An iterative approximation heat balance test method for heat test heat dissipation surface and heat pipe system

Abstract

The application discloses an iterative approximation thermal balance test method for a heat dissipation surface and a heat pipe system of a thermal test, and relates to the technical field of spaceflight. The application discloses an iterative approximation thermal balance test method for a heat dissipation surface and a heat pipe system of a thermal test, and relates to the technical field of spaceflight. When the heat dissipation surface-heat pipe system is used for the thermal test, a set of simulated heat pipes and the heat dissipation surface of the thermal test are arranged by removing the real heat pipe in the on-orbit original configuration, the thermal test configuration construction is completed, the heat transfer amount of the heat dissipation surface or the heat dissipation surface and the heat pipe, the heat dissipation amount of the heat dissipation surface or the heat dissipation surface and the environment, and the heat exchange amount of the heat dissipation surface and other structures are accurately obtained through several test iterations of the double parameters of different heat dissipation plates during the thermal test, and the accurate thermal boundary conditions are determined, so that the problem of insufficient verification of the thermal test is solved, and the reliability of the thermal design of a spacecraft can be effectively improved.

Description

TECHNICAL FIELD

[0001] The present application relates to an iterative approximation heat balance test method for a heat test heat dissipation surface and a heat pipe system, and belongs to the technical field of spacecraft thermal control. BACKGROUND

[0002] Currently, the thermal control measures of spacecraft are increasingly complex. Many components are inside the spacecraft. To achieve heat dissipation of these internal components, independent heat dissipation surfaces are usually arranged outside the spacecraft. The surface state of the heat dissipation surface is generally a low solar absorption ratio / high emissivity material. A heat pipe is used to connect the component itself and the heat dissipation surface together to form a good heat conduction path. The arrangement of the heat dissipation surface-heat pipe system is shown in Figure 1

[0003] Generally, the correctness of the thermal design of the spacecraft needs to be verified by ground heat balance test. Unlike the state of the spacecraft in orbit, the ground test of the spacecraft is affected by gravity. When the height of the heat dissipation surface is lower than that of the heat generating component, the heat pipe connecting the two has the risk of not being able to start smoothly. According to the provisions of GB / T 34515-2017 "Spacecraft Heat Balance Test Method", the heat test configuration should ensure that the heat pipe is placed horizontally or can work normally. However, the height position relationship between the heat dissipation surface and the heat generating component is determined by the overall configuration of the spacecraft. As the configuration of the spacecraft becomes more complex, it is more and more difficult to consider the orientation of all heat pipes. If some heat pipes fail to start in the heat test, it will affect the effect of the heat balance test.

[0004] At the same time, when using the special heat test heat dissipation surface-heat pipe system, the traditional method is used to carry out the test, and the actual heat pipe heat transfer amount Q2, the equivalent value Q3' of the net heat exchange amount of the real heat dissipation surface and other parts in orbit cannot be obtained. Using the hypothetical value / simulation value to carry out the test will bring errors, and there is a lack of accurate method to obtain the two amounts. SUMMARY

[0005] The technical problem solved by the present application is that, in view of the various defects of the traditional heat balance test method in the prior art, an iterative approximation heat balance test method for a heat test heat dissipation surface and a heat pipe system is proposed.

[0006] The present application solves the above technical problem by the following technical scheme:

[0007] An iterative approximation heat balance test method for a heat test heat dissipation surface and a heat pipe system, comprising:

[0008] Manufacturing and assembling the heat test heat dissipation surface and the heat pipe system, setting an analog heat dissipation plate in the heat dissipation surface and the heat pipe system, and constructing a heat test configuration;

[0009] Performing thermal analysis on the analog heat dissipation plate and the real heat dissipation plate in the heat test configuration; ​

[0010] According to the thermal analysis results, an external heat flow is applied to the simulation heat sink and a preset equivalent peripheral heat transfer amount is given;

[0011] After measuring the temperature parameters of the simulation heat sink in the thermal equilibrium state, the heat dissipation amount of the simulation heat sink is calculated, and the current heat pipe heat transfer amount is calculated according to the heat dissipation amount;

[0012] The simulation heat sink is applied with the calculated heat pipe heat transfer amount and the theoretical external heat flow of the simulation heat sink, and after the real heat sink reaches the thermal equilibrium state, the temperature parameters of the real heat sink in the thermal equilibrium state are measured to calculate the heat dissipation amount of the real heat sink;

[0013] The net heat exchange amount equivalent value of the real heat dissipation surface is calculated according to the heat dissipation amount of the real heat sink;

[0014] The net heat exchange amount equivalent value of the real heat dissipation surface is applied to the simulation heat sink in the form of heat, and after the simulation heat sink reaches the thermal equilibrium state, the temperature parameters of the simulation heat sink are measured to calculate the heat dissipation amount of the simulation heat sink in the current thermal equilibrium state;

[0015] The current heat pipe heat transfer amount is calculated according to the heat dissipation amount of the simulation heat sink in the current thermal equilibrium state;

[0016] The temperature parameters of the simulation heat sink and the temperature parameters of the real heat sink are measured and compared, and whether the simulation heat sink and the real heat sink are equivalent is determined according to the comparison result, if the simulation heat sink and the real heat sink are equivalent, the test is ended and the current temperature parameters of the thermal test configuration are taken as the final temperature result of the thermal equilibrium test, otherwise the thermal test is continued;

[0017] The current heat pipe heat transfer amount is applied to the real heat sink, and after the thermal equilibrium state is reached, the temperature parameters of the real heat sink are measured and compared with the temperature parameters of the simulation heat sink, and whether the simulation heat sink and the real heat sink are equivalent is determined according to the comparison result, if the simulation heat sink and the real heat sink are equivalent, the test is ended and the current temperature parameters of the thermal test configuration are taken as the final temperature result of the thermal equilibrium test, otherwise the thermal test is continued;

[0018] The heat pipe heat transfer amount calculation of the simulation heat sink in the thermal equilibrium state and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer amount is applied are repeated until the simulation heat sink and the real heat sink are completely equivalent, and the current temperature parameters of the thermal test configuration are taken as the final temperature result of the thermal equilibrium test.

[0019] The method for thermal analysis of the simulation heat sink and the real heat sink is as follows:

[0020] For the thermal test configuration, a thermal balance equation is established for any component to determine the relationship between the heat dissipation and the external heat flow, the heat pipe heat transfer, and the net heat exchange with the heat dissipation surface; the external heat flow is simulated by external heating, and the net heat exchange with the heat dissipation surface is automatically generated after the temperature parameters of the heat dissipation surface are determined; the heat pipe heat transfer is determined according to the selected heat pipe simulation; the thermal test configuration has a heat leakage, and during the thermal test process, the sum of the heat dissipation and the heat leakage is equivalent to the sum of the external heat flow, the heat pipe heat transfer, and the net heat exchange with the heat dissipation surface.

[0021] The heat leakage is controlled by tracking the temperature control or heat insulation installation of the support structure of the thermal test configuration to achieve negligible heat leakage.

[0022] The heat dissipation of the simulated heat dissipation plate and the real heat dissipation plate is Q4 = ε r · ζ · (T - T back ) 4

[0023] In the formula, ε r is the infrared emissivity of the heat dissipation surface (known), ζ is the Boltzmann constant, T back is the background temperature, and T is the temperature of the heat dissipation surface B.

[0024] The external heat flow Q1 is the real external heat flow absorbed by the heat dissipation surface in orbit, which is independent of the temperature of the heat dissipation surface itself.

[0025] The heat pipe heat transfer Q2 is affected by the temperature difference of the heat pipe installation interface, and when the temperature of the device end is constant, the heat transfer is related to the temperature of the heat dissipation surface; when the temperature of the heat dissipation surface increases, the heat pipe heat transfer decreases, and the heat pipe heat transfer Q2 is monotonically decreasing with respect to the temperature of the heat dissipation surface.

[0026] The net heat exchange Q3 between the heat dissipation plate and the heat dissipation surface is monotonically decreasing with respect to the temperature of the heat dissipation surface.

[0027] After the heat dissipation conditions of any component of the thermal test configuration are consistent with the on-orbit state, a thermal equilibrium state is reached, wherein:

[0028] In the thermal equilibrium state, the measured temperature parameters of the simulated heat dissipation plate are the same as those of the real heat dissipation plate, the heat pipe heat transfer of the simulated heat dissipation plate is applied to the actual heat dissipation plate, and the net heat exchange with the heat dissipation surface of the other part of the real heat dissipation plate is applied to the simulated heat dissipation plate; for any heat dissipation plate, the heat dissipation is the sum of the external heat flow, the heat pipe heat transfer, and the net heat exchange with the heat dissipation surface.

[0029] The thermal equilibrium state of the simulated heat dissipation plate and the thermal equilibrium state of the real heat dissipation plate are achieved by adjusting the heat pipe heat transfer actively applied to the real heat dissipation plate and the net heat exchange with the heat dissipation surface actively applied to the simulated heat dissipation plate, and keeping the heat pipe heat transfer and the net heat exchange with the heat dissipation surface consistent with those in the corresponding another group of thermal equilibrium states.

[0030] The method for obtaining the heat pipe heat Q2 actively applied to the real heat sink and the net heat exchange Q3' of the heat sink surface actively applied to the simulated heat sink and the net heat exchange Q3' of the heat sink surface is as follows:

[0031] When the simulated heat sink A is in a thermal equilibrium state, Q3' = 0, the current heat pipe heat Q2' actively applied to the simulated heat sink is calculated, so that the real heat sink B enters a thermal equilibrium state.

[0032] The equivalent value Q3 of the net heat exchange of the real heat sink surface is calculated as the net heat exchange Q3' of the simulated heat sink surface applied to the simulated heat sink A, and after the simulated heat sink achieves a second thermal equilibrium, the current heat pipe heat Q2' in a new thermal equilibrium state is calculated.

[0033] The current heat pipe heat Q2' in the new thermal equilibrium state is applied to the real heat sink B to form a new thermal equilibrium state of the real heat sink B.

[0034] If the temperature parameter difference between the simulated heat sink A and the real heat sink B in the current state is outside the error allowable range, the latest equivalent value Q3 of the net heat exchange of the real heat sink surface is applied to the simulated heat sink A as a latest heat exchange equivalent value to establish a third thermal equilibrium state of the simulated heat sink, and the temperature parameter difference and the error allowable range are repeatedly judged to realize the optimization iteration between the equivalent value Q3 of the net heat exchange of the real heat sink surface and the net heat exchange Q3' of the simulated heat sink surface and the heat pipe heat Q2 and the heat pipe heat Q2', until the parameters of the thermal equilibrium state are completely consistent with the parameters in the on-orbit state.

[0035] The method for comparing the temperature parameters of the real heat sink measured after the thermal equilibrium with the temperature parameters of the simulated heat sink is as follows:

[0036] After the simulated heat sink achieves a second thermal equilibrium, the temperature parameters of the simulated heat sink and the temperature parameters of the real heat sink are measured, including the temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink, and the comparison relationship between |T1-T'2| and δ is judged, if |T1-T'2| > δ, the current heat pipe heat is applied to the real heat sink, and after the thermal equilibrium, the comparison judgment is continuously performed; if |T1-T'2| < δ, the simulated heat sink and the real heat sink are equivalent, the test is ended, and the current temperature parameters of the heat test configuration are taken as the final temperature results of the thermal equilibrium test.

[0037] The heat pipe heat transfer quantity is applied to the real heat dissipation plate, and when the real heat dissipation plate realizes thermal equilibrium for the second time, the temperature parameters of the real heat dissipation plate are measured and compared with the temperature parameters of the simulation heat dissipation plate, including comparison between the temperature T2 of the simulation heat dissipation plate and the temperature T'2 of the simulation heat dissipation plate, if |T2-T'2|<δ, the simulation heat dissipation plate and the real heat dissipation plate are equivalent, the test is ended and the current temperature parameters of the heat test configuration are taken as the final temperature results of the thermal equilibrium test; if |T2-T'2|>δ, the heat pipe heat transfer quantity calculation of the simulation heat dissipation plate under the thermal equilibrium state is repeated, the corresponding double-plate temperature parameter comparison after the heat pipe heat transfer quantity is applied is repeated, and the simulation heat dissipation plate and the real heat dissipation plate are completely equivalent until |T n-1 -T' n |<δ or |T n -T' n |<δ is obtained.

[0038] The comparison value δ is determined according to the accuracy requirement of the heat test; the heat test configuration has heat leakage, so that the temperature T'2 of the simulation heat dissipation plate and the temperature T1 of the real heat dissipation plate have differences, and the temperature T'2 of the simulation heat dissipation plate and the temperature T1 of the real heat dissipation plate are reduced by the heat leakage parameter to reduce the differences and the influence on the temperature parameter comparison.

[0039] Compared with the prior art, the present application has the following advantages:

[0040] (1) The heat test heat dissipation surface and the iterative approximation thermal equilibrium test method of the heat pipe system provided by the present application simulate the temperature boundary in orbit well by setting the heat pipe and the heat dissipation surface system special for heat test and developing iterative approximation test, solve the problems of heat test accuracy and effectiveness, and accurately simulate the thermal boundary of the component M to be tested in the thermal equilibrium test by obtaining the real heat pipe heat transfer quantity Q2 in the on-orbit state, the equivalent value Q3' of the real heat dissipation surface net heat exchange quantity and other parts in the on-orbit state.

[0041] (2) The heat test “heat dissipation surface-heat pipe system” is used in the present application, the heat transfer quantity of the heat dissipation plate / heat dissipation surface and the heat pipe, the heat dissipation quantity of the heat dissipation plate / heat dissipation surface and the environment, and the heat exchange quantity of the heat dissipation surface and other structures are accurately obtained through several times of test iteration, the accurate thermal boundary condition is determined, the problem of insufficient verification of the heat test is solved, and the reliability of the spacecraft thermal design can be effectively improved. BRIEF DESCRIPTION OF DRAWINGS

[0042] Figure 1 The present application provides a traditional configuration heat dissipation path schematic diagram;

[0043] Figure 2 The present application provides a real configuration to heat test configuration schematic diagram;

[0044] Figure 3The iterative approximation heat balance test method flow chart of the heat test heat dissipation surface and heat pipe system provided by the application;

[0045] Figure 4 The heat exchange schematic diagram of the real heat dissipation surface and the simulated heat dissipation plate with the outside provided by the application;

[0046] Figure 5 The real heat pipe trend and heat dissipation surface position schematic diagram of component K provided by the application;

[0047] Figure 6 The real heat pipe trend and heat dissipation surface position schematic diagram of component L provided by the application;

[0048] Figure 7 The heat test heat pipe trend and simulated heat dissipation plate position schematic diagram of component K provided by the application;

[0049] Figure 8 The heat test heat pipe trend and simulated heat dissipation plate position schematic diagram of component L provided by the application;

[0050] Figure 9 The temperature curve of different parts of component K in working condition one provided by the application;

[0051] Figure 10 The temperature curve of different parts of component L in working condition one provided by the application; DETAILED DESCRIPTION

[0052] The iterative approximation heat balance test method of the heat test heat dissipation surface and heat pipe system, when using the heat test special heat dissipation surface-heat pipe system, by removing the real heat pipe in the original configuration on the orbit, arranging a set of simulated heat pipe and heat dissipation surface for heat test, completing the heat test configuration construction, through several test iterations of different heat dissipation plate double parameters in the heat test process, accurately obtaining the heat transfer amount of the heat dissipation plate or heat dissipation surface and the heat pipe, the heat dissipation amount of the heat dissipation plate or heat dissipation surface and the environment, the heat exchange amount of the heat dissipation surface and other structures, determining the accurate thermal boundary conditions, solving the problem of insufficient verification of heat test, and effectively improving the reliability of spacecraft thermal design.

[0053] The iterative approximation heat balance test method of the heat test heat dissipation surface and heat pipe system, the specific steps are:

[0054] Manufacture and assemble the heat test heat dissipation surface and heat pipe system, set the simulated heat dissipation plate in the heat dissipation surface and heat pipe system, and construct the heat test configuration;

[0055] Perform thermal analysis on the simulated heat dissipation plate and the real heat dissipation plate in the heat test configuration;

[0056] According to the thermal analysis result, apply external heat flow to the simulated heat dissipation plate and give a preset equivalent peripheral heat transfer amount;

[0057] The temperature parameters of the simulation heat sink after measuring the heat balance are used to calculate the heat dissipation of the simulation heat sink, and the current heat pipe heat transfer is calculated according to the heat dissipation;

[0058] The heat pipe heat transfer of the calculated simulation heat sink and the theoretical external heat flow are applied to the real heat sink, and after the real heat sink reaches thermal equilibrium, the temperature parameters of the real heat sink after thermal equilibrium are measured to calculate the heat dissipation of the real heat sink;

[0059] The net heat exchange equivalent value of the real heat dissipation surface is calculated according to the heat dissipation of the real heat dissipation surface;

[0060] The net heat exchange equivalent value of the real heat dissipation surface is applied to the simulation heat sink in the form of heat, and when the simulation heat sink reaches thermal equilibrium, the temperature parameters of the simulation heat sink are measured to calculate the heat dissipation of the simulation heat sink at this time;

[0061] The current heat pipe heat transfer is calculated according to the heat dissipation of the simulation heat sink at this time;

[0062] The temperature parameters of the simulation heat sink are measured and compared with the temperature parameters of the real heat sink, and whether the simulation heat sink and the real heat sink are equivalent is judged according to the comparison result, if equivalent, the test is ended and the current temperature parameters of the heat test configuration are taken as the final temperature result of the heat balance test, otherwise the heat test is continued;

[0063] The current heat pipe heat transfer is applied to the real heat sink, and after thermal equilibrium, the temperature parameters of the real heat sink are measured and compared with the temperature parameters of the simulation heat sink, and whether the simulation heat sink and the real heat sink are equivalent is judged according to the comparison result, if equivalent, the test is ended and the current temperature parameters of the heat test configuration are taken as the final temperature result of the heat balance test, otherwise the heat test is continued;

[0064] The heat pipe heat transfer of the simulation heat sink under thermal equilibrium and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer is applied are repeated until the simulation heat sink and the real heat sink are completely equivalent, and the current temperature parameters of the heat test configuration are taken as the final temperature result of the heat balance test.

[0065] The method for thermal analysis of the simulation heat sink and the real heat sink is:

[0066] For the heat test configuration, the heat balance equation is established according to any component, the relationship between the heat dissipation and the external heat flow, the heat pipe heat transfer and the net heat exchange of the heat dissipation surface is determined; the external heat flow is simulated by external heating, and the net heat exchange of the heat dissipation surface is automatically generated after the temperature parameters of the heat dissipation surface are determined; the heat pipe heat transfer is determined according to the selected heat pipe simulation; the heat test configuration has a heat leakage, and during the heat test process, the sum of the heat dissipation and the heat leakage is equivalent to the sum of the external heat flow, the heat pipe heat transfer and the net heat exchange of the heat dissipation surface.

[0067] The heat leakage is controlled by tracking the temperature of the support structure of the thermal test configuration or by installing a thermal insulation to achieve negligible heat leakage.

[0068] The heat dissipation Q4 of the simulation heat sink and the real heat sink is: Q4 = ε r · ζ · (T - T back ) 4

[0069] In the formula, ε r is the infrared emissivity of the heat dissipation surface (known), ζ is the Boltzmann constant, T back is the background temperature, and T is the temperature of the heat dissipation surface B.

[0070] The external heat flow Q1 is the real external heat flow absorbed by the heat dissipation surface in orbit, which is independent of the temperature of the heat dissipation surface itself.

[0071] The heat pipe heat transfer Q2 is affected by the temperature difference of the heat pipe installation interface. When the temperature of the equipment end is constant, the heat transfer is related to the temperature of the heat dissipation surface. When the temperature of the heat dissipation surface increases, the heat pipe heat transfer decreases, and the heat pipe heat transfer Q2 is monotonically decreasing with respect to the temperature of the heat dissipation surface.

[0072] The net heat exchange Q3 between the heat sink and the heat dissipation surface is monotonically decreasing with respect to the temperature of the heat dissipation surface.

[0073] After the heat dissipation conditions of any component of the thermal test configuration are consistent with the on-orbit state, a thermal equilibrium state is reached, wherein:

[0074] In the thermal equilibrium state, the measured temperature parameters of the simulation heat sink are the same as those of the real heat sink, the heat pipe heat transfer of the simulation heat sink is applied to the real heat sink, the net heat exchange between the other parts and the heat dissipation surface of the real heat sink is applied to the simulation heat sink, and for any heat sink, the heat dissipation is the sum of the external heat flow, the heat pipe heat transfer, and the net heat exchange between the other parts and the heat dissipation surface.

[0075] The thermal equilibrium state of the simulation heat sink and the thermal equilibrium state of the real heat sink are achieved by adjusting the heat pipe heat transfer actively applied to the real heat sink and the net heat exchange with the heat dissipation surface actively applied to the simulation heat sink, and keeping the heat pipe heat transfer and the net heat exchange with the heat dissipation surface consistent with those in the other group of thermal equilibrium states.

[0076] The method for obtaining the heat pipe heat transfer Q2 actively applied to the real heat sink and the net heat exchange Q3' with the heat dissipation surface actively applied to the simulation heat sink is:

[0077] Let Q3' = 0, when the thermal equilibrium state of the simulation heat sink A, calculate the current heat pipe heat transfer Q2' actively applied to the simulation heat sink, so that the real heat sink B enters the thermal equilibrium state.

[0078] The equivalent value Q3 of the net heat exchange of the real heat dissipation surface is calculated as the net heat exchange Q3' of the simulation heat dissipation surface applied to the simulation heat dissipation plate A, and the current heat pipe heat transfer Q2' in the new thermal equilibrium state is calculated after the simulation heat dissipation plate realizes the second thermal equilibrium;

[0079] The current heat pipe heat transfer Q2' in the new thermal equilibrium state is applied to the real heat dissipation plate B to form a new thermal equilibrium state of the real heat dissipation surface B;

[0080] If the temperature parameter difference between the simulation heat dissipation plate A and the real heat dissipation plate B in the current state is outside the error allowable range, the latest equivalent value Q3 of the net heat exchange of the real heat dissipation surface of the real heat dissipation plate B is applied to the simulation heat dissipation plate A as the latest heat exchange equivalent value to establish the third thermal equilibrium state of the simulation heat dissipation plate, and the temperature parameter difference and the error allowable range are repeatedly judged to realize the optimization iteration between the equivalent value Q3 of the net heat exchange of the real heat dissipation surface and the net heat exchange Q3' of the simulation heat dissipation surface and the heat pipe heat transfer Q2 and the heat pipe heat transfer Q2' until the parameters of the thermal equilibrium state are completely consistent with the parameters in the on-orbit state.

[0081] After the thermal equilibrium, the temperature parameters of the real heat dissipation plate are measured and compared with the temperature parameters of the simulation heat dissipation plate in the following method:

[0082] After the second thermal equilibrium of the simulation heat dissipation plate is realized, the temperature parameters of the simulation heat dissipation plate and the temperature parameters of the real heat dissipation plate are measured, including the temperature T'2 of the simulation heat dissipation plate and the temperature T1 of the real heat dissipation plate, and the comparison relationship between |T1-T'2| and δ is judged. If |T1-T'2|>δ, the current heat pipe heat transfer is applied to the real heat dissipation plate, and the comparison judgment is continuously performed after the thermal equilibrium. If |T1-T'2|<δ, the simulation heat dissipation plate and the real heat dissipation plate are equivalent, the test is ended, and the current temperature parameters of the heat test configuration are taken as the final temperature results of the thermal equilibrium test.

[0083] The current heat pipe heat transfer is applied to the real heat dissipation plate, and after the real heat dissipation plate realizes the second thermal equilibrium, the temperature parameters of the real heat dissipation plate are measured and compared with the temperature parameters of the simulation heat dissipation plate, including the comparison between the temperature T2 of the simulation heat dissipation plate and the temperature T'2 of the simulation heat dissipation plate. If |T2-T'2|<δ, the simulation heat dissipation plate and the real heat dissipation plate are equivalent, the test is ended, and the current temperature parameters of the heat test configuration are taken as the final temperature results of the thermal equilibrium test. If |T2-T'2|>δ, the heat pipe heat transfer calculation of the simulation heat dissipation plate in the thermal equilibrium state and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer is applied are repeatedly performed until the simulation heat dissipation plate and the real heat dissipation plate are completely equivalent, that is, |T n-1 n n n .

[0084] ​​​The contrast value δ is determined according to the accuracy requirement of the thermal test; the thermal test configuration has heat leakage, which causes the difference between the temperature T'2 of the simulated heat dissipation panel and the temperature T1 of the real heat dissipation panel, and the temperature T'2 of the simulated heat dissipation panel and the temperature T1 of the real heat dissipation panel are reduced by the heat leakage parameter to reduce the difference and the influence on the temperature parameter contrast.

[0085] Further description is made below in combination with the drawings of the specification and the preferred embodiments:

[0086] In the current embodiment, the iterative approximation thermal balance test method of the heat dissipation surface and the heat pipe system of the thermal test, the arrangement of the heat surface-heat pipe system is as shown in Figure 1 , and in the new thermal test configuration as shown in Figure 2 , the in-orbit real heat pipe under the original configuration is removed, and the in-orbit real heat dissipation surface is usually directly arranged on the cabin body and cannot be removed; in order to achieve good heat dissipation, a set of simulated heat pipe and heat dissipation surface for thermal test is specially arranged;

[0087] For the component M to be cooled, its thermal balance equation is: the heat generation Q M,heat of the component M = the external radiation Q M,r of the component + the external heat transfer Q M,c1 of the component through the cabin + the external heat transfer Q M,c2 of the component through the heat pipe. In the thermal balance test, in order to ensure that the temperature level of the component M is consistent with that in orbit, the above three items need to be simulated.

[0088] The external radiation Q M,r of the component and the external heat transfer Q M,c1 of the component through the cabin depend on the temperature distribution of the cabin, and in terms of the actual situation of the thermal balance test, while the external heat flow of the cabin is normally simulated, the temperature level of the real heat dissipation surface remaining on the cabin should be consistent with that in orbit. For the real heat dissipation surface B of the outer surface of the original cabin panel (the heat dissipation surface is normally installed during the thermal test, but the heat pipe connected thereto has been removed), the heat balance condition of the surface is as shown in Figure 4 ;

[0089] The heat dissipation Q4 = the external heat flow Q1 + the heat pipe heat transfer Q2 + the net heat exchange Q3 between the other parts and the heat dissipation surface …… Equation ①

[0090] In the above equation: the external heat flow Q1 can be simulated by the infrared cage / infrared lamp / heater in the thermal test; the net heat exchange Q3 between the other parts and the heat dissipation surface is unknown, which is passively generated when the temperature level of the real heat dissipation surface B is determined; the heat pipe heat transfer Q2 is related to the capacity of the heat pipe, which needs to be simulated in the thermal test, but the amount is unknown. According to the traditional thermal test method, the test is directly carried out by using the pre-given Q2; but the traditional method cannot know the deviation degree of Q2 from the in-orbit, and cannot eliminate the boundary simulation error caused by the inaccurate Q2.

[0091] Heat transfer Q outwards by heat pipe M,c2 Depend on the consistency of heat pipe heat transfer link. When arranging heat test heat pipe-sink surface, the hardware connection relationship on the heat transfer link can be ensured to be consistent with the real product through the hardware design of the product. The root cause of affecting the heat dissipation capacity of the link is the temperature level of the heat test sink surface. The temperature level of the heat test sink surface should be consistent with that in orbit in the heat test. For the heat test simulation heat dissipation plate A, the heat balance of the plate is as shown in Figure 4 ;

[0092] Heat dissipation Q4' = external heat flow Q1' + heat pipe heat transfer Q2' + equivalent value of net heat exchange of other parts and real sink surface Q3' - heat leakage Q5' …… Equation ②

[0093] In equation ②, the heat leakage Q5' can be controlled to a negligible level through tracking temperature control, heat insulation installation, etc. After ignoring this item, the heat balance equation becomes:

[0094] Heat dissipation Q4' = external heat flow Q1' + heat pipe heat transfer Q2' + equivalent value of net heat exchange of other parts and real sink surface Q3' …… Equation ③

[0095] In equation ③, the heat flow Q1' can be simulated by an infrared cage / infrared lamp / heater in the heat test; the heat pipe heat transfer Q2' is unknown and is generated automatically when the temperature level of the simulation heat dissipation plate A is determined; the equivalent value of net heat exchange of other parts and real sink surface Q3' is used to simulate the thermal boundary of the in-orbit sink surface and is also unknown; the heat leakage Q5' can be controlled to a negligible level through tracking temperature control, heat insulation installation, etc. According to the traditional test method, the test is directly carried out by using the pre-given Q3'; however, the traditional method cannot know the deviation degree of Q3' from the in-orbit value and cannot eliminate the simulation error of the heat pipe heat transfer link caused by the inaccuracy of Q3'.

[0096] From the above analysis, when using the heat test special sink surface-heat pipe system, the test is carried out by using the traditional method, the real heat pipe heat transfer Q2 and the equivalent value of net heat exchange of other parts and real sink surface Q3' cannot be known, and the test is carried out by using the hypothetical value / simulation value, which will bring errors. If the real values of Q2 and Q3' can be accurately obtained, the accuracy of the heat balance test will be greatly improved.

[0097] For the original real sink surface B on the outer surface of the cabin plate, in the in-orbit state, there is:

[0098] Heat dissipation Q4 = external heat flow Q1 + heat pipe heat transfer Q2 + net heat exchange Q3 of other parts and sink surface …… Equation ①

[0099] Each term in equation ① will be analyzed as follows:

[0100] Left side first term: heat dissipation Q4 = ε r · ζ · (T - T back ) 4 , ε r - Infrared emissivity of the heat dissipation surface (known), ζ - Boltzmann constant, T back - Background temperature, T - Temperature of the heat dissipation surface B. T is generally below 100 K, and its effect on the test can be ignored. Therefore, Q4 can be considered as Q4 = ε r · ζ · T 4 ……Equation 4, which is monotonically increasing with respect to T.

[0101] Right side first term: external heat flow Q1, which represents the actual external heat flow absorbed by the heat dissipation surface B itself in orbit, and is independent of T.

[0102] Right side second term: heat pipe heat transfer Q2. For heat pipe heat transfer components, the effect of heat pipe installation interface temperature difference is considered. When the temperature of the hot end (device end temperature) is basically unchanged, the heat transfer is a function of the temperature of the cold end (heat dissipation surface temperature), i.e. Q2 = f(T). When the cold end temperature increases, the heat transfer through the heat pipe will decrease. It can be considered that Q2 is monotonically decreasing with respect to T.

[0103] Right side third term: net heat exchange Q3 of other parts with the heat dissipation surface. Generally, the temperature of the heat dissipation surface will be lower than that of the surrounding cabin, and the remaining parts of the cabin will transfer heat to it. When the temperature of the heat dissipation surface is higher, the surrounding heat transfer will be smaller. If this part of the heat transfer is considered as a function Q3 = g(T) related to the temperature of the heat dissipation surface, it can be considered that Q3 is monotonically decreasing with respect to T.

[0104] In the heat balance test, in order to make the heat dissipation conditions of the component M under test consistent with the on-orbit state, when the heat balance is finally reached, there should be:

[0105] Q1 = Q1';

[0106] Q2 = Q2';

[0107] Q3 = Q3';

[0108] Q4 = Q4'.

[0109] In order to make Q4 = Q4', the temperature T A ' of the simulated heat dissipation plate A should be the same as the temperature T of the actual heat dissipation surface B. In the heat test, we can measure T', T, and calculate Q4, Q4' by bringing them into equation 4.

[0110] To make Q2 = Q2', Q2' on the simulation heat sink A should be known and applied as Q2 on the real heat sink B; in equation ③, Q4' after balance is measurable, Q1' and Q3' are actively applied heat, so Q2' = Q4' - Q1' - Q3', which can be calculated by the heat balance equation (equation ③) of the simulation heat sink A.

[0111] To make Q3 = Q3', Q3 on the real heat sink B should be known and applied as Q3' on the simulation heat sink A; in equation ②, Q4 after balance is measurable, Q1 and Q2 are actively applied heat, so Q3 = Q4 - Q1 - Q2, which can be calculated by the heat balance equation (equation ②) of the real heat sink B.

[0112] Obviously, in the thermal test, we need to achieve two sets of equivalent heat balance of A and B, and we only need to adjust the values of Q2 actively applied to the real heat sink B and Q3' on the simulation heat sink A, and make them consistent with the calculated values Q2' and Q3 in the other set of heat balance, respectively.

[0113] For these two quantities that affect each other and have a mutual relationship, we can use the iterative approximation method to obtain their true values. That is, the following steps:

[0114] (1) Let Q3' = 0, establish the heat balance of the simulation heat sink A, calculate Q2', and apply Q2' as Q2 on B to establish the heat balance of the real heat sink B;

[0115] (2) After the heat balance of the real heat sink B is achieved, calculate Q3, and apply Q3 as Q3' on A to establish the heat balance of the simulation heat sink A; after the heat balance is achieved, calculate the new Q2';

[0116] (3) At this time, the temperatures of the simulation heat sink A and the real heat sink B may still have some difference, which is due to the new Q2' being slightly smaller than Q2, making T' still slightly smaller than T. Continue the operation in (1) to apply the new Q2' as the new Q2 on B to form a new heat balance of the real heat sink B; at this time, since the new Q2 is slightly smaller than the old Q2, the temperatures of the A and B plates are further approximated.

[0117] (4) If the difference between the temperatures of the A and B plates at this time is still outside the error allowed range, apply the latest Q3 of the real heat sink B as the latest Q3' on A to establish the latest heat balance of the simulation heat sink A, and the temperatures of the A and B plates will continue to further approximate.

[0118] After such iterations, the temperature difference between the two plates A and B will ultimately be within the allowable error range, and the difference between Q2 and Q2' can be ignored, and the difference between Q3 = Q3' can also be ignored. Based on the fact that the thermal equilibrium of both the simulated heat dissipation plate A and the real heat dissipation surface B is achieved and consistent with each other, the obtained Q2, Q3, Q4, Q2', Q3', and Q4' are all consistent with the real in-orbit situation.

[0119] Summarizing the above discussion, the steps of the thermal equilibrium test for iterative approximation can be obtained as Figure 3 shown, specifically including:

[0120] Step 1: Complete the manufacture and assembly of the "heat pipe - heat dissipation surface" system for the thermal test;

[0121] Step 2: Apply the external heat flux Q1' at the simulated heat dissipation plate A according to the theoretical heat flux absorbed by the heat dissipation surface, and given a preset equivalent peripheral heat transfer quantity Q3' (in the first balance, Q3' can be preset to 0 or a certain expected value. In this article, it is described with a preset of 0. The iterative steps with other preset values are not different from those described in this article). After reaching thermal equilibrium, the average temperature T'1 of the simulated plate A can be measured and obtained (*Note), and thus the heat dissipation quantity Q4'1 can be calculated. Substitute Q1' and Q4'1 into Equation ③ to calculate Q2'1.

[0122] *Note: The subscript " 1 " represents the quantity in the first round of thermal equilibrium iteration, and the subscript " 2 " represents the quantity in the second round of thermal equilibrium iteration; the superscript "'" represents the quantity of the simulated heat dissipation plate A, and without the superscript represents the quantity of the simulated heat dissipation surface B; the same below.

[0123] Step 3: Let Q21 = Q2'1 and apply it to the real heat dissipation surface B, and at the same time apply the theoretical external heat flux absorption value Q1 to the real heat dissipation surface B in the form of heat. After reaching this thermal equilibrium, since in the actual situation of the real heat dissipation surface B, Q31 > Q3'1 = 0, so at this time T1 > T'1 and Q41 > Q4'1. T1 can be measured and obtained, and thus Q41 can be calculated, and then substitute it into Equation ① to calculate Q31.

[0124] Step 4: The states of the real heat dissipation surface B and the simulated heat dissipation plate A have not converged with each other due to the difference between Q3'1 and Q31. Let Q3'2 = Q31 in Equation ③. Apply Q3'2 to the simulated heat dissipation plate A in the form of heat. After reaching this thermal equilibrium, since the applied Q3'2 > Q3'1 = 0, the temperature of the simulated heat dissipation plate A has increased compared to the previous equilibrium state, the heat transfer temperature difference of the heat pipe has decreased, and the heat transfer quantity has decreased compared to the previous equilibrium state, resulting in Q2'2 < Q2'1 = Q21. Comparing Equation ③ with Equation ①, it can be seen that Q4'2 < Q41. T'2 can be measured and obtained, and thus Q4'2 can be calculated, and then substitute it into Equation ③ to calculate Q2'2.

[0125] Step five: after the heat balance of step four is reached, the measured T'2 of the simulation heat sink is compared with T1 of the real heat sink. If |T1-T'2|<δ, the states of the two are completely equivalent. If |T1-T'2|>δ, step six is continued. Generally, the value of δ is determined according to the test accuracy requirement. In this step, if T'2 and T1 have a non-negligible difference due to the existence of weak heat leakage (Q5' in formula ②), Q5' can be subtracted. The subtracted T'2 and T1 are used for calculation and determination.

[0126] Step six: Q22=Q2'2 in formula ①. Q22 is applied to the real heat sink B in the form of heat instead of Q21. After the heat balance is reached, since Q22<Q21, the temperature of the real heat sink is lower than that in the last balance state (T2<T1), which further leads to Q32>Q31=Q3'2. Comparing formula ③ with formula ①, the difference between the heat balance state of the simulation heat sink A and that of the real heat sink B in the last balance state is further reduced.

[0127] Step seven: after the heat balance of step six is reached, T2 of the real heat sink B is compared with T'2 of the simulation heat sink. If |T2-T'2|<δ, the states of the two are completely equivalent. If |T2-T'2|>δ, step eight is continued. Generally, the value of δ is determined according to the test accuracy requirement. The processing method of heat leakage Q5' is the same as that in step five.

[0128] Step eight: Q3'3=Q32. The process of steps four to seven is repeated until |T n-1 -T' n |<δ or |T n -T' n |<δ. At this time, the states of the simulation heat sink A and the real heat sink B are equivalent, and the temperature T0 of the component M being tested is the temperature of the component after the heat balance is reached.

[0129] Embodiment

[0130] The process of the heat balance test of a certain spacecraft load component is used to illustrate the specific implementation mode of the present application. As shown in FIG. 1, the heat pipe and the corresponding heat sink position in a certain spacecraft load component are shown in a schematic diagram. There are K and L types of components in the load, which need to conduct heat to the heat sink through the heat pipe. The heat pipe is relatively tortuous. Due to the limited configuration, the positions of the K and L types of components are higher than the heat sink during the heat balance test, and the heat pipe is difficult to start in the heat test. If the heat pipe does not play a heat transfer role, the temperatures of the K and L types of components will be significantly higher, and the purpose of verifying the correctness of the heat design through the heat balance test cannot be achieved. Figure 5 、 Figure 6 As shown in FIG. 1, the heat pipe and the corresponding heat sink position in a certain spacecraft load component are shown in a schematic diagram. There are K and L types of components in the load, which need to conduct heat to the heat sink through the heat pipe. The heat pipe is relatively tortuous. Due to the limited configuration, the positions of the K and L types of components are higher than the heat sink during the heat balance test, and the heat pipe is difficult to start in the heat test. If the heat pipe does not play a heat transfer role, the temperatures of the K and L types of components will be significantly higher, and the purpose of verifying the correctness of the heat design through the heat balance test cannot be achieved.

[0131] In the thermal balance test of the component, a test "heat pipe-heat dissipation surface" system is specially set up, and the method described in the application is used to successfully ensure the smooth progress of the test.

[0132] Step one: complete the manufacture and assembly of the "heat pipe-heat dissipation surface" system for thermal test.

[0133] Considering the placement orientation of the load component in the thermal balance test, the thermal test heat pipes are designed and manufactured, and a total of 5 main thermal test heat pipes for components K and L are designed and manufactured, with the direction and position as shown in Figure 7 、 Figure 8 The conditions met by these heat pipes are as follows:

[0134] a) By controlling the contact length between the thermal test heat pipe and the heat generating component, the consistency of the contact area is ensured;

[0135] b) The thermal test heat pipe and the original heat pipe are installed in the same way, both of which are installed on the heat dissipation surface by pressing plate;

[0136] c) The number of bends N of the thermal test heat pipe is consistent with that of the original heat pipe;

[0137] d) The contact area between the thermal test heat pipe and the heat dissipation surface is consistent with that between the original heat pipe and the heat dissipation surface;

[0138] e) From component K and component L, along the entire path of the thermal test heat pipe to the simulated heat dissipation surface, there is no downward movement along the direction of gravity.

[0139] According to the configuration of the load component, the simulated heat dissipation surface for thermal test is designed, and one simulated heat dissipation surface is provided for each of components K and L in the thermal balance test, with the following states:

[0140] a) The surface state of the simulated heat dissipation surface of component K is the same as that of the real heat dissipation surface (both are a certain white paint), and the area is 0.34m 2 The surface state of the simulated heat dissipation surface of component L is the same as that of the real heat dissipation surface (both are a certain white paint), and the area is 0.31m 2 ;

[0141] b) The simulated heat dissipation surface is pasted with a heater on the back for applying heat;

[0142] c) The two simulated heat dissipation surfaces are supported by a support, and the support tracks the temperature of the simulated heat dissipation surface, and Q5' is small.

[0143] The above conditions are general designs, and the same operation is performed when using the special heat dissipation surface-heat pipe system for thermal test.

[0144] The manufacturing and assembly of the "heat pipe-radiator" system used in the thermal test were completed, and the system was put into the vacuum tank together with the load components for thermal balance test. In this load test, three different working conditions (working condition 1, working condition 2, and working condition 3) were performed.

[0145] Taking working condition 1 as an example, the iterative adjustment process is as follows:

[0146] Step two: according to the theoretical radiator absorption external heat flow value, a pure absorption external heat flow Q1' is applied to the simulated radiator plate of component K (note), and an initial equivalent peripheral heat transfer Q3' is set K = 13.8 W, an initial equivalent peripheral heat transfer Q3' is set 1,K = 24.6 W, and a pure absorption external heat flow Q1' is applied to the simulated radiator plate of component L L = 14.4 W, and an initial equivalent peripheral heat transfer Q3' is set 1,L = 38.0 W. Wait for thermal equilibrium. The average temperature of the simulated radiator plate of component K is measured as T' 1,K = +3.8℃, and the average temperature of the simulated radiator plate of component L is measured as T' 1,L = -1.1℃, so the heat dissipation Q4' is calculated as Q4' 1,K = 96.3 W, and Q4' is calculated as Q4' 1,L = 80.6 W. Substitute Q1' and Q4' into formula ③ to calculate the total heat transfer Q2' of the heat pipe to the simulated radiator plate in this round 1,K = 55.5 W, and Q2' is calculated as Q2' 1,L = 24.7 W.

[0147] Step three: let Q2' 1,K = 55.5 W, and Q2' 1,L = 24.6 W be applied to the real radiator, and the theoretical external heat flow absorption value Q1' K = 13.8 W, and Q1' L = 14.4 W be applied to the real radiator in the form of heat. Wait for thermal equilibrium. The average temperature of the real radiator of component K is measured as T' 1,K = -0.2℃, and the average temperature of the real radiator of component L is measured as T' 1,L = -2.2℃, so Q4' is calculated as Q4' 1,K = 91.0 W, and Q4' is calculated as Q4' 1,L = 79.2 W. Then substitute into formula ① to calculate Q3' 1,K = 21.7 W, and Q3' is calculated as Q3' 1,L = 40.2 W.

[0148] Step four: the state of the real radiator and the simulated radiator plate has not yet converged to each other due to the difference between Q3' and Q3'. Therefore, let Q3' 2,K = Q3 1,K = 21.7 W, and let Q3' 2,L = Q31,L = 40.2 W, which is applied to the simulation heat sink in the form of heat. Wait for thermal equilibrium to be reached. The average temperature T' of the simulation heat sink of components K and L is measured 2,K = 3.3 ℃, T' 2,L = 0.1 ℃, and Q4' is calculated therefrom 2,K = 95.7 W, Q4' 2,L = 82.0 W, and Q2' is calculated therefrom by substituting into equation (3) 2,K = 57.7 W, Q2' 2,L = 23.8 W.

[0149] Step five: after the thermal equilibrium of step four is reached, the heat leakage Q5' of the two simulation heat sinks K = 2.4 W, Q5' L = 3.5 W is deducted from the actual heat exchange, and after the deduction, T' 2,K = 1.2 ℃, T' 2,L = -2.0 ℃. The T'2 of the simulation heat sink is compared with the T1 of the real heat sink, and if |T1-T'2| < 1.5 ℃ is satisfied, the states of the two are equivalent. There is no need to continue the subsequent steps.

[0150] The tests are carried out according to the above steps for the three thermal equilibrium conditions respectively, and the heat exchange of each part is shown in Table 1. At this time, the simulation heat sink and the real heat sink are equivalent to each other in terms of temperature, heat pipe heat transfer, equivalent heat transfer of the surrounding structure, etc. The temperature T0 of the tested component reflected in the thermal test is equivalent to the temperature of the heat generating component with the real heat sink.

[0151] Table 1 Statistics of the heat exchange of the simulation heat sink and the real heat sink

[0152]

[0153]

[0154] Since the load component K and the component L have high temperature stability requirements (the component K requires ±0.1 ℃, and the component L requires ±0.3 ℃), high-precision temperature measurement and control are designed on the components, and the boundary accuracy of heat dissipation is crucial to whether the thermal control indicators can be successfully implemented. The test is carried out by using the method described in the application, and taking the working condition 1 as an example,

[0155] As shown in Figure 9 , Figure 10 , the temperature curves of the component K and the component L at different positions after the thermal equilibrium of the test is reached. The test results are consistent with the simulation analysis, and the test proves that the thermal control measures for the above components can meet the temperature stability requirements.

[0156] So far, by setting the heat pipe and the heat dissipation surface system special for the heat test, and through the iterative approximation test by the method of the application, the temperature boundary in orbit is well simulated, and the problem of the accuracy and effectiveness of the heat test is solved.

[0157] Although the present application has been disclosed with the above preferred embodiments, it is not intended to limit the present application, and any person skilled in the art can make possible changes and modifications to the technical solutions of the present application by using the disclosed methods and technical contents without departing from the spirit and scope of the present application. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present application, which does not depart from the technical solutions of the present application, shall fall within the protection scope of the technical solutions of the present application.

[0158] The contents not described in detail in the specification of the present application belong to the known technology of the person skilled in the art.

Claims

1. An iterative approach to thermal balance testing of a heat spreader and heat pipe system for a thermal test surface, the method comprising: The method comprises the following steps: ​ Manufacture and assemble the heat dissipation surface and the heat pipe system for thermal test, set up the simulation heat dissipation plate in the heat dissipation surface and the heat pipe system, and build the thermal test configuration; Perform thermal analysis on the simulation heat dissipation plate and the real heat dissipation plate in the thermal test configuration; According to the thermal analysis result, apply external heat flow to the simulation heat dissipation plate and give the preset equivalent peripheral heat transfer amount; After the thermal balance, measure the temperature parameters of the simulation heat dissipation plate to calculate the heat dissipation amount of the simulation heat dissipation plate, and calculate the current heat pipe heat transfer amount according to the heat dissipation amount; Apply the calculated heat pipe heat transfer amount and the theoretical external heat flow of the simulation heat dissipation plate to the real heat dissipation plate, and after the real heat dissipation plate reaches the thermal balance, measure the temperature parameters of the real heat dissipation plate to calculate the heat dissipation amount of the real heat dissipation plate; Calculate the equivalent value of the net heat exchange amount of the real heat dissipation surface according to the heat dissipation amount of the real heat dissipation plate; Apply the equivalent value of the net heat exchange amount of the real heat dissipation surface to the simulation heat dissipation plate in the form of heat, and after the simulation heat dissipation plate reaches the thermal balance, measure the temperature parameters of the simulation heat dissipation plate to calculate the heat dissipation amount of the simulation heat dissipation plate in this thermal balance; Calculate the current heat pipe heat transfer amount according to the heat dissipation amount of the simulation heat dissipation plate in this thermal balance; Compare the actually measured temperature parameters of the simulation heat dissipation plate with the temperature parameters of the real heat dissipation plate, and according to the comparison result, judge whether the simulation heat dissipation plate and the real heat dissipation plate are equivalent, if yes, end the test and take the current temperature parameters of the thermal test configuration as the final temperature result of the thermal balance test, otherwise, continue the thermal test; Apply the current heat pipe heat transfer amount to the real heat dissipation plate, measure the temperature parameters of the real heat dissipation plate after the thermal balance, compare the temperature parameters with the temperature parameters of the simulation heat dissipation plate, and according to the comparison result, judge whether the simulation heat dissipation plate and the real heat dissipation plate are equivalent, if yes, end the test and take the current temperature parameters of the thermal test configuration as the final temperature result of the thermal balance test, otherwise, continue the thermal test; Repeat the calculation of the heat pipe heat transfer amount of the simulation heat dissipation plate in the thermal balance state, the comparison of the temperature parameters of the simulation heat dissipation plate after the heat pipe heat transfer amount is applied, until the simulation heat dissipation plate and the real heat dissipation plate are completely equivalent, and take the current temperature parameters of the thermal test configuration as the final temperature result of the thermal balance test.

2. The iterative approximation thermal balance test method of the heat dissipation surface and the heat pipe system for thermal test according to claim 1, wherein the method for performing thermal analysis on the simulation heat dissipation plate and the real heat dissipation plate comprises the following steps: According to any component, establish a thermal balance equation for the thermal test configuration, determine the relationship among the heat dissipation amount, the external heat flow, the heat pipe heat transfer amount and the net heat exchange amount of the heat dissipation surface; the external heat flow is simulated by external heating, the net heat exchange amount of the heat dissipation surface is automatically generated after the temperature parameters of the heat dissipation surface are determined; the heat pipe heat transfer amount is determined according to the selected heat pipe simulation; the thermal test configuration has a heat leakage amount, and during the thermal test process, the sum of the heat dissipation amount and the heat leakage amount is equivalent to the sum of the external heat flow, the heat pipe heat transfer amount and the net heat exchange amount of the heat dissipation surface.

3. The iterative approximation thermal balance test method of the heat dissipation surface and the heat pipe system for thermal test according to claim 2, wherein the heat leakage amount is controlled by tracking and controlling the temperature or installing heat insulation to the support structure of the thermal test configuration to make the heat leakage amount negligible. ​ ​ 4. The iterative approximation thermal balance test method of a heat dissipation surface and heat pipe system of a thermal test according to claim 2, characterized in that: The simulation heat sink, real heat sink: heat dissipation Q4 = ε r ·σ·(T-T back ) 4 where ε r - the infrared emissivity of the heat sink surface, σ - the Boltzmann constant, T back - the background temperature, T - the temperature of the heat sink surface; the external heat flow Q1 is the actual external heat flow absorbed by the heat dissipation surface in orbit, and is irrelevant to the temperature of the heat dissipation surface; the heat pipe heat transfer Q2 is affected by the temperature difference of the heat pipe installation interface, and the heat transfer is related to the temperature of the heat dissipation surface when the temperature of the equipment end is unchanged; when the temperature of the heat dissipation surface is increased, the heat pipe heat transfer is reduced, and the heat pipe heat transfer Q2 is monotonously decreased with respect to the temperature of the heat dissipation surface; the net heat exchange Q3 of the heat dissipation plate heat dissipation surface is monotonously decreased with respect to the temperature of the heat dissipation surface.

5. The iterative approximation thermal balance test method of a heat dissipation surface and heat pipe system of a thermal test according to claim 4, characterized in that: the heat dissipation conditions of any component of the thermal test configuration are consistent with the in-orbit state to reach a thermal balance state, wherein: in the thermal balance state, the measured temperature parameters of the simulation heat dissipation plate are the same as those of the actual heat dissipation plate, the heat pipe heat transfer of the simulation heat dissipation plate is applied to the actual heat dissipation plate, the net heat exchange of the other part of the heat dissipation surface of the actual heat dissipation plate is applied to the simulation heat dissipation plate, and for any heat dissipation plate, the heat dissipation is the sum of the external heat flow, the heat pipe heat transfer and the net heat exchange of the other part of the heat dissipation surface.

6. The iterative approximation thermal balance test method of a heat dissipation surface and heat pipe system of a thermal test according to claim 4, characterized in that: the thermal balance state of the simulation heat dissipation plate and the thermal balance state of the actual heat dissipation plate are achieved by adjusting the heat pipe heat transfer actively applied to the actual heat dissipation plate and the net heat exchange of the heat dissipation surface actively applied to the simulation heat dissipation plate, and keeping the heat pipe heat transfer and the net heat exchange of the heat dissipation surface consistent with those in another group of thermal balance states.

7. The iterative approximation thermal balance test method of a heat dissipation surface and heat pipe system of a thermal test according to claim 4, characterized in that: the method for obtaining the heat pipe heat transfer Q2 actively applied to the actual heat dissipation plate and the net heat exchange Q3' of the heat dissipation surface actively applied to the simulation heat dissipation plate is as follows: when the simulation heat dissipation plate A is in a thermal balance state, Q3'=0, the current heat pipe heat transfer Q2' actively applied to the simulation heat dissipation plate is calculated, so that the actual heat dissipation plate B enters a thermal balance state; the equivalent value Q3 of the net heat exchange of the actual heat dissipation surface is calculated as the net heat exchange Q3' of the simulation heat dissipation surface applied to the simulation heat dissipation plate A, and when the simulation heat dissipation plate achieves a second thermal balance, the current heat pipe heat transfer Q2' in the new thermal balance state is calculated; the current heat pipe heat transfer Q2' in the new thermal balance state is applied to the actual heat dissipation plate B to form a new thermal balance state of the actual heat dissipation plate B; if the temperature parameter difference between the simulation heat dissipation plate A and the actual heat dissipation plate B in the current state is outside the error allowable range, the latest equivalent value Q3 of the net heat exchange of the actual heat dissipation surface of the actual heat dissipation plate B is taken as the latest heat exchange equivalent value applied to the simulation heat dissipation plate A, a third thermal balance state of the simulation heat dissipation plate is established, the temperature parameter difference and the error allowable range are repeatedly judged, and the optimization iteration between the equivalent value Q3 of the net heat exchange of the actual heat dissipation surface and the net heat exchange Q3' of the simulation heat dissipation surface and the heat pipe heat transfer Q2 and the current heat pipe heat transfer Q2' is realized until the parameters of the thermal balance state are completely consistent with those in the in-orbit state.

8. The iterative approximation heat balance test method for heat test heat dissipation surface and heat pipe system of claim 7, characterized in that: The method for comparing the measured temperature parameters of the real heat dissipation plate with the simulated heat dissipation plate after heat balance is: After the second heat balance of the simulated heat dissipation plate is realized, the temperature parameters of the simulated heat dissipation plate and the real heat dissipation plate are measured, including the temperature T'2 of the simulated heat dissipation plate and the temperature T1 of the real heat dissipation plate, and the comparison relationship between |T1-T'2| and δ is judged. If |T1-T'2| > δ, the current heat pipe heat transfer amount is applied to the real heat dissipation plate, and the comparison judgment is continued after heat balance. If |T1-T'2| < δ, the simulated heat dissipation plate and the real heat dissipation plate are equivalent, the test is ended, and the current temperature parameters of the heat test configuration are taken as the final temperature results of the heat balance test.

9. The iterative approximation heat balance test method for heat test heat dissipation surface and heat pipe system of claim 8, characterized in that: The heat transfer amount of the heat pipe is applied to the real heat dissipation plate, and after the real heat dissipation plate realizes thermal equilibrium for the second time, the temperature parameters of the real heat dissipation plate are measured and compared with the temperature parameters of the simulation heat dissipation plate, including comparison of the temperature T2 of the real heat dissipation plate with the temperature T'2 of the simulation heat dissipation plate, if |T2-T'2|<δ, the simulation heat dissipation plate and the real heat dissipation plate are equivalent, the test is ended and the current temperature parameters of the thermal test configuration are taken as the final temperature results of the thermal equilibrium test; if |T2-T'2|>δ, the heat pipe heat transfer amount calculation of the simulation heat dissipation plate under the thermal equilibrium state and the corresponding double-plate temperature parameter comparison after the heat pipe heat transfer amount is applied are repeated until the simulation heat dissipation plate and the real heat dissipation plate are completely equivalent, that is, |T n-1 -T' n |<δ or |T n -T' n |<δ is met.

10. The iterative approximation heat balance test method for heat test heat dissipation surface and heat pipe system of claim 9, characterized in that: The comparison value δ is determined according to the heat test accuracy requirement; the heat test configuration has heat leakage, which causes the difference between the temperature T'2 of the simulated heat dissipation plate and the temperature T1 of the real heat dissipation plate, and the temperature T'2 of the simulated heat dissipation plate and the temperature T1 of the real heat dissipation plate are reduced through the heat leakage parameter to reduce the difference and the influence on the temperature parameter comparison.

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