Centrifugal gain type involute heat pipe design method

Abstract

The centrifugal gain type involute heat pipe design method comprises the steps that platform configuration and heat source distribution are optimized, and the farthest distance between a heat source and the rotating center of a rotating platform is determined; optimizing the configuration and layout of the heat pipe, controlling the distance between the heat pipe and the rotation center to be gradually reduced from the hot end to the cold end, and controlling the acting force of the rotation acceleration on the heat pipe to be always in the liquid backflow direction; optimizing the configuration and layout of the heat pipe, and controlling the heat pipe to be a linear section from a bubble nucleation point to an initial liquid level position; calculating the proportion of the working medium pressure difference caused by the accelerated speed of the heat pipe to the capillary force pressure difference of the heat pipe at the working rotating speed; and evaluating whether the heat pipe indexes meet task requirements. According to the method, the limit heat transfer capacity of the heat pipe can be improved, the influence of the rotation acceleration on starting of the heat pipe is reduced, the temperature control requirement of high-heat-consumption equipment of a satellite rotating platform is met, and meanwhile the invention further provides a ground verification method for the performance of the involute heat pipe.

Description

Technical Field

[0001] The invention relates to the technical field of heat dissipation optimization of a rotating platform of a ring-sweeping spacecraft, and in particular to a design method of a centrifugal gain type involute heat pipe. Background Art

[0002] High-efficiency heat transfer technology can effectively solve the problem of equipment overheating caused by local heat concentration in spacecraft, and is an important means of spacecraft thermal control. It mainly includes heat pipe technology, fluid circuit technology, and heat transfer products such as heat-conducting copper strips, heat-conducting cables, and heat expansion plates. Heat pipe products such as axial groove heat pipes are widely used in the field of spacecraft thermal control due to their advantages such as high efficiency of heat transfer and high reliability of pure passive operation.

[0003] The new scanning satellite payload platform has the property of high-speed rotation, and the rotation will produce an acceleration effect on the heat pipe that relies on the capillary groove to generate driving force. When the driving force generated by the acceleration effect is contrary to the capillary driving force and the acceleration driving force is greater, the heat pipe function will be completely ineffective. When the driving force generated by the acceleration effect and the capillary driving force are in the same direction, the heat transfer capacity of the heat pipe will be improved. However, due to the accumulation effect of the liquid working medium, it will affect the start-up of the heat pipe. In severe cases, the liquid working medium in the heat pipe will accumulate completely and cannot be started. Therefore, special attention should be paid to the selection of heat pipes for the rotating payload platform of the spacecraft.

[0004] For example, the 2-meter-diameter circular instrument mounting plate of the Fengyun-2 satellite adopts a design method of pre-buried arc-shaped heat pipes, so that the distance from the rotation center of each part of the heat pipe is basically the same, and the radius of the hot end is slightly larger than the radius of the cold end, thereby weakening the acceleration effect of the rotation of the whole satellite on the heat pipe and ensuring the normal operation of the heat pipe in the rotating state. However, for new circumscanning satellites, the size limit of the rotating platform cannot meet the design conditions of arc-shaped heat pipes, and the thermal control design of high heat consumption electronic equipment has put forward higher requirements on the heat transfer capacity of the heat pipe.

[0005] The compact rotating platform of the spacecraft cannot meet the layout conditions of the annular heat pipe because the rotation center is close to the short side of the platform. In addition, the heat consumption of the electronic equipment on the payload platform is large and concentrated, which is higher than the limit heat transfer capacity of the optional axial groove heat pipe. Therefore, it is urgent to explore and study the heat transfer technology that can adapt to and utilize this type of spacecraft rotating payload platform. Summary of the invention

[0006] In order to solve the technical problems existing in the above-mentioned prior art, the purpose of the present invention is to provide a centrifugal gain involute heat pipe design method, which can improve the ultimate heat transfer capacity of the heat pipe, reduce the influence of rotation acceleration on the start-up of the heat pipe, and meet the temperature control requirements of high heat consumption equipment of the satellite rotating platform. A ground verification method for the performance of the involute heat pipe is also proposed.

[0007] To achieve the above-mentioned object of the invention, the present invention provides a centrifugal gain involute heat pipe design method, comprising the following steps:

[0008] Step S1, optimizing the platform configuration and heat source distribution, and determining that the distance between the heat source and the rotation center of the rotating platform is the farthest;

[0009] Step S2, optimizing the configuration and layout of the heat pipe, controlling the distance between the heat pipe and the rotation center to gradually decrease from the hot end to the cold end, and controlling the force of the rotation acceleration on the heat pipe to always be in the direction of liquid reflux;

[0010] Step S3, optimizing the configuration and layout of the heat pipe, and controlling the heat pipe to be a straight line segment from the bubble nucleation point to the initial liquid surface position;

[0011] Step S4, calculating the ratio of the working fluid pressure difference caused by the acceleration of the heat pipe to the capillary pressure difference of the heat pipe at the working speed;

[0012] Step S5, evaluating whether the heat pipe index meets the task requirements, if not, repeating steps S2 to S5 until the heat pipe index meets the task requirements.

[0013] According to a technical solution of the present invention, after the heat pipe index meets the task requirements, it also includes:

[0014] Step S6, using the involute heat pipe centrifugal test system to complete the heat pipe index verification, specifically including:

[0015] Step S61, constructing a test system and completing initial preparations;

[0016] Step S62, completing the ultimate heat transfer capacity test;

[0017] Step S63, completing the startup performance test;

[0018] Wherein, the test system includes: a level adjustment system, a cooling system, an acceleration simulation system and a data acquisition system.

[0019] According to a technical solution of the present invention, the step S1 specifically includes:

[0020] Step S11: According to the task characteristics, the rotating platform structure is preliminarily determined through mechanical and thermal integration design, and a heat pipe installation interface is reserved;

[0021] Step S12, determining the rotation center of the rotating platform;

[0022] Step S13: determine the maximum distance between the heat source and the rotation center of the rotating platform.

[0023] According to a technical solution of the present invention, in step S2, the force exerted by the rotational acceleration on the heat pipe is always controlled along the liquid reflux direction, and the centrifugal force direction vector of different positions of the heat pipe is Direction of the tangent vector to the centerline of the heat pipe Satisfies the following relationship:

[0024]

[0025] According to a technical solution of the present invention, in step S3, based on step S2, the control vector and The angle θ between them increases from the bubble nucleation point to the liquid surface.

[0026] According to a technical solution of the present invention, in step S4, the ratio of the additional pressure head of the heat pipe caused by acceleration to the capillary pressure head of the heat pipe is expressed as:

[0027]

[0028] Where ΔP a is the additional pressure head caused by acceleration; ρ is the working fluid density; is the acceleration vector; ΔP c is the capillary pressure difference.

[0029] According to a technical solution of the present invention, the step S61 specifically includes:

[0030] Step S611, calibration and calibration of instruments and measuring systems: calibrate the power supply, data acquisition instrument, acceleration sensor in the test system, calibrate the temperature measurement system, and eliminate control and measurement errors;

[0031] Step S612, adjustment and inspection of the horizontality of the heat pipe: using a motion camera and laser radiation method to measure the horizontality of the heat pipe during rotation, and iteratively adjusting until the test system meets the horizontality requirement in a high-speed rotation state;

[0032] Step S613, thermal insulation implementation and environmental heat leakage assessment: thermally insulate the heat pipe to be tested, control the heat pipe to operate at different temperatures to be tested by adjusting the load, and measure the heat leakage of the test system in static and rotating states.

[0033] According to a technical solution of the present invention, the step S62 specifically includes:

[0034] Step S621, raising the hot end of the heat pipe by 0.1-2 mm;

[0035] Step S622, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements;

[0036] Step S623, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements;

[0037] Step S624, adjusting the hot end load power in steps, iteratively adjusting the platform acceleration of the acceleration simulation system, controlling the operating temperature of the heat pipe to achieve a temperature difference of more than 5° C. between the hot end and the cold end of the heat pipe, and recording the ultimate heat transfer capacity of the heat pipe under this acceleration environment and operating temperature;

[0038] Step S625, repeat the above steps to test the ultimate heat transfer capacity of the involute heat pipe at different operating temperatures under different acceleration environments.

[0039] According to a technical solution of the present invention, the step S63 specifically includes:

[0040] Step S631, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements;

[0041] Step S632, maintaining the rotation speed for 8-15 minutes until the distribution of the working medium gas and liquid in the heat pipe reaches a new equilibrium;

[0042] Step S633, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements;

[0043] Step S634, gradually adjusting the hot end load power from small to large, and judging the minimum starting power required by the heat pipe at the corresponding speed according to the temperature changes of each measuring point of the heat pipe;

[0044] Step S635, adjusting the rotation speed according to the task requirements, and repeating the steps S631 to S634 to test the minimum starting power required by the involute heat pipe at different operating temperatures under different acceleration environments.

[0045] According to one aspect of the present invention, there is provided an involute heat pipe designed by using the centrifugal gain involute heat pipe design method as described in any one of the above technical solutions, and the heat pipe is suitable for a rotating platform.

[0046] Compared with the prior art, the present invention has the following beneficial effects:

[0047] The present invention proposes a centrifugal gain involute heat pipe design method, which uses the centrifugal acceleration generated by the platform rotation to break through the ultimate heat transfer capacity of the heat pipe while reducing the negative impact of the centrifugal acceleration on the start-up of the heat pipe, and realizes the development demand of the spacecraft compact rotating platform thermal control system for low start-up heat flow and higher heat transfer capacity heat pipes, and is a purely passive method with high reliability.

[0048] The horizontality measurement of the heat pipe during the ground test is achieved by the method of "motion camera + laser radiation". The method is simple, reliable and has low measurement cost.

[0049] Overcome the systemic condition limitations such as the condensing water temperature range and heat source power of the verification system through the method of "relative calibration and strict prediction";

[0050] Through the ground verification system, the speed, heating power, and heat pipe operating temperature can be controlled during high-speed rotation, and the test data can be measured and transmitted in real time. At the same time, the test verification and in-depth research on the heat pipe's ultimate heat transfer capacity, starting performance, and failure mode with speed, heat source position, and heat pipe operating temperature as influencing factors are also realized. This verification method has the advantages of high reliability, high applicability, and high scalability. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention, and for ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0052] Figure 1 Schematically showing a schematic diagram of a gradual heat pipe structure of a rotating load platform in an embodiment of the present invention;

[0053] Figure 2 A schematic diagram showing the composition of a heat pipe ground test verification system in an embodiment of the present invention;

[0054] Figure 3 Schematically showing the layout of heat pipes, heat sources and cold sources of the heat pipe ground test verification system in an embodiment of the present invention;

[0055] Figure 4 A schematic diagram of a heat pipe ground test verification method according to an embodiment of the present invention is shown;

[0056] Figure 5 A flow chart of a centrifugal gain involute heat pipe design method in an embodiment of the present invention is schematically shown. DETAILED DESCRIPTION

[0057] The description of the embodiments of this specification should be combined with the corresponding drawings, which should be considered as part of the complete specification. In the drawings, the shape or thickness of the embodiments may be enlarged and indicated for simplification or convenience. Furthermore, the parts of each structure in the drawings will be described separately. It is worth noting that the elements not shown in the drawings or not described in words are in a form known to ordinary technicians in the relevant technical field.

[0058] The description of the embodiments herein and any reference to directions and orientations are only for the convenience of description and are not to be construed as any limitation on the scope of protection of the present invention. The following description of the preferred embodiments may involve combinations of features, which may exist independently or in combination, and the present invention is not particularly limited to the preferred embodiments. The scope of the present invention is defined by the claims.

[0059] like Figures 1 to 5 As shown, a centrifugal gain involute heat pipe design method of the present invention comprises the following steps:

[0060] Step S1, optimizing the platform configuration, such as the example trapezoidal platform structure, optimizing the heat source distribution, and determining that the distance between the heat source and the rotation center 2 of the rotating platform is the farthest, specifically including:

[0061] Step S11, according to the task characteristics, the rotating platform structure is preliminarily determined through mechanical and thermal integration design, and the installation interface of the heat pipe 1 is reserved;

[0062] Step S12, determining the rotation center 2 of the rotating platform;

[0063] Step S13, determining the maximum distance between the heat source and the rotation center 2 of the rotating platform, Figure 1 In the figure, the distances between the heat pipe 1 and the rotation center 2 are represented by R 1 , R 2 and R 3 , where R 3 For the longest distance.

[0064] Step S2, optimizing the configuration and layout of the heat pipe 1, controlling the distance between the heat pipe and the rotation center 2 to gradually decrease from the hot end to the cold end, and controlling the force of the rotation acceleration on the heat pipe to always be along the liquid reflux direction;

[0065] Control the force of the rotation acceleration on the heat pipe to always be in the direction of liquid return, then the direction vector of the centrifugal force at different positions of the heat pipe is Direction of the tangent vector to the centerline of the heat pipe Satisfies the following relationship:

[0066]

[0067] Step S3, optimize the heat pipe configuration and layout, control the heat pipe along the bubble nucleation point to the initial liquid surface position is a straight line segment, based on step S2, control vector and The angle θ between them increases from the bubble nucleation point to the liquid surface position;

[0068] Control the centrifugal force direction vector at different positions of the heat pipe Direction of the tangent vector to the centerline of the heat pipe Satisfying equation (1), the force of the rotation acceleration on the heat pipe is always controlled in the direction of liquid reflux, promoting the reflux of liquid working medium and improving the ultimate heat transfer capacity of the heat pipe; the distance between the heat pipe and the rotation center 2 is controlled to gradually decrease from the hot end to the cold end, ensuring that when the working medium condenses and refluxes, there is no accumulation effect at any position in the middle of the heat pipe under the action of centrifugal force. The principle is as follows Figure 1 As shown, Figure 1 The direction of the arrow in is the direction of the working fluid return flow.

[0069] From equations (2) and (3), it can be seen that the heat flux Q required for the internal liquid working medium to reach the initial boiling state at the start-up time of the heat pipe affected by centrifugal acceleration is start The acceleration at different positions between the working fluid bubble nucleation point and the liquid surface With length Δ The present invention optimizes the configuration of the heat pipe 1, and the liquid level is located at Figure 1 In the straight line segment shown, from the bubble nucleation area to the liquid surface, while ensuring that the centrifugal force on the working fluid is significantly reduced, the vector and The angle θ between them is also significantly reduced, which effectively controls the influence of the tail term of formula (3) on the critical superheat and reduces the influence of centrifugal acceleration on the initial boiling heat flow required for the start-up of the heat pipe 1.

[0070]

[0071] Where: l e (m) is the length of the evaporation section; k eff (W / m·K) is the thermal conductivity of the heat pipe shell; D in (m) Inner diameter of heat pipe shell; D v (m) is the diameter of the steam channel; ΔT cr (K) is the critical superheat, which can be expressed as:

[0072]

[0073] Where: T v (K) is the temperature of the gaseous working fluid; L (J / kg) is the latent heat of gasification of the working fluid; ρ v (kg / m 3 ) is the density of gaseous working fluid; ρ l (kg / m 3 ) is the density of the liquid working fluid; σ (N / m) is the surface tension; (m / s 2 ) The acceleration vector caused by the centrifugal force; R m (m) The radius of the meniscus of the liquid column; R n(m) The radius of the bubble core at the initial boiling; the tail term is the integral of the dot product of the acceleration vector and the length vector from the bubble nucleation point to the liquid surface.

[0074] Step S4: Under the action of acceleration, the height difference of the liquid or gas inside the heat pipe will generate an acceleration pressure difference, thereby causing a working fluid pressure difference; the ratio of the additional pressure head caused by the acceleration of the heat pipe to the capillary pressure head of the heat pipe at the working speed is calculated, which is expressed as:

[0075]

[0076] Where ΔP a is the additional pressure head caused by acceleration; ρ is the working fluid density; is the acceleration vector; ΔP c is the capillary pressure difference.

[0077] For example, when ω=2.512 rad / s, the acceleration pressure difference of the exemplary heat pipe is 230.9% of the capillary pressure difference.

[0078] Step S5, evaluating whether the heat pipe index meets the task requirements, if not, repeating steps S2 to S5 until the heat pipe index meets the task requirements.

[0079] The present invention optimizes the heat pipe configuration and controls the heat source layout so that the heat pipe can break through the inherent static heat transfer capacity of the heat pipe under the action of acceleration, while effectively reducing the influence of acceleration on the start-up of the heat pipe, thereby meeting the temperature control requirements of high heat consumption equipment of the satellite rotating platform.

[0080] In some embodiments of the present invention, Figure 4 As shown, after the heat pipe indicators meet the mission requirements, it also includes:

[0081] Step S6, using the involute heat pipe centrifugal test system to complete the heat pipe index verification, specifically including:

[0082] Step S61: construct a test system and complete initial preparations, including:

[0083] Step S611, calibration and calibration of instruments and measuring systems: calibrate the power supply, data acquisition instrument 13, and acceleration sensor in the test system, calibrate the temperature measurement system, and eliminate control and measurement errors;

[0084] Step S612, adjustment and inspection of the horizontality of the heat pipe: using a motion camera and laser radiation method to measure the horizontality of the heat pipe during rotation, and iteratively adjusting until the test system meets the horizontality requirement in a high-speed rotation state;

[0085] Step S613, thermal insulation implementation and environmental heat leakage assessment: thermally insulate the heat pipe to be tested, control the heat pipe to operate at different temperatures to be tested by adjusting the load, and measure the heat leakage of the test system in static and rotating states.

[0086] Step S62, completing the ultimate heat transfer capacity test, specifically including:

[0087] Step S621, applying the proposed "relative calibration, strict prediction" method to raise the hot end of the heat pipe by 0.1 to 2 mm, preferably 1 mm;

[0088] Step S622, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements;

[0089] Step S623, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements;

[0090] Step S624, adjusting the hot end load power in steps, iteratively adjusting the platform acceleration of the acceleration simulation system, controlling the operating temperature of the heat pipe to achieve a temperature difference of more than 5° C. between the hot end and the cold end of the heat pipe, and recording the ultimate heat transfer capacity of the heat pipe under this acceleration environment and operating temperature;

[0091] Step S625, repeat the above steps to test the ultimate heat transfer capacity of the involute heat pipe at different operating temperatures under different acceleration environments.

[0092] Step S63: completing the startup performance test, specifically including:

[0093] Step S631, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements;

[0094] Step S632, maintaining the rotation speed for 8-15 minutes, preferably 10 minutes, until the distribution of the working medium gas and liquid in the heat pipe reaches a new equilibrium;

[0095] Step S633, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements;

[0096] Step S634, gradually adjust the hot end load power from small to large, and determine the minimum starting power required for the heat pipe at the corresponding speed according to the temperature changes of each measuring point of the heat pipe; adjust the hot end load power by small step adjustment.

[0097] Step S635, adjusting the rotation speed according to the task requirements, and repeating the steps S631 to S634 to test the minimum starting power required by the involute heat pipe at different operating temperatures under different acceleration environments.

[0098] The test system includes: a level adjustment system, a cooling system II, an acceleration simulation system III and a data acquisition system. The acceleration simulation system III is composed of a control computer 11 and sensors, which can realize the control and feedback of the platform rotation acceleration; the heat source and data acquisition system I is composed of a data acquisition instrument 13, a junction box 14, a power supply 15 and a computer 4 and is integrated in the centrifugal test platform, which can realize temperature collection and heat source power control during the platform rotation process; the cooling system II is composed of a cooling water tank 5, a flow meter 8, a mechanical pump 9, a control valve 6 and is integrated in the centrifugal test platform 10, which can realize the application of the cold source at the cold end of the heat pipe and temperature control during the platform rotation. Figure 2 and Figure 3 As shown, Figure 2 In the figure, T101 to T108 represent the temperature measurement points, specifically:

[0099] (1) Level adjustment system: The measurement and guarantee of the level of the heat pipe during the rotation process is a key factor in the verification test, providing a horizontal rotating platform without gravity for the test heat pipe. The level adjustment system consists of a level, a laser terminal, a motion camera, a support structure, a tooling structure, fasteners, and adjustment materials. Limited by the influence of the platform rotation, the gravity level is distorted under the action of centrifugal force and cannot measure the level of the test system during the rotation process. Therefore, a "motion camera + laser radiation" method is proposed to achieve the measurement and calibration of the level of the heat pipe under the rotating state. The specific method is as follows: First, the test system in a static state is calibrated by a gravity level, and then the laser device is fixed to the test system. The position of the ray terminal when the test platform is not rotated and is at the initial angles of 0°, 45°, 90°, 135°, 180°, 225°, 270°, and 315° is recorded by laser emission. The motion camera combined with the laser device is used to record the position of the ray terminal when the test platform passes through the corresponding angle during the movement of the test platform. The level control of the heat pipe on the test system is completed by comparing the position offset. This constitutes a level adjustment and testing system.

[0100] (2) Cooling system II: The heat transfer and dissipation of the test system in the rotating state is realized by cooling system II, which consists of a cooling water tank 5, a flow meter 8, a mechanical pump 9, a control valve 6, a filter 7, a condenser, etc. The heat dissipation capacity of the system is controlled by adjusting the water tank temperature and the cooling water flow driven by the pump; the test system is cooled by heat exchange between the condenser and the cold end of the heat pipe.

[0101] (3) Acceleration simulation system III: The application and adjustment of the rotational angular velocity of the test system are realized by the acceleration simulation system III, which consists of a frequency converter, a protection device, a main motor, a rotating arm, a liquid conversion device, an electrical signal conversion device, a junction box, a control computer 11, etc. The platform is rotated at an adjustable speed through the control computer, the main motor and the frequency converter; the application of cooling water during rotation is realized through the liquid conversion device; the application of heat source power and temperature collection during rotation are realized through the electrical signal conversion device.

[0102] (4) Data acquisition system: The heat source application and temperature information visualization of the test system are realized by the data acquisition system, which consists of a DC power supply, an electric heater, a data acquisition instrument 13, a Pt100 temperature sensor and a sensor controller 12, a computer, etc. Through the electrical signal conversion device, the heating, control and temperature data collection and recording of the test heat pipe in the rotating state are realized.

[0103] The hot end load power is limited due to factors such as the limited effective cooling area of ​​the cold end caused by the platform and the size of the heat pipe, the anti-freezing of the cooling water temperature, and the upper limit of the operating temperature of the electric heater. Therefore, a "relative calibration, strict prediction" method is proposed to calibrate the heat transfer capacity of the rotating heat pipe and predict the starting power. The specific method is as follows: when measuring the change in the heat transfer capacity of the heat pipe caused by acceleration, the hot end is raised by 1mm to suppress the reflux of the liquid working fluid. By measuring the heat transfer capacity of the heat pipe without acceleration, it is compared with the standard heat transfer capacity of the heat pipe at the corresponding temperature to obtain the calibration coefficient A. When conducting heat transfer capacity tests under different acceleration environments, the obtained results are corrected by the calibration coefficient A; when measuring the starting load of the heat pipe caused by acceleration, the cold end is raised by 1mm, the accumulation degree of the liquid working fluid at the hot end is tightened, and the required starting load power is predicted more strictly.

[0104] The heat source control, temperature measurement and cooling system II control of the test system are all integrated into the centrifugal test machine platform, which can simultaneously realize the control of the speed, heat source power, cold end temperature and the real-time collection of parameters such as temperature, flow, and current. During the test, the temperature distribution of the heat pipe can be used to determine the relative relationship between its heat transfer capacity, failure mode, startup heat flow and other performance parameters driven by centrifugal force and independent variables such as speed, heat pipe configuration, and heat source position.

[0105] According to one aspect of the present invention, there is provided an involute heat pipe designed by using the centrifugal gain involute heat pipe design method as described in any one of the above technical solutions, and the heat pipe is suitable for a rotating platform.

[0106] It should be noted that, in this article, the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, article or terminal device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or terminal device. In the absence of further restrictions, the elements defined by the sentence "comprises a ..." do not exclude the existence of other identical elements in the process, method, article or terminal device including the elements.

[0107] Finally, it should be noted that the above is a preferred embodiment of the present invention. It should be pointed out that although the preferred embodiment of the present invention has been described, for those skilled in the art, once the basic creative concept of the present invention is known, several improvements and modifications can be made without departing from the principles of the present invention, and these improvements and modifications should also be regarded as the protection scope of the present invention. Therefore, the attached claims are intended to be interpreted as including the preferred embodiment and all changes and modifications that fall within the scope of the embodiments of the present invention.

Claims

1. A centrifugal gain involute heat pipe design method, characterized in that: The following steps are involved: Step S1, optimizing the platform configuration and heat source distribution, and determining that the distance between the heat source and the rotation center of the rotating platform is the farthest; Step S2, optimizing the configuration and layout of the heat pipe, controlling the distance between the heat pipe and the rotation center to gradually decrease from the hot end to the cold end, and controlling the force of the rotation acceleration on the heat pipe to always be in the direction of liquid reflux; Step S3, optimizing the configuration and layout of the heat pipe, and controlling the heat pipe to be a straight line segment from the bubble nucleation point to the initial liquid surface position; Step S4, calculating the ratio of the working fluid pressure difference caused by the acceleration of the heat pipe to the capillary pressure difference of the heat pipe at the working speed; Step S5, evaluating whether the heat pipe index meets the task requirements, if not, repeating steps S2 to S5 until the heat pipe index meets the task requirements.

2. The centrifugal gain involute heat pipe design method according to claim 1, characterized in that: After the heat pipe indicators meet the mission requirements, it also includes: Step S6, using the involute heat pipe centrifugal test system to complete the heat pipe index verification, specifically including: Step S61, constructing a test system and completing initial preparations; Step S62, completing the ultimate heat transfer capacity test; Step S63, completing the startup performance test; Wherein, the test system includes: a level adjustment system, a cooling system, an acceleration simulation system and a data acquisition system.

3. The centrifugal gain involute heat pipe design method according to claim 1, characterized in that: The step S1 specifically includes: Step S11: According to the task characteristics, the rotating platform structure is preliminarily determined through mechanical and thermal integration design, and a heat pipe installation interface is reserved; Step S12, determining the rotation center of the rotating platform; Step S13: determine the maximum distance between the heat source and the rotation center of the rotating platform.

4. The centrifugal gain involute heat pipe design method according to claim 3, characterized in that: In step S2, the force exerted by the rotational acceleration on the heat pipe is controlled to always be in the direction of liquid reflux, and the direction vector of the centrifugal force exerted on different positions of the heat pipe is Direction of the tangent vector to the centerline of the heat pipe Satisfies the following relationship:

5. The centrifugal gain involute heat pipe design method according to claim 4, characterized in that: In step S3, based on step S2, the control vector and The angle θ between them increases from the bubble nucleation point to the liquid surface.

6. The centrifugal gain involute heat pipe design method according to claim 5, characterized in that: In step S4, the ratio of the additional pressure head of the heat pipe caused by acceleration to the capillary pressure head of the heat pipe is expressed as: Among them, ΔP a is the additional pressure head caused by acceleration; ρ is the working fluid density; is the acceleration vector; ΔP c is the capillary pressure difference.

7. The centrifugal gain involute heat pipe design method according to claim 2, characterized in that: The step S61 specifically includes: Step S611, calibration and calibration of instruments and measuring systems: calibrate the power supply, data acquisition instrument, acceleration sensor in the test system, calibrate the temperature measurement system, and eliminate control and measurement errors; Step S612, adjustment and inspection of the horizontality of the heat pipe: using a motion camera and laser radiation method to measure the horizontality of the heat pipe during rotation, and iteratively adjusting until the test system meets the horizontality requirement in a high-speed rotation state; Step S613, thermal insulation implementation and environmental heat leakage assessment: thermally insulate the heat pipe to be tested, control the heat pipe to operate at different temperatures to be tested by adjusting the load, and measure the heat leakage of the test system in static and rotating states.

8. The centrifugal gain involute heat pipe design method according to claim 2, characterized in that: The step S62 specifically includes: Step S621, raising the hot end of the heat pipe by 0.1-2 mm; Step S622, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements; Step S623, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements; Step S624, adjusting the hot end load power in steps, iteratively adjusting the platform acceleration of the acceleration simulation system, controlling the operating temperature of the heat pipe to achieve a temperature difference of more than 5° C. between the hot end and the cold end of the heat pipe, and recording the ultimate heat transfer capacity of the heat pipe under this acceleration environment and operating temperature; Step S625, repeat the above steps to test the ultimate heat transfer capacity of the involute heat pipe at different operating temperatures under different acceleration environments.

9. The centrifugal gain involute heat pipe design method according to claim 2, characterized in that: The step S63 specifically includes: Step S631, adjusting the acceleration simulation system to control the platform acceleration to match the task requirements; Step S632, maintaining the rotation speed for 8-15 minutes until the distribution of the working medium gas and liquid in the heat pipe reaches a new equilibrium; Step S633, adjusting the temperature and flow rate of the fluid in the cooling system to control the operating temperature of the heat pipe to match the task requirements; Step S634, gradually adjusting the hot end load power from small to large, and judging the minimum starting power required by the heat pipe at the corresponding speed according to the temperature changes of each measuring point of the heat pipe; Step S635, adjusting the rotation speed according to the task requirements, and repeating the steps S631 to S634 to test the minimum starting power required by the involute heat pipe at different operating temperatures under different acceleration environments.

10. An involute heat pipe designed by using the centrifugal gain involute heat pipe design method according to any one of claims 1 to 9, wherein the heat pipe is suitable for a rotating platform.

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