shows a block diagram of the seal assembly.
Detailed Description
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required to be used in the embodiments will be briefly described below. It is apparent that the drawings in the following description are only some embodiments of the present invention, and that other drawings may be obtained from these drawings without inventive effort for a person of ordinary skill in the art.
In describing embodiments of the present invention, the terms "longitudinal," "transverse," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer" and the like are used in terms of orientation or positional relationship based on that shown in the drawings, which are merely for convenience of description and to simplify the description, rather than to indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operate in a specific orientation, and thus the above terms should not be construed as limiting the present invention.
The present invention will be described in detail below with reference to the drawings and the specific embodiments, which are not described in detail herein, but the embodiments of the present invention are not limited to the following embodiments.
Referring to fig. 1 to 4, the present invention provides a design method of a heat exchange compression device, which includes a volute 1, a cylinder 2, an impeller 3, blades 31 and an impeller shaft 4, wherein the volute 1 is connected with the cylinder 2, the impeller 3 is disposed in the volute 1, the blades 31 are disposed on the outer surface of the impeller 3, and the impeller shaft 4 is disposed in the cylinder 2. The impeller shaft system 4 includes an impeller shaft 41, a seal assembly 42, and a bearing 43, the seal assembly 42 and the bearing 43 being disposed in sequence between the impeller shaft 41 and the inner wall of the cylinder 2 in a direction away from the impeller 3. Wherein the impeller 3 is integrally processed with the impeller shaft 41. According to the concept of the invention, the impeller 3 and the impeller shaft 41 are integrally processed, so that the phenomenon that the impeller 3 and the impeller shaft 41 are loosened under high-speed rotation is avoided. Meanwhile, the axial length of the whole device is reduced, and the miniaturization of products is realized. The heat exchange compression device adopts a centrifugal impeller structure to realize temperature rise and compression of refrigerant, the refrigerant vapor firstly enters a suction chamber in front of an impeller inlet and then enters an impeller 3, and under the action of a blade 31, gas rotates at a high speed along with the impeller 3 and flows in a diffusion way in a channel of the blade 3 under the action of centrifugal force, so that the pressure and the speed of the gas are both improved.
In the present embodiment, the shape of the blade 31 is determined by the aerodynamic parameters of the blade given, and by the basic flow equation and the flow equation. According to the concept of the present invention, the gas is diffused in the vane channel by the centrifugal force while rotating at a high speed along with the impeller 3 by the vane 31, so that the shape of the vane 31 greatly affects the flow of the gas, and the pressure and speed of the gas can be greatly improved by determining the shape of the vane 31 by the above equation. In this embodiment, the dynamic simulation software is used to perform simulation calculation on the impeller shaft system 4 to guide the design of the impeller shaft system. According to the conception of the invention, when the device runs, the end face of the impeller 3 is in air inlet, and the impeller shaft is in a cantilever state, so that the load dynamics simulation analysis is carried out on the impeller shaft system 4, the position relation between the bearing supporting rigidity and the supporting point can be calculated, the design of the impeller shaft system 4 is further guided, the layout of the heat exchange compression device is more reasonable, and the service life is prolonged. In this embodiment, the design of the seal assembly 42 is accomplished by creating a three-dimensional model of the seal assembly 42. According to the concept of the invention, by establishing a three-dimensional model, reasonable geometric parameters can be established through simulation, such as the elastic modulus of the sealing assembly 42, the interference (initial compression amount) of the sealing assembly 42, the contact width, the temperature, the friction heat and other data can be precisely controlled, so that the sealing effect of the sealing assembly 42 can be further improved. In this embodiment, a dynamic model of the impeller shaft is built and the dynamic response of the volute under load is analyzed. According to the conception of the invention, the flow loss of the gas at the outlets of the impeller and the diffuser is reduced, and the efficiency of the whole machine is improved.
According to the design method of the heat exchange compression device, impeller basic size parameters are calculated in an iterative mode according to a basic flow continuity equation and an energy equation, impeller outlet structure parameters are calculated, the obtained parameters are returned to the iteration mode, and the impeller structure is further optimized until an optimal solution is obtained. By the design method, the actual work of the impeller on the unit mass gas is improved, and the efficiency of the whole machine is improved.
According to the design method of the heat exchange compression device, a three-dimensional model of a sealing structure is firstly established, boundary conditions (the maximum contact stress sigma p of the sealing component is larger than or equal to the medium pressure p) are defined, dry film contact analysis is carried out on the sealing component 42, simulation analysis is mainly carried out on the contact stress, and the contact stress in the compression state of the sealing component is analyzed. Factors affecting sealing performance, such as modulus of elasticity of the material, interference of the seal assembly 42 (initial amount of compression), contact width, temperature, frictional heat, etc., are analyzed for contact stress distribution of the seal assembly in the unloaded and loaded states. The specific pressure criteria are used to determine the initial contact stress of the seal assembly 42 and to construct reasonable geometric parameters. According to the conception of the invention, through the design method, the selection of the materials of the sealing assembly 42 and the design of the structure are further determined by considering various factors influencing the sealing, so that reworking is prevented, the cost is saved, and the sealing performance of the sealing structure is further improved.
Referring to fig. 5, according to an embodiment of the present invention, the seal assembly 42 includes a seal frame 44 and a seal 45, and the seal frame 42 is coupled to the cylinder 2. In this embodiment, one end of the seal 45 is connected to the inside of the groove of the seal frame 44, and closely fits the shape of the groove, and the other end closely fits the impeller shaft. According to the conception of the invention, the mixed lubrication flow state is constructed, the sealing life is prolonged and the fault-free working time of the whole machine is improved on the basis of ensuring reliable sealing.
As shown in fig. 5, in the present embodiment, the sealing material 45 is polytetrafluoroethylene or high-molecular polyethylene. According to the conception of the invention, polytetrafluoroethylene or high-molecular polyethylene has strong high and low temperature resistance, excellent chemical stability and electrical insulation property, can ensure that the sealing element 45 cannot be damaged in a special use environment, improves the sealing performance, has low price, and reduces the manufacturing cost of the heat exchange compression device.
The above description is only one embodiment of the present invention and is not intended to limit the present invention, and various modifications and variations of the present invention will be apparent to those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (6)
1. The design method of the heat exchange compression device is characterized by comprising a volute (1), a cylinder body (2), an impeller (3), blades (31) and an impeller shaft system (4), wherein the impeller shaft system (4) comprises an impeller shaft (41), a sealing assembly (42) and a bearing (43), the volute (1) is connected with the cylinder body (2), the impeller (3) is arranged in the volute (1) and integrally processed with the impeller shaft (41), the blades (31) are arranged on the impeller (3), the sealing assembly (42) and the bearing (43) are arranged in the cylinder body and are sequentially arranged on the impeller shaft (41) along the direction far away from the impeller, and the design method comprises the following steps:
S1, determining the shape of the blade (31) through a given aerodynamic parameter of the blade (31) and a flow continuous equation, wherein the blade (31) is designed by the following steps:
A) Constructing and establishing the impeller flow calculation model according to the theoretical work W th of the impeller on the unit mass gas;
b) Then, a streamline curvature method is adopted, according to the assumed streamline shape, the streamline curvature and the slope are adopted as parameters, a normal or quasi-normal velocity gradient equation along the streamline is integrated along the gas through flow section, and a new streamline shape is obtained according to a flow equation;
c) Repeating the iteration in this way until a converging solution is obtained, obtaining the shape of the blade (31);
d) Finally determining the shape of the blade (31) by means of a three-dimensional CFD numerical analysis;
S2, performing simulation calculation on the impeller shaft system (4) through dynamics simulation software, and designing the impeller shaft system (4);
S3, designing the sealing assembly (42) by establishing a three-dimensional model of the sealing assembly (42), wherein the design method of the sealing assembly (42) comprises the following steps:
a) Firstly, establishing a three-dimensional model of a sealing assembly (42), defining boundary conditions, and carrying out dry film contact analysis on the sealing assembly (42);
b) -analysing factors affecting the sealing performance of the sealing assembly (42);
C) Then analyzing the contact stress distribution of the seal assembly (42) in the unloaded and loaded state, determining the initial contact stress of the seal assembly using specific pressure criteria, and constructing reasonable geometric parameters;
d) Completing the design of the seal assembly (42);
s4, establishing a dynamic model of the impeller shaft (41), and analyzing dynamic response of the volute (1) under the action of load.
2. The design method according to claim 1, wherein in the step a) of the step S1, the impeller flow calculation model is constructed according to theoretical work Wth performed by the impeller on a unit mass of gas:
Wth＝c2uu2-c1uu1
Wherein c 2u is the radial component speed of the absolute speed c 2 of the impeller blade outlet in m/s, u 2 is the linear speed of the impeller blade outlet in m/s, c 1u is the radial component speed of the absolute speed c 1 of the impeller blade outlet in m/s, and u 1 is the linear speed of the impeller blade inlet in m/s.
3. The design method as defined in claim 1, wherein in the step B) of the step S1,
The flow equation is:
Wherein d m is the mass of the flow passing through the unit time d t, and the energy equation is as follows:
Wtot＝Wth+hL+hdf
Wherein the unit of the mass flow q m is kg/s, the unit of W tot is J/kg of total power consumption of the impeller on unit mass of gas, the unit of h L is internal leakage loss, the unit of J/kg is loss of wheel resistance, and the unit of hdf is J/kg.
4. The design method according to claim 1, characterized in that the sealing assembly (42) comprises a sealing skeleton (44) and a sealing member (45), the sealing skeleton (44) is provided with a groove, the sealing skeleton (44) is connected with the cylinder body (2), one end of the sealing member (45) is installed in the groove and tightly fits the shape of the groove, and the other end is tightly fitted on the impeller shaft (41).
5. Design method according to claim 4, characterized in that the seal (45) is polytetrafluoroethylene or high molecular weight polyethylene.
6. Design method according to claim 1, characterized in that in said step S4, the method of analysing the dynamic response of the volute (1) under load is:
a) Firstly, establishing a dynamic model of the impeller shaft (41);
B) Carrying out finite element model concept analysis on the impeller (3) and the volute (1) by utilizing a finite element method and a multi-body dynamics theory to obtain natural frequency and vibration mode characteristic parameters of the impeller shaft (41) and the volute (1);
c) The gas force load and relevant parameters of the volute (1) bearing the main and auxiliary bearings are obtained through multi-body dynamics analysis of the impeller shaft (41);
D) Finally, the dynamic response analysis of the volute (1) under load is completed.
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| CN202111351666.8A CN114218818B (en) | 2021-11-16 | 2021-11-16 | Design method of heat exchange compression device |
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| CN202111351666.8A CN114218818B (en) | 2021-11-16 | 2021-11-16 | Design method of heat exchange compression device |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110705079A (en) * | 2019-09-25 | 2020-01-17 | 哈尔滨工程大学 | A Structural Optimization Method of Centrifugal Compressor Based on Simulated Annealing Algorithm |
| CN112128099A (en) * | 2019-06-25 | 2020-12-25 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP5495700B2 (en) * | 2009-10-07 | 2014-05-21 | 三菱重工業株式会社 | Centrifugal compressor impeller |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112128099A (en) * | 2019-06-25 | 2020-12-25 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN110705079A (en) * | 2019-09-25 | 2020-01-17 | 哈尔滨工程大学 | A Structural Optimization Method of Centrifugal Compressor Based on Simulated Annealing Algorithm |
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