Iterative approximation heat balance test method for heat test radiating surface and heat pipe system

Abstract

The invention relates to an iterative approximation heat balance test method of a heat dissipation surface and heat pipe system for a thermal test, which comprises the following steps of: when a special heat dissipation surface-heat pipe system for the thermal test is used, removing an on-orbit real heat pipe under an original configuration, arranging a set of simulated heat pipe and heat dissipation surface for the thermal test, and finishing the construction of a thermal test configuration; through multiple times of test iteration of two parameters of different heat dissipation plates in the heat test process, the heat transfer amount between the heat dissipation plate or the heat dissipation surface and a heat pipe, the heat dissipation amount between the heat dissipation plate or the heat dissipation surface and the environment and the heat exchange amount between the heat dissipation surface and other structures are accurately obtained, the accurate heat boundary condition is determined, the problem of insufficient verification of the heat test is solved, and the test efficiency is improved. And the thermal design reliability of the spacecraft can be effectively improved.

Description

Technical Field

[0001] The invention relates to an iterative approximation thermal 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 Art

[0002] At present, the thermal control measures of spacecraft are becoming increasingly complex. Many components are located inside the spacecraft. In order to achieve the heat dissipation of these internal components, it is usually necessary to arrange independent heat dissipation surfaces outside the spacecraft. The surface state of the heat dissipation surface is generally low solar absorption ratio / high emissivity material; heat pipes are used to connect the components themselves to the heat dissipation surface to form a good heat conduction path. The layout of the heat dissipation surface-heat pipe system is as follows: Figure 1 shown.

[0003] Generally, the correctness of the thermal design of a spacecraft needs to be verified through a ground-based thermal balance test. Unlike the state of a spacecraft in orbit, the ground test of a spacecraft is affected by gravity. When the height of the heat dissipation surface is lower than the heat generating component, there is a risk that the heat pipe connecting the two will not be able to start smoothly. According to the provisions of GB / T 34515-2017 "Spacecraft Thermal Balance Test Method", the thermal 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 spacecraft configuration develops towards complexity, it becomes increasingly difficult to take into account the position of all heat pipes. If some heat pipes fail to start during the thermal test, it will affect the thermal balance test effect.

[0004] At the same time, when using a heat sink-heat pipe system specifically designed for thermal testing, the traditional method of conducting the test makes it impossible to obtain the actual on-orbit heat pipe heat transfer Q2 and the equivalent value of the net heat exchange between other parts and the actual heat sink Q3'. Using hypothetical / simulated values ​​to conduct the test will introduce errors, and there is a lack of accurate methods to obtain the two quantities. Summary of the invention

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

[0006] The present invention solves the above technical problems by the following technical solutions:

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

[0008] Manufacture and assemble the heat dissipation surface and heat pipe system for thermal testing, set up simulated heat dissipation plates in the heat dissipation surface and heat pipe system, and construct a thermal test configuration;

[0009] Conduct thermal analysis on simulated heat sinks and real heat sinks in thermal test configurations;

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

[0011] After measuring the thermal equilibrium, the temperature parameters of the simulated heat sink are used to calculate the heat dissipation of the simulated heat sink, and the current heat transfer of the heat pipe is calculated based on the heat dissipation;

[0012] Apply the calculated heat pipe heat transfer and theoretical external heat flux of the simulated heat sink to the real heat sink. 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.

[0013] Calculate the equivalent value of the net heat exchange of the actual heat dissipation surface according to the heat dissipation of the actual heat dissipation plate;

[0014] The equivalent value of the net heat exchange of the real heat dissipation surface is applied to the simulated heat dissipation plate in the form of heat. When the simulated heat dissipation plate achieves thermal equilibrium, the temperature parameters of the simulated heat dissipation plate are measured to calculate the heat dissipation of the simulated heat dissipation plate in this thermal equilibrium;

[0015] Calculate the current heat transfer amount of the heat pipe based on the heat dissipation of the simulated heat sink thermal balance;

[0016] The temperature parameters of the simulated heat sink are measured and compared with the temperature parameters of the real heat sink. According to the comparison results, it is determined whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test. Otherwise, the thermal test is continued.

[0017] Apply the current heat transfer amount of the heat pipe to the real heat sink, measure the temperature parameters of the real heat sink after thermal equilibrium, and compare them with the temperature parameters of the simulated heat sink. According to the comparison results, determine whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, end the test and use the current temperature parameters of the thermal test configuration as the final temperature result of the thermal equilibrium test, otherwise continue the thermal test;

[0018] Repeat the calculation of the heat pipe heat transfer of the simulated heat sink under the thermal equilibrium state and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer is applied until the simulated heat sink and the real heat sink are completely equivalent. The current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test.

[0019] The method for thermal analysis of simulated heat sink and real heat sink is:

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

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

[0022] The simulated heat sink and the real heat sink have the following heat dissipation: Q4 = ε r ·ζ·(TT back ) 4

[0023] In the formula, ε r -Infrared emissivity of the heat dissipation surface (known), ζ-Boltzmann constant, T back -background temperature, T-temperature of heat dissipation surface B;

[0024] The external heat flux Q1 is the actual external heat flux absorbed by the heat dissipation surface in orbit, which has nothing to do with the temperature of the heat dissipation surface itself;

[0025] The heat transfer amount Q2 of the heat pipe is affected by the temperature difference of the heat pipe installation interface. When the temperature at the equipment end remains unchanged, the heat transfer amount is related to the heat dissipation surface temperature; when the heat dissipation surface temperature increases, the heat transfer amount of the heat pipe decreases, and the heat transfer amount Q2 of the heat pipe decreases monotonically with respect to the heat dissipation surface temperature;

[0026] The net heat exchange amount Q3 between the heat sink and the heat dissipation surface decreases monotonically with respect to the heat dissipation surface temperature.

[0027] The heat dissipation condition of any component of the thermal test configuration reaches a thermal equilibrium state after being consistent with the on-orbit state, wherein:

[0028] Under the thermal equilibrium state, the measured temperature parameters of the simulated heat sink are the same as those of the real heat sink. The heat transfer of the heat pipe of the simulated heat sink is applied to the actual heat sink, and the net heat exchange between other parts of the real heat sink and the heat dissipation surface is applied to the simulated heat sink. For any heat sink, the heat dissipation is the sum of the external heat flux, the heat transfer of the heat pipe, and the net heat exchange between other parts and the heat dissipation surface.

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

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

[0031] Let Q3'=0, when simulating the thermal equilibrium state of heat sink A, calculate the current heat transfer amount Q2' of the heat pipe actively applied to the simulated heat sink, so that the real heat sink B enters the thermal equilibrium state;

[0032] Calculate the equivalent value Q3 of the net heat transfer of the real heat dissipation surface as the net heat transfer Q3' of the simulated heat dissipation surface and apply it to the simulated heat dissipation plate A. When the simulated heat dissipation plate achieves the second thermal equilibrium, calculate the current heat transfer Q2' of the heat pipe under the new thermal equilibrium state.

[0033] Apply the current heat transfer amount Q2' of the heat pipe in the new thermal equilibrium state 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 allowable error range, the latest real heat sink net heat exchange equivalent value Q3 of the real heat sink B is applied to the simulated heat sink A as the latest heat exchange equivalent value, and the third thermal equilibrium state of the simulated heat sink is established. The judgment of the temperature parameter difference and the allowable error range is repeated to achieve optimization iteration between the real heat sink net heat exchange equivalent value Q3 and the simulated heat sink net heat exchange Q3', 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.

[0035] The method for measuring the temperature parameters of the actual heat sink after thermal equilibrium and comparing them with the temperature parameters of the simulated heat sink is as follows:

[0036] After achieving the second thermal equilibrium of the simulated heat sink, 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 comparative relationship between |T1-T'2| and δ is judged. If |T1-T'2|>δ, the current heat transfer amount of the heat pipe is applied to the real heat sink, and the comparative judgment is continued after thermal equilibrium; if |T1-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, and the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test.

[0037] The current heat transfer amount of the heat pipe is applied to the real heat sink. When the real heat sink achieves thermal equilibrium for the second time, the temperature parameters of the real heat sink are measured and compared with the temperature parameters of the simulated heat sink, including the temperature T2 of the simulated heat sink and the temperature T'2 of the simulated heat sink. If |T2-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, the test is terminated, and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test; if |T2-T'2|>δ, the heat transfer amount of the simulated heat sink under thermal equilibrium state is calculated, and the corresponding double-plate temperature parameters are compared after the heat transfer amount of the heat pipe is applied, until the simulated heat sink and the real heat sink are completely equivalent, that is, |T n-1 -T' n |<δ or |T n -T' n |<δ.

[0038] The comparison value δ is determined according to the accuracy requirements of the thermal test; there is heat leakage in the thermal test configuration, which leads to differences between the temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink. The temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink are subtracted by heat leakage parameters to reduce the differences and the impact on the comparison of temperature parameters.

[0039] The advantages of the present invention compared with the prior art are:

[0040] (1) The invention provides an iterative approximation thermal balance test method for a heat dissipation surface and a heat pipe system for a thermal test. By setting a heat pipe and a heat dissipation surface system dedicated to the thermal test and carrying out an iterative approximation test, the on-orbit temperature boundary is well simulated, and the accuracy and effectiveness of the thermal test are solved. The actual on-orbit heat transfer Q2 of the heat pipe in the on-orbit state and the equivalent value Q3' of the net heat transfer between other parts and the actual heat dissipation surface are obtained, and the thermal boundary of the component M under test in the thermal balance test is accurately simulated.

[0041] (2) The present invention uses the thermal test "heat sink-heat pipe system" to accurately obtain the heat transfer between the heat sink / heat sink and the heat pipe, the heat dissipation between the heat sink / heat sink and the environment, and the heat exchange between the heat sink and other structures through several test iterations, and determines the accurate thermal boundary conditions, thereby solving the problem of insufficient verification of thermal tests and effectively improving the reliability of spacecraft thermal design. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] Figure 1 A schematic diagram of the heat dissipation path of the traditional configuration provided for the invention;

[0043] Figure 2 Schematic diagram of the actual configuration to the hot test configuration provided for the invention;

[0044] Figure 3A flow chart of the iterative approximation thermal balance test method for the heat test heat dissipation surface and heat pipe system provided by the invention;

[0045] Figure 4 Schematic diagram of heat exchange between the real heat dissipation surface provided by the invention and the simulated heat dissipation plate and the outside world;

[0046] Figure 5 A schematic diagram of the actual heat pipe direction and heat dissipation surface position of component K provided for the invention;

[0047] Figure 6 A schematic diagram of the actual heat pipe direction and heat dissipation surface position of the component L provided for the invention;

[0048] Figure 7 A schematic diagram of the heat pipe orientation and simulated heat sink position for the thermal test of component K provided by the invention;

[0049] Figure 8 A schematic diagram of the heat pipe orientation and simulated heat sink position for the thermal test of component L provided by the invention;

[0050] Fig. 9 The temperature curves of different parts of component K in working condition 1 provided by the invention;

[0051] Fig.10 The temperature curves of different parts of component L in the working condition 1 provided by the invention; DETAILED DESCRIPTION

[0052] The invention discloses an iterative approximation thermal balance test method for a heat dissipation surface and a heat pipe system for a thermal test. When a heat dissipation surface-heat pipe system dedicated to the thermal test is used, the real heat pipes in orbit under the original configuration are removed, and a set of simulated heat pipes and heat dissipation surfaces for the thermal test are arranged to complete the construction of the thermal test configuration. Through several test iterations of dual parameters of different heat dissipation plates during the thermal test, the heat transfer between the heat dissipation plate or heat dissipation surface and the heat pipe, the heat dissipation between the heat dissipation plate or heat dissipation surface and the environment, and the heat exchange between the heat dissipation surface and other structures are accurately known, and accurate thermal boundary conditions are determined, thereby solving the problem of insufficient verification of the thermal test and effectively improving the reliability of the thermal design of the spacecraft.

[0053] Thermal test heat sink and heat pipe system iterative approximation thermal balance test method, the specific steps are:

[0054] Manufacture and assemble the heat dissipation surface and heat pipe system for thermal testing, set up simulated heat dissipation plates in the heat dissipation surface and heat pipe system, and construct a thermal test configuration;

[0055] Conduct thermal analysis on simulated heat sinks and real heat sinks in thermal test configurations;

[0056] According to the thermal analysis results, an external heat flux is applied to the simulated heat sink and a preset equivalent peripheral heat transfer amount is given;

[0057] After measuring the thermal equilibrium, the temperature parameters of the simulated heat sink are used to calculate the heat dissipation of the simulated heat sink, and the current heat transfer of the heat pipe is calculated based on the heat dissipation;

[0058] Apply the calculated heat pipe heat transfer and theoretical external heat flux of the simulated heat sink to the real heat sink. 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] Calculate the equivalent value of the net heat exchange of the actual heat dissipation surface according to the heat dissipation of the actual heat dissipation plate;

[0060] The equivalent value of the net heat exchange of the real heat dissipation surface is applied to the simulated heat dissipation plate in the form of heat. When the simulated heat dissipation plate achieves thermal equilibrium, the temperature parameters of the simulated heat dissipation plate are measured to calculate the heat dissipation of the simulated heat dissipation plate in this thermal equilibrium;

[0061] Calculate the current heat transfer amount of the heat pipe based on the heat dissipation of the simulated heat sink thermal balance;

[0062] The temperature parameters of the simulated heat sink are measured and compared with the temperature parameters of the real heat sink. According to the comparison results, it is determined whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test. Otherwise, the thermal test is continued.

[0063] Apply the current heat transfer amount of the heat pipe to the real heat sink, measure the temperature parameters of the real heat sink after thermal equilibrium, and compare them with the temperature parameters of the simulated heat sink. According to the comparison results, determine whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, end the test and use the current temperature parameters of the thermal test configuration as the final temperature result of the thermal equilibrium test, otherwise continue the thermal test;

[0064] Repeat the calculation of the heat pipe heat transfer of the simulated heat sink under the thermal equilibrium state and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer is applied until the simulated heat sink and the real heat sink are completely equivalent. The current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test.

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

[0066] For the thermal test configuration, a heat balance equation is established based on any component to determine the relationship between the heat dissipation and the external heat flux, the heat transfer of the heat pipe and the net heat exchange with the heat dissipation surface; the external heat flux is simulated by external heating, and the net heat exchange with the heat dissipation surface is automatically generated after the heat dissipation surface temperature parameters are determined; the heat transfer of the heat pipe is determined based on the selected heat pipe simulation; there is heat leakage in the thermal test configuration, and during the thermal test, the sum of the heat dissipation and the heat leakage is equivalent to the sum of the external heat flux, the heat transfer of the heat pipe and the net heat exchange with the heat dissipation surface.

[0067] The heat leakage can be neglected by controlling the temperature of the support structure of the thermal test configuration or by installing thermal insulation.

[0068] Simulated heat sink, real heat sink: heat dissipation Q4 = ε r ·ζ·(TT back ) 4

[0069] In the formula, ε r -Infrared emissivity of the heat dissipation surface (known), ζ-Boltzmann constant, T back -background temperature, T-temperature of heat dissipation surface B;

[0070] The external heat flux Q1 is the actual external heat flux absorbed by the heat dissipation surface in orbit, which has nothing to do with the temperature of the heat dissipation surface itself;

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

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

[0073] The heat dissipation condition of any component of the thermal test configuration is consistent with the on-orbit state and reaches thermal equilibrium, where:

[0074] Under the thermal equilibrium state, the measured temperature parameters of the simulated heat sink are the same as those of the real heat sink. The heat transfer of the heat pipe of the simulated heat sink is applied to the actual heat sink, and the net heat exchange between other parts of the real heat sink and the heat dissipation surface is applied to the simulated heat sink. For any heat sink, the heat dissipation is the sum of the external heat flux, the heat transfer of the heat pipe, and the net heat exchange between other parts and the heat dissipation surface.

[0075] The thermal equilibrium state of the simulated heat sink and the thermal equilibrium state of the real heat sink are achieved by adjusting the heat transfer of the heat pipes actively applied to the real heat sink and the net heat exchange with the heat dissipation surface actively applied to the simulated heat sink, and keeping them consistent with the heat transfer of the heat pipes and the net heat exchange with the heat dissipation surface in another corresponding set of thermal equilibrium states.

[0076] The method for obtaining the heat transfer amount Q2 of the heat pipe actively applied to the real heat sink and the net heat exchange amount Q3' of the heat sink actively applied to the simulated heat sink is:

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

[0078] Calculate the equivalent value Q3 of the net heat transfer of the real heat dissipation surface as the net heat transfer Q3' of the simulated heat dissipation surface and apply it to the simulated heat dissipation plate A. When the simulated heat dissipation plate achieves the second thermal equilibrium, calculate the current heat transfer Q2' of the heat pipe under the new thermal equilibrium state.

[0079] Apply the current heat transfer amount Q2' of the heat pipe in the new thermal equilibrium state to the real heat sink B to form a new thermal equilibrium state of the real heat sink B;

[0080] If the temperature parameter difference between the simulated heat sink A and the real heat sink B in the current state is outside the allowable error range, the latest real heat sink net heat exchange equivalent value Q3 of the real heat sink B is applied to the simulated heat sink A as the latest heat exchange equivalent value, and the third thermal equilibrium state of the simulated heat sink is established. The judgment of the temperature parameter difference and the allowable error range is repeated to achieve optimization iteration between the real heat sink net heat exchange equivalent value Q3 and the simulated heat sink net heat exchange Q3', 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] The method for measuring the temperature parameters of the actual heat sink after thermal equilibrium and comparing them with the temperature parameters of the simulated heat sink is as follows:

[0082] After achieving the second thermal equilibrium of the simulated heat sink, 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 comparative relationship between |T1-T'2| and δ is judged. If |T1-T'2|>δ, the current heat transfer amount of the heat pipe is applied to the real heat sink, and the comparative judgment is continued after thermal equilibrium; if |T1-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, and the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test.

[0083] The current heat transfer amount of the heat pipe is applied to the real heat sink. When the real heat sink achieves thermal equilibrium for the second time, the temperature parameters of the real heat sink are measured and compared with the temperature parameters of the simulated heat sink, including the temperature T2 of the simulated heat sink and the temperature T'2 of the simulated heat sink. If |T2-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, the test is terminated, and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test; if |T2-T'2|>δ, the heat transfer amount of the simulated heat sink under thermal equilibrium state is calculated, and the corresponding double-plate temperature parameters are compared after the heat transfer amount of the heat pipe is applied, until the simulated heat sink and the real heat sink are completely equivalent, that is, |T n-1 -T' n |<δ or |T n -T' n |<δ.

[0084] The comparison value δ is determined according to the accuracy requirements of the thermal test. The thermal test configuration has heat leakage, which leads to differences between the temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink. The temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink are subtracted by heat leakage parameters to reduce the differences and the impact on the comparison of temperature parameters.

[0085] The following is further described in conjunction with the accompanying drawings and preferred embodiments of the specification:

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

[0087] For the heat dissipated component M, its heat balance equation is: The heat generated by component M is Q M,heat = Component radiates outward Q M,r + Heat transfer from components to the outside through the cabin Q M,c1 + Components transfer heat to the outside through heat pipes Q M,c2 In the thermal balance test, in order to ensure that the temperature level of component M is consistent with that on orbit, the above three items need to be simulated.

[0088] Component radiates Q M,r , components transfer heat to the outside through the cabin Q M,c1 It depends on the temperature distribution of the cabin. In terms of the actual situation of the thermal balance test, while simulating the heat flow outside the cabin as usual, the temperature level of the real heat dissipation surface retained on the cabin should be consistent with that on orbit. For the real heat dissipation surface B on the original cabin board outer surface (this heat dissipation surface is normally installed during the thermal test, but the heat pipe connected to it has been removed), the heat balance of this surface is as follows Figure 4 As shown;

[0089] Heat dissipation Q4 = external heat flow Q1 + heat transfer from heat pipe Q2 + net heat exchange between other parts and heat dissipation surface Q3 ... Formula ①

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

[0091] Components transfer heat to the outside through heat pipes Q M,c2 Depends on the consistency of the heat pipe heat transfer link. When arranging the heat pipe-heat dissipation surface for thermal testing, 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 the link heat dissipation capacity is the temperature level of the heat dissipation surface for thermal testing. During the thermal test, the temperature level of the heat dissipation surface for thermal testing should be consistent with that on track. For the thermal test simulation heat sink A, the heat balance of this surface is as follows Figure 4 As shown;

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

[0093] In formula ②, the heat leakage Q5' can be controlled to a negligible level by tracking the temperature of the supporting structure, installing thermal insulation, etc. After ignoring this term, the heat balance equation becomes:

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

[0095] In formula ③: heat flux Q1' can be simulated by infrared cage / infrared lamp / heater in thermal test; heat transfer of heat pipe Q2' is unknown, which is passively generated and automatically generated when the temperature level of simulated heat dissipation surface A is determined; the equivalent value of net heat exchange of other parts and real heat dissipation surface Q3' is used to simulate the thermal boundary of the heat dissipation surface on track, which is also unknown; the heat leakage Q5' can be controlled to a negligible degree by tracking temperature control of the support structure and installing thermal insulation. According to the traditional test method, the test is carried out directly with the pre-given Q3'; but the traditional method cannot know the degree of deviation of Q3' from the on-track, and cannot eliminate the simulation error of the heat transfer link of the heat pipe caused by inaccurate Q3'.

[0096] From the above analysis, it can be seen that when using a heat sink-heat pipe system for thermal tests, the traditional method of conducting tests cannot obtain the actual heat transfer Q2 of the heat pipe on track and the equivalent value Q3' of the net heat transfer between other parts and the actual heat sink. Using hypothetical values / simulated values ​​to conduct tests will lead to errors. If the true values ​​of Q2 and Q3' can be accurately obtained, the accuracy of the thermal balance test will be greatly improved.

[0097] For the real heat dissipation surface B of the original cabin outer surface, in the on-orbit state:

[0098] Heat dissipation Q4 = external heat flow Q1 + heat transfer from heat pipe Q2 + net heat exchange between other parts and heat dissipation surface Q3 ... Formula ①

[0099] The following is an analysis of each item in formula ①:

[0100] The first item on the left: heat dissipation Q4 = ε r ·ζ·(TT back ) 4 , ε r -Infrared emissivity of the heat dissipation surface (known), ζ-Boltzmann constant, T back - background temperature, T - the temperature of the heat dissipation surface B. T is generally below 100K, and its influence on the test can be ignored. Therefore, it can be considered that Q4 = ε r ·ζ·T 4 ...Formula ④ is monotonically increasing with respect to T.

[0101] The first item on the right: external heat flux Q1, represents the actual external heat flux absorbed by the heat dissipation surface B itself in orbit and has nothing to do with T.

[0102] The second item on the right: heat transfer amount Q2 of the heat pipe. For heat transfer components such as heat pipes, the influence of the temperature difference of the heat pipe installation interface is considered. When the temperature of the hot end (the temperature of the equipment end) remains basically unchanged, the heat transfer amount is a function related to the temperature of the cold end (the temperature of the heat dissipation surface), that is, Q2 = f(T). When the temperature of the cold end increases, the heat transfer amount through the heat pipe will decrease. It can be considered that Q2 decreases monotonically with respect to T.

[0103] The third item on the right: the net heat exchange between other parts and the heat dissipation surface Q3. Generally, the temperature of the heat dissipation surface will be lower than the surrounding cabin, and the rest of the cabin will transfer heat to it. When the temperature of the heat dissipation surface is higher, the heat transfer around it will be smaller. If this part of the heat transfer is regarded as a function related to the temperature of the heat dissipation surface Q3 = g(T), it can be considered that Q3 decreases monotonically with respect to T.

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

[0105] Q1 = Q1';

[0106] Q2 = Q2';

[0107] Q3 = Q3';

[0108] Q4=Q4'.

[0109] To make Q4 = Q4', simulate the temperature T of the heat sink A A ' should be the same as the temperature T of the actual heat dissipation surface B. In the thermal test, we can calculate Q4 and Q4' by measuring T' and T and substituting them into formula ④.

[0110] In order to make Q2=Q2', Q2' on the simulated heat sink A should be known and this value should be applied to the actual heat sink B as Q2; in formula ③, Q4' after reaching equilibrium is measurable, Q1' and Q3' are actively applied heat, so Q2'=Q4'-Q1'-Q3', which can be calculated by the thermal balance equation of the simulated heat sink A (formula ③).

[0111] In order to make Q3=Q3', Q3 on the actual heat dissipation surface B should be known and this value should be applied to the simulated heat dissipation plate A as Q3'; in formula ②, Q4 after reaching equilibrium is measurable, Q1 and Q2 are actively applied heat, so Q3=Q4-Q1-Q2, which can be calculated through the thermal balance equation of the real heat dissipation surface B (formula ②).

[0112] Obviously, in the thermal test, we need to achieve two sets of equivalent thermal balances, A and B, at the same time. We need to and only need to adjust the values ​​of Q2 actively applied to the real heat dissipation surface B and Q3' on the simulated heat sink A, and make them consistent with the estimated values ​​Q2' and Q3 in the other set of thermal balance.

[0113] For these two quantities that influence each other and have a relationship with each other, the true values ​​of the two can be obtained by iterative approximation. That is, the following steps:

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

[0115] (2) After the thermal equilibrium of the real heat dissipation surface B is reached, Q3 is calculated and applied to A as Q3' to establish the thermal equilibrium of the simulated heat dissipation plate A. After the thermal equilibrium is reached, the new Q2' is calculated;

[0116] (3) At this time, the temperature of the simulated heat sink A and the actual heat sink B may still be slightly different. This is because the new Q2' in the latest equilibrium will be slightly smaller than Q2, so that T' is still slightly smaller than T. Continue to execute the operation in (1), apply the new Q2' as the new Q2 on B, and form a new thermal equilibrium of the actual 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 closer.

[0117] (4) If the temperature difference between plates A and B is still outside the allowable error range, the latest Q3 of the actual heat dissipation surface B is applied to A as the latest Q3' to establish the latest thermal equilibrium of the simulated heat dissipation plate A. At this time, the temperatures of plates A and B will continue to approach each other.

[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, as can the difference between Q3 = Q3'. 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 they are 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 below, specifically including:

[0120] Step 1: Complete the manufacturing 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 external heat flux absorbed by the heat dissipation surface. Given a preset equivalent peripheral heat transfer quantity Q3' (in the first equilibrium, 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 a 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. 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 Q31 > Q3'1 = 0 in the actual situation of the real heat dissipation surface B, at this time, T1 > T'1 and Q41 > Q4'1. T1 can be measured and obtained, and Q41 can be calculated therefrom, 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 yet converged 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 Q4'2 can be calculated therefrom, and then substitute it into Equation ③ to calculate Q2'2.

[0125] Step 5: After the thermal equilibrium in Step 4 is achieved, compare the measured T'2 of the simulated heat dissipation plate with T1 of the actual heat dissipation surface. If |T1 - T'2| < δ, the states of the two are completely equivalent; if |T1 - T'2| > δ, proceed to Step 6. Generally, the value of δ is determined according to the requirements of the test accuracy. In this step, if there is a negligible difference between T'2 and T1 due to weak heat leakage (Q5' in Equation ②), Q5' can be subtracted; use the subtracted T'2 and T1 for calculation and determination.

[0126] Step 6: Let Q22 = Q2'2 in Equation ①. Apply Q22 to the actual heat dissipation plate B in the form of heat instead of Q21. After the thermal equilibrium of this time is reached, since the applied Q22 < Q21, the temperature of the actual heat dissipation surface decreases compared with the previous equilibrium state (T2 < T1), which in turn leads to Q32 > Q31 = Q3'2. Comparing Equation ③ with Equation ①, the difference between the thermal equilibrium state of the simulated heat dissipation plate A this time and the thermal equilibrium state of the actual heat dissipation surface B last time is further reduced.

[0127] Step 7: After the thermal equilibrium in Step 6 is achieved, compare the measured T2 of the actual heat dissipation plate B with T'2 of the simulated heat dissipation plate. If |T2 - T'2| < δ, the states of the two are completely equivalent; if |T2 - T'2| > δ, proceed to Step 8. Generally, the value of δ is determined according to the requirements of the test accuracy. The treatment method for heat leakage Q5' is the same as that in Step 5.

[0128] Step 8: Let Q3'3 = Q32. Repeatedly repeat the process of Steps 4 to 7 until |T n-1 -T' n | < δ or |T n -T' n | < δ. At this time, the states of the simulated heat dissipation plate A and the actual heat dissipation plate B are equivalent, and the temperature T0 of the component M to be evaluated at this time is the temperature of the component after reaching thermal equilibrium.

[0129] Embodiment

[0130] Take the process of conducting a thermal equilibrium test on a payload component of a certain spacecraft as an example to illustrate the specific implementation manner of the present invention. As Figure 5 、 Figure 6 shown in the schematic diagram of the heat pipe for heat conduction and the corresponding heat dissipation surface position in a payload component of a certain spacecraft, there are two types of components K and L in this payload that need to conduct heat to the heat dissipation surface through the heat pipe, and the heat pipe routing is relatively tortuous. Due to configuration limitations, during the thermal equilibrium test, the positions of both types of components K and L are higher than the heat dissipation surface, and it is difficult for the heat pipes to start in the thermal test; if the heat pipes cannot play a heat transfer role, the temperatures of both types of components K and L will be significantly too high, and the purpose of verifying the correctness of the thermal design through the thermal equilibrium test cannot be achieved.

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

[0132] Step 1: Complete the manufacture and assembly of the “heat pipe-heat dissipation surface” system for thermal testing.

[0133] Considering the placement of the load components in the thermal balance test, a thermal test heat pipe was designed and manufactured. A total of 5 main thermal test heat pipes for K and L components are used. Their directions and positions are as follows: Figure 7 , Figure 8 As shown, the conditions satisfied by these heat pipes are as follows:

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

[0135] b) The installation method of the heat pipe for thermal test is the same as that of the original heat pipe, and both are installed on the heat dissipation surface using a pressure plate;

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

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

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

[0139] According to the configuration of the load component, the simulated heat dissipation surface used in the thermal test is designed. In the thermal balance test, one simulated heat dissipation surface is set for each component K and component L. The status is as follows:

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

[0141] b) A heater is attached to the back of the simulated heat dissipation surface to apply heat thereto;

[0142] c) The two simulated heat dissipation surfaces are supported by brackets, which track and control the temperature of the simulated heat dissipation surfaces, and Q5' is relatively small.

[0143] The above conditions are general designs and should be followed when using a heat sink-heat pipe system specifically designed for thermal testing.

[0144] The manufacturing and assembly of the "heat pipe-heat dissipation surface" system used in the thermal test was completed, and it entered the vacuum tank together with the load components for thermal balance testing. A total of three different working conditions (condition 1, condition 2, and condition 3) were carried out in this load test.

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

[0146] Step 2: According to the theoretical heat dissipation surface absorption external heat flux value, apply pure absorption external heat flux Q1' to the simulated heat dissipation plate of component K (** Note) K =13.8W, set the initial equivalent surrounding heat transfer value Q3' 1,K = 24.6W, a pure absorption external heat flux Q1' is applied to the simulated heat sink of component L L =14.4W, set the initial equivalent surrounding heat transfer value Q3' 1,L =38.0W. Waiting for thermal equilibrium to be reached. The average temperature of the simulated heat sink of component K is T' 1,K = +3.8℃, the average temperature of the simulated heat sink of component L is T' 1,L =-1.1℃, thus the heat dissipation Q4' is calculated 1,K =96.3W, Q4' 1,L =80.6W. Substitute Q1' and Q4'1 into formula ③ to calculate the total heat transfer Q2' of the heat pipe to the simulated heat sink in this round 1,K =55.5W, Q2' 1,L =24.7W.

[0147] Step 3: Let Q2 1,K =55.5W, Q2 1,L = 24.6W applied to the actual heat dissipation surface, while the theoretical external heat flux absorption value Q1 K =13.8W, Q1 L = 14.4W is applied to the real heat dissipation surface in the form of heat. Wait for thermal equilibrium to be reached. The average temperature T of the real heat dissipation surface of component K is measured. 1,K =-0.2℃, the average temperature of the actual heat dissipation surface of component L is T 1,L = -2.2℃, from which Q4 is calculated 1,K =91.0W, Q4 1,L =79.2W. Then substitute into formula ① to calculate Q3 1,K =21.7W, Q3 1,L =40.2W.

[0148] Step 4: The states of the real heat sink and the simulated heat sink have not yet converged due to the differences between Q3'1 and Q31. So let Q3' in equation ③ 2,K =Q3 1,K =21.7W, let Q3' 2,L =Q31,L = 40.2W, which is applied to the simulated heat sink in the form of heat. Wait for thermal equilibrium to be reached. Measure the average temperature T' of the simulated heat sink of components K and L 2,K =3.3℃, ​​T' 2,L = 0.1°C, and Q4' is calculated from this 2,K =95.7W, Q4' 2,L =82.0W, and then substitute into formula ③ to calculate Q2' 2,K =57.7W, Q2' 2,L =23.8W.

[0149] Step 5: After the thermal balance in step 4 is achieved, the heat leakage Q5' of the two simulated heat sinks is K =2.4W, Q5' L = 3.5W is deducted from the actual heat exchange amount. After deduction, T' 2,K =1.2℃、T' 2,L = -2.0℃. Compare T'2 of the simulated heat sink with T1 of the real heat sink. If |T1-T'2|<1.5℃, the two states are equivalent. No need to proceed to the next steps.

[0150] The tests were carried out according to the above steps for three thermal balance conditions, and the heat exchange comparison of each part is shown in Table 1. At this time, the simulated heat sink and the real heat sink are equivalent to each other in terms of temperature, heat transfer of heat pipes, and equivalent heat transfer of surrounding structures. The temperature T0 of the tested component reflected in the thermal test is equivalent to the temperature of the heat-generating component using the real heat sink.

[0151] Table 1 Statistics of various heat transfer related to simulated heat sink and real heat sink

[0152]

[0153]

[0154] Since the load components K and L have high temperature stability requirements (component K requires ±0.1℃, component L requires ±0.3℃), high-precision temperature measurement and control related designs are carried out on the components. The accuracy of the heat dissipation boundary is very critical to whether it can successfully achieve thermal control indicators. The method described in the present invention is used to carry out experiments, taking working condition 1 as an example.

[0155] like Fig. 9 , Fig.10 As shown in Figure 1, the temperature curves of different parts of components K and L after the final thermal equilibrium is achieved. The test results are consistent with the simulation analysis, and the test proves that the thermal control measures for the above components can meet their temperature stability requirements.

[0156] Thus, by setting up a heat pipe and heat dissipation surface system dedicated to the thermal test and carrying out iterative approximation tests using the method of the present invention, the on-orbit temperature boundary is well simulated, solving the problems of accuracy and effectiveness of the thermal test.

[0157] Although the present invention has been disclosed as above in the form of a preferred embodiment, it is not intended to limit the present invention. Any person skilled in the art may make possible changes and modifications to the technical solution of the present invention by using the methods and technical contents disclosed above without departing from the spirit and scope of the present invention. Therefore, any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention shall fall within the protection scope of the technical solution of the present invention.

[0158] The contents not described in detail in the specification of the present invention belong to the common knowledge of those skilled in the art.

Claims

1. An iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system, characterized in that include: Manufacture and assemble the heat dissipation surface and heat pipe system for thermal testing, set up simulated heat dissipation plates in the heat dissipation surface and heat pipe system, and construct a thermal test configuration; Conduct thermal analysis on simulated heat sinks and real heat sinks in thermal test configurations; According to the thermal analysis results, an external heat flux is applied to the simulated heat sink and a preset equivalent peripheral heat transfer amount is given; After measuring the thermal equilibrium, the temperature parameters of the simulated heat sink are used to calculate the heat dissipation of the simulated heat sink, and the current heat transfer of the heat pipe is calculated based on the heat dissipation; Apply the calculated heat pipe heat transfer and theoretical external heat flux of the simulated heat sink to the real heat sink. 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. Calculate the equivalent value of the net heat exchange of the actual heat dissipation surface according to the heat dissipation of the actual heat dissipation plate; The equivalent value of the net heat exchange of the real heat dissipation surface is applied to the simulated heat dissipation plate in the form of heat. When the simulated heat dissipation plate achieves thermal equilibrium, the temperature parameters of the simulated heat dissipation plate are measured to calculate the heat dissipation of the simulated heat dissipation plate in this thermal equilibrium; Calculate the current heat transfer amount of the heat pipe based on the heat dissipation of the simulated heat sink thermal balance; The temperature parameters of the simulated heat sink are measured and compared with the temperature parameters of the real heat sink. According to the comparison results, it is determined whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test. Otherwise, the thermal test is continued. Apply the current heat transfer amount of the heat pipe to the real heat sink, measure the temperature parameters of the real heat sink after thermal equilibrium, and compare them with the temperature parameters of the simulated heat sink. According to the comparison results, determine whether the simulated heat sink and the real heat sink are equivalent. If they are equivalent, end the test and use the current temperature parameters of the thermal test configuration as the final temperature result of the thermal equilibrium test, otherwise continue the thermal test; Repeat the calculation of the heat pipe heat transfer of the simulated heat sink under the thermal equilibrium state and the comparison of the corresponding double-plate temperature parameters after the heat pipe heat transfer is applied until the simulated heat sink and the real heat sink are completely equivalent. The current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal balance test.

2. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 1, characterized in that: The method for thermal analysis of simulated heat sink and real heat sink is: For the thermal test configuration, a heat balance equation is established based on any component to determine the relationship between the heat dissipation and the external heat flux, the heat transfer of the heat pipe and the net heat exchange with the heat dissipation surface; the external heat flux is simulated by external heating, and the net heat exchange with the heat dissipation surface is automatically generated after the heat dissipation surface temperature parameters are determined; the heat transfer of the heat pipe is determined based on the selected heat pipe simulation; there is heat leakage in the thermal test configuration, and during the thermal test, the sum of the heat dissipation and the heat leakage is equivalent to the sum of the external heat flux, the heat transfer of the heat pipe and the net heat exchange with the heat dissipation surface.

3. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 2, characterized in that: The amount of heat leakage is controlled by tracking the temperature of the support structure of the thermal test configuration or by heat insulation installation to achieve negligible heat leakage.

4. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 2, characterized in that: The simulated heat sink and the real heat sink have the following heat dissipation: Q4 = ε r ·ζ·(TT back ) 4 In the formula, ε r -Infrared emissivity of the heat dissipation surface (known), ζ-Boltzmann constant, T back -background temperature, T-temperature of heat dissipation surface B; The external heat flux Q1 is the actual external heat flux absorbed by the heat dissipation surface in orbit, which has nothing to do with the temperature of the heat dissipation surface itself; The heat transfer amount Q2 of the heat pipe is affected by the temperature difference of the heat pipe installation interface. When the temperature at the equipment end remains unchanged, the heat transfer amount is related to the heat dissipation surface temperature; when the heat dissipation surface temperature increases, the heat transfer amount of the heat pipe decreases, and the heat transfer amount Q2 of the heat pipe decreases monotonically with respect to the heat dissipation surface temperature; The net heat exchange amount Q3 between the heat sink and the heat dissipation surface decreases monotonically with respect to the heat dissipation surface temperature.

5. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 4, characterized in that: The heat dissipation condition of any component of the thermal test configuration reaches a thermal equilibrium state after being consistent with the on-orbit state, wherein: Under the thermal equilibrium state, the measured temperature parameters of the simulated heat sink are the same as those of the real heat sink. The heat transfer of the heat pipe of the simulated heat sink is applied to the actual heat sink, and the net heat exchange between other parts of the real heat sink and the heat dissipation surface is applied to the simulated heat sink. For any heat sink, the heat dissipation is the sum of the external heat flux, the heat transfer of the heat pipe, and the net heat exchange between other parts and the heat dissipation surface.

6. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 4, characterized in that: The thermal equilibrium state of the simulated heat sink and the thermal equilibrium state of the real heat sink are achieved by adjusting the heat transfer amount of the heat pipe actively applied to the real heat sink and the net heat exchange amount with the heat dissipation surface actively applied to the simulated heat sink, and keeping them consistent with the heat transfer amount of the heat pipe and the net heat exchange amount with the heat dissipation surface in another corresponding group of thermal equilibrium states.

7. The iterative approximation thermal balance test method for a heat test heat dissipation surface and a heat pipe system according to claim 4, characterized in that: The method for obtaining the heat transfer amount Q2 of the heat pipe actively applied to the real heat sink and the net heat exchange amount Q3' of the heat sink actively applied to the simulated heat sink is: Let Q3'=0, when simulating the thermal equilibrium state of heat sink A, calculate the current heat transfer amount Q2' of the heat pipe actively applied to the simulated heat sink, so that the real heat sink B enters the thermal equilibrium state; Calculate the equivalent value Q3 of the net heat transfer of the real heat dissipation surface as the net heat transfer Q3' of the simulated heat dissipation surface and apply it to the simulated heat dissipation plate A. When the simulated heat dissipation plate achieves the second thermal equilibrium, calculate the current heat transfer Q2' of the heat pipe under the new thermal equilibrium state. Apply the current heat transfer amount Q2' of the heat pipe in the new thermal equilibrium state to the real heat sink B to form a new thermal equilibrium state of the real heat sink B; If the temperature parameter difference between the simulated heat sink A and the real heat sink B in the current state is outside the allowable error range, the latest real heat sink net heat exchange equivalent value Q3 of the real heat sink B is applied to the simulated heat sink A as the latest heat exchange equivalent value, and the third thermal equilibrium state of the simulated heat sink is established. The judgment of the temperature parameter difference and the allowable error range is repeated to achieve optimization iteration between the real heat sink net heat exchange equivalent value Q3 and the simulated heat sink net heat exchange Q3', 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.

8. The iterative approximation thermal balance test method for heat dissipation surface and heat pipe system of thermal test according to claim 7, characterized in that: The method for measuring the temperature parameters of the actual heat sink after thermal equilibrium and comparing them with the temperature parameters of the simulated heat sink is as follows: After achieving the second thermal equilibrium of the simulated heat sink, 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 comparative relationship between |T1-T'2| and δ is judged. If |T1-T'2|>δ, the current heat transfer amount of the heat pipe is applied to the real heat sink, and the comparative judgment is continued after thermal equilibrium; if |T1-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, and the test is terminated and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test.

9. The iterative approximation thermal balance test method for heat dissipation surface and heat pipe system of thermal test according to claim 8, characterized in that: The current heat transfer amount of the heat pipe is applied to the real heat sink. When the real heat sink achieves thermal equilibrium for the second time, the temperature parameters of the real heat sink are measured and compared with the temperature parameters of the simulated heat sink, including the temperature T2 of the simulated heat sink and the temperature T'2 of the simulated heat sink. If |T2-T'2|<δ, the simulated heat sink and the real heat sink are equivalent, the test is terminated, and the current temperature parameters of the thermal test configuration are used as the final temperature results of the thermal equilibrium test; if |T2-T'2|>δ, the heat transfer amount of the simulated heat sink under thermal equilibrium state is calculated, and the corresponding double-plate temperature parameters are compared after the heat transfer amount of the heat pipe is applied, until the simulated heat sink and the real heat sink are completely equivalent, that is, |T n-1 -T' n |<δ or |T n -T' n |<δ.

10. The iterative approximation thermal balance test method for heat dissipation surface and heat pipe system of thermal test according to claim 9, characterized in that: The comparison value δ is determined according to the accuracy requirements of the thermal test; there is heat leakage in the thermal test configuration, which leads to differences between the temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink. The temperature T'2 of the simulated heat sink and the temperature T1 of the real heat sink are subtracted by heat leakage parameters to reduce the differences and the impact on the comparison of temperature parameters.

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