A metallurgical furnace cooling stave provided with a pulsating heat pipe structure

Abstract

This invention discloses a cooling wall for metallurgical furnaces with a pulsating heat pipe structure, relating to the field of metallurgical furnace technology. It includes: a cooling wall with a pulsating heat pipe assembly fixedly installed inside; the pulsating heat pipe assembly consists of several parallel, equidistantly arranged pulsating heat pipes inclined relative to the cooling wall; each pulsating heat pipe is composed of four interconnected pipe sections, each section being U-shaped, arranged radially parallel and equidistantly, with the bottom of the sections connected by a U-shaped structure, and the two outermost sections connected by an inverted U-shaped structure, forming a continuous, closed annular flow path. This invention employs a composite structure of cooling wall and pulsating heat pipes, utilizing the compact, stable structure and excellent heat transfer performance of the pulsating heat pipes to overcome the limitations of the traditional single heat transfer mode of cooling walls, adapting to changes in dynamic heat load, and enhancing the comprehensive heat transfer performance of the cooling wall in high heat load areas, thus achieving energy saving.

Description

Technical Field

[0001] This invention relates to the field of metallurgical furnace and kiln technology, specifically to a metallurgical furnace and kiln cooling wall with a pulsating heat pipe structure. Background Technology

[0002] As a crucial cooling component installed on metallurgical furnaces, the cooling wall functions similarly to a microchannel heat exchanger used in electronic devices. By directly protecting the furnace shell from high temperatures, it extends the blast furnace's lifespan. The cooling wall not only maintains the dynamic stability of the furnace's internal thermal balance but also plays a critical role in delaying the deterioration of the furnace shell structure.

[0003] Currently, most industrial furnace cooling walls adopt the traditional single heat transfer mode: the main problem with this is: 1. Simply optimizing the heat transfer characteristics of the working fluid and the design of the tube side structure results in a delayed response to dynamic heat load fluctuations under high-temperature heat load conditions in metallurgical furnaces and kilns. The thermal response time of the cooling system under a single heat transfer mode is mostly 20-30 seconds, which can easily lead to local thermal stress concentration and slag layer instability failure.

[0004] 2. In the actual operation of metallurgical furnaces and kilns, the heat transfer performance of the cooling wall should not be evaluated solely based on the average temperature, because the main reason for equipment shutdown and maintenance is the breakdown and damage of the hot surface due to high-temperature thermal stress, rather than the average temperature exceeding the standard.

[0005] With the increasing scale and complexity of modern metallurgical furnaces, the traditional single heat transfer mode of cooling walls cannot keep up with the dynamic heat load fluctuations caused by the movement of furnace charge, changes in gas flow, and adjustments in pulverized coal injection. This leads to localized heat accumulation, which accelerates the erosion of the refractory lining and creates potential for thermal stress concentration. This technical problem directly results in traditional cooling walls being unable to adapt to the dynamic heat load requirements of modern metallurgical furnaces, becoming a core bottleneck restricting the long-term and stable operation of these furnaces. Summary of the Invention

[0006] To address the shortcomings of existing technologies, the main objective of this invention is to provide a cooling wall for metallurgical furnaces with a pulsating heat pipe structure. By applying the pulsating heat pipe to the copper cooling wall, this invention aims to solve the problem that existing single copper cooling walls in metallurgical furnaces cannot meet the requirements for adaptability to dynamic heat loads.

[0007] To achieve the above objectives, the present invention provides a cooling wall for a metallurgical furnace with a pulsating heat pipe structure, comprising: a cooling wall, wherein a pulsating heat pipe assembly is fixedly disposed inside the cooling wall; the pulsating heat pipe assembly is composed of several pulsating heat pipes arranged parallel to each other at equal intervals and inclined relative to the cooling wall; The pulsating heat pipe is composed of four interconnected tube sections, each tube section being U-shaped. The tube sections are arranged radially parallel and equidistantly, with the bottom of the tube sections connected by a U-shaped structure. The two outermost tube sections are connected by an inverted U-shaped structure, so that all tube sections form a continuous, closed annular flow path.

[0008] As a further improvement of the present invention, the cooling wall is made of pure copper and the outer wall of the pulsating heat pipe is plated with nickel.

[0009] As a further improvement of the present invention, the geometric dimensions of the cooling wall are 400 mm × 300 mm × 110 mm, the distance d1 between the center of the pulsating heat pipe plane and the hot surface of the cooling wall is 70 mm, the distance d2 between the center of the pulsating heat pipe plane and the cold surface of the cooling wall is 40 mm, and the length L of a single tube section 101 of the pulsating heat pipe is 108 mm.

[0010] As a further improvement of the present invention, the pulsating heat pipe assembly and the cooling wall are integrally cast.

[0011] As a further improvement of the present invention, the lengths of the evaporation section, condensation section and adiabatic section of the pulsating heat pipe account for 50%, 30% and 20% of the length of the entire pulsating heat pipe, respectively.

[0012] As a further improvement of the present invention, a third temperature measuring hole is provided on the side of the hot surface of the cooling wall, a first temperature measuring hole and a first pressure measuring hole are provided at the condensation section of the pulsating heat pipe 1, and a second temperature measuring hole and a second pressure measuring hole are provided at the evaporation section of the pulsating heat pipe.

[0013] As a further improvement of the present invention, the installation tilt angle α of the pulsating heat pipe is 50°-90°, wherein the installation tilt angle refers to the angle between the central plane of the pulsating heat pipe and the direction perpendicular to the cooling wall.

[0014] As a further improvement of the present invention, the inner diameter D of the pulsating heat pipe is 2mm, the outer diameter De is 4mm, and the pipe section spacing H is 10mm.

[0015] As a further improvement of the present invention, the cooling medium inside the pulsating heat pipe is ethanol.

[0016] The beneficial effects of this invention are reflected in: 1. This invention applies a pulsating heat pipe to a copper cooling wall, utilizing the compact structure and excellent self-oscillating heat transfer characteristics of the pulsating heat pipe. These characteristics are compatible with the high thermal conductivity and thermal shock resistance of the copper cooling wall, thereby improving the overall cooling efficiency of the cooling wall, extending the service life of the metallurgical furnace, and reducing equipment downtime and maintenance caused by thermal fatigue.

[0017] 2. The pulsating heat pipe of the present invention adopts a closed-loop structure. The heat transport is achieved by driving the cooling medium to oscillate and flow through the pressure difference generated by the alternating gas-liquid plugs. The closed loop avoids the leakage of the cooling medium and does not require a liquid suction core structure, which reduces maintenance requirements. It is particularly suitable for industrial environments that require efficient and stable heat transfer, and can ensure the stable circulation of the cooling medium to achieve more efficient heat transfer.

[0018] 3. The pulsating heat pipe in this invention is based on a three-stage heat transfer mechanism of "evaporation-insulation-condensation". Heat transfer is achieved through the reciprocating oscillation of the gas-liquid plug, requiring no external power. It relies on phase change and pressure difference to drive fluid circulation, thereby achieving efficient and stable heat transfer. At the same time, this invention achieves efficient heat transfer by optimizing the length ratio of each segment of the pulsating heat pipe, effectively reducing inter-segment heat loss and improving overall heat transfer efficiency and system stability. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a side view of the present invention; Figure 3 This is a schematic diagram of the cooling wall hot surface structure of the present invention; Figure 4 This is a schematic diagram of a single section of the pulsating heat pipe of the present invention; Figure 5 This is a schematic diagram of the overall assembly structure of the pulsating heat pipe structure of the present invention; Figure 6 This is a comparison chart of the highest temperature of the copper cooling wall under different installation angles and pipe diameters in the technical solution of this invention. Figure 7 This is a schematic diagram of Fluent mesh generation in Embodiment 2 of the present invention; Figure 8 This is a comparison diagram of the highest temperature of the copper cooling wall surface in Embodiment 2 of the present invention between the pulsating heat pipe structure and the smooth heat pipe structure.

[0020] Explanation of reference numerals in the attached figures: 1. Pulsating heat pipe; 101. Pipe section; 105. First temperature measuring hole; 106. First pressure measuring hole; 107. Second temperature measuring hole; 108. Second pressure measuring hole; 109. Third temperature measuring hole; 2. Cooling wall; 201. Hot surface of cooling wall; 202. Cold surface of cooling wall. Detailed Implementation

[0021] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0022] Example 1 In this embodiment, see Figure 1-5 The present invention provides a cooling wall for a metallurgical furnace with a pulsating heat pipe structure, comprising: a cooling wall 2, wherein a pulsating heat pipe assembly is fixedly disposed inside the cooling wall 2; the pulsating heat pipe assembly is composed of several pulsating heat pipes 1 arranged parallel to each other at equal intervals and inclined relative to the cooling wall 2; The pulsating heat pipe 1 is composed of four interconnected pipe sections 101. Each pipe section 101 is U-shaped and arranged radially parallel and equidistantly. The bottom of the pipe sections 101 is connected by a U-shaped structure, and the two outermost pipe sections 101 are connected by an inverted U-shaped structure, so that all pipe sections 101 form a continuous and closed annular flow path.

[0023] Preferably, the pulsating heat pipe 1 adopts a closed-loop structure. The pulsating heat pipe 1 adopts a closed-loop two-phase heat transfer structure composed of a U-shaped sealed vacuum tube. Heat transport is achieved by driving the oscillating flow of the cooling medium through the pressure difference generated by the alternating gas-liquid plugs. The closed-loop design avoids cooling medium leakage and eliminates the need for a liquid wick structure, reducing maintenance requirements.

[0024] In the above configuration, the present invention applies a pulsating heat pipe to the cooling wall 2, taking advantage of the compact structure of the pulsating heat pipe 1 and its excellent self-oscillating heat transfer characteristics.

[0025] The self-oscillating heat transfer of the pulsating heat pipe 1 is a two-phase oscillation process that is completely driven by heat and requires no external power. It can achieve efficient heat transport in a very small space. The periodic vaporization and condensation process of the internal cooling working fluid does not require external power, which significantly improves the heat transfer efficiency.

[0026] The composite structure of the pulsating heat pipe 1 and the cooling wall 2 possesses self-oscillating heat transfer characteristics that enable efficient heat transport within a very small space. That is, the periodic vaporization and condensation process of the cooling working fluid inside the pulsating heat pipe 1 does not require external power. This characteristic is consistent with the high thermal conductivity and thermal shock resistance of the copper cooling wall, which can significantly improve heat transfer efficiency, thereby extending the service life of metallurgical furnaces and reducing equipment downtime and maintenance caused by thermal fatigue.

[0027] Furthermore, the cooling wall 2 is made of pure copper, and the outer wall of the pulsating heat pipe 1 is plated with nickel.

[0028] In the above setup, the copper cooling wall has the advantages of high thermal conductivity and fast heat transfer rate; the nickel plating layer on the outer wall of the pulsating heat pipe 1 is used to suppress the oxidation and corrosion reaction between copper and the cooling medium (such as ethanol, water, methanol) at high temperature, and improve the long-term stability of the device.

[0029] Furthermore, the geometric dimensions of the cooling wall 2 are 400 mm × 300 mm × 110 mm, the distance d1 between the center of the pulsating heat pipe 1 and the hot surface of the cooling wall is 70 mm, the distance d2 between the center of the pulsating heat pipe 1 and the cold surface of the cooling wall is 40 mm, and the length L of a single pipe section 101 of the pulsating heat pipe 1 is 108 mm.

[0030] Furthermore, the pulsating heat pipe assembly and the cooling wall 2 are integrally cast.

[0031] Furthermore, the lengths of the evaporation section, condensation section, and adiabatic section of the pulsating heat pipe 1 account for 50%, 30%, and 20% of the entire pulsating heat pipe 1, respectively.

[0032] In the above configuration, after the cooling medium is injected into the closed pulsating heat pipe 1, the cooling medium forms alternating liquid and vapor plug structures within the microcapillary due to the combined effects of surface tension and gravity. In the evaporation section (heating section) of the pulsating heat pipe 1, the cooling medium absorbs heat and turns into vapor, and the heated bubbles expand, pushing the liquid plugs towards the cold end. In the condensation section (cooling section) of the pulsating heat pipe 1, the cooling medium releases heat and condenses, the bubbles contract or rupture, and the pressure drops. This causes the liquid plugs to be pulled back or redistributed, forming a backflow and completing an oscillating cycle. This alternating cycle of forward pushing and reverse suction constitutes a self-sustaining oscillation, the frequency and amplitude of which are dynamically adjusted with heat flux density, filling rate, and pipe geometry. Each movement of the liquid plug through the pipe wall is accompanied by strong turbulent disturbance and boundary layer disruption, greatly improving the convective heat transfer coefficient between the pipe wall and the cooling medium. This periodic oscillation greatly enhances the convective heat transfer between the pipe wall and the cooling medium, making the heat transfer efficiency of the pulsating heat pipe 1 much higher than that of traditional heat pipes.

[0033] This invention achieves efficient heat transfer by optimizing the length ratio of each segment of the pulsating heat pipe 1: the evaporation segment, condensation segment, and adiabatic segment are 50%, 30%, and 20% of the length of the pulsating heat pipe 1, respectively, to effectively reduce inter-segment heat loss and improve overall heat transfer efficiency and system stability. The three-segment heat transfer mechanism is the core of the pulsating heat pipe's efficient heat transfer. In this mechanism, the evaporation segment absorbs heat, causing the cooling medium to boil and generate a gas plug; the condensation segment condenses the gas plug into a liquid plug; and the adiabatic segment serves as a transitional region connecting the two without phase change. This structure achieves heat transfer through the reciprocating oscillation of the gas and liquid plugs, requiring no external power and relying on phase change and pressure difference to drive fluid circulation, thereby achieving efficient and stable heat transfer.

[0034] Furthermore, a third temperature measuring hole 109 is provided on the side of the hot surface of the cooling wall, a first temperature measuring hole 105 and a first pressure measuring hole 106 are provided at the condensation section of the pulsating heat pipe 1, and a second temperature measuring hole 107 and a second pressure measuring hole 108 are provided at the evaporation section of the pulsating heat pipe 1.

[0035] Preferably, the side of the cooling wall hot surface is provided with 9 third temperature measuring holes 109, the condensation section of the pulsating heat pipe 1 is provided with 2 first temperature measuring holes 105 and 2 first pressure measuring holes 106, and the evaporation section of the pulsating heat pipe 1 is provided with 2 second temperature measuring holes 107 and 2 second pressure measuring holes 108.

[0036] In the above configuration, during actual operation, the present invention enables real-time monitoring of the internal temperature and pressure of the cooling wall 2 via the first and second temperature measuring holes 107 and the first and second pressure measuring ports located in the condensation and evaporation sections of the pulsating heat pipe 1, as well as the third temperature measuring hole 109 on the side of the hot surface of the cooling wall. This configuration is crucial for understanding the heat exchange process and predicting the performance of the cooling wall 2. Accurate temperature monitoring helps to detect and adjust areas of concentrated heat (hot spots), while pressure monitoring ensures that the cooling wall 2 operates under safe working pressure.

[0037] Furthermore, the installation tilt angle α of the pulsating heat pipe 1 is 50°-90°, where the installation tilt angle refers to the angle between the central plane of the pulsating heat pipe 1 and the vertical direction of the cooling wall 2.

[0038] Furthermore, the inner diameter D of the pulsating heat pipe 1 is 2mm, the outer diameter De is 4mm, and the spacing H between pipe sections 101 is 10mm.

[0039] For details regarding the above settings, please refer to [link / reference]. Figure 6 , Figure 6 To numerically simulate and evaluate the effects of different installation angles (50°-90°) and different pipe diameters (4-8 mm) of the pulsating heat pipe 1 on the maximum temperature of the cooling wall 2, the peak temperature of the cooling wall 2 interface was reduced by 11.5%, 10.5%, and 10.3% respectively when different installation angles of the heat pipe 1 were compared under the same pipe diameter. When the baseline design (pipe diameter 8 mm, installation angle 60°) was compared with the optimized design (pipe diameter 4 mm, installation angle 70°), the peak temperature was reduced by 8.2%.

[0040] The mechanism is as follows: (1) When the installation tilt angle is higher than 60°, the gravity effect is consistent with the heat drive direction. At this time, the liquid film flows back more smoothly under the action of gravity, which can effectively reduce the start-up time; (2) When the installation tilt angle is higher than 80°, the gravity effect is too strong, resulting in the liquid plug flow rate being too fast, the heat exchange time being insufficient, and the overall heat transfer efficiency being reduced; (3) A smaller pipe diameter can enhance the capillary force effect, which is conducive to the spontaneous formation of distributed liquid plugs and gas plugs by the cooling working fluid under the action of surface tension. This is the basic condition for the operation of the pulsating heat pipe 1.

[0041] Furthermore, the cooling medium inside the pulsating heat pipe 1 is ethanol.

[0042] Example 2 In this embodiment, a numerical simulation is performed on the cooling wall 2 equipped with a pulsating heat pipe 1. The heat exchange performance of the copper cooling wall of an industrial furnace with a pulsating heat pipe 1 structure is described below.

[0043] This test uses computational fluid dynamics (CFD) software to numerically simulate the temperature field of the cooling wall 2. Simulation conditions: copper cooling wall with pulsating heat pipe 1 pipe structure, and ethanol as the cooling medium.

[0044] In Fluent's mesh generation process, the meshing strategies for solid and fluid domains exhibit significant differences. For solid domains involving only heat conduction, mesh generation is relatively simple, requiring only coordination with the meshing logic of fluid domain blocks, without needing to consider complex flow characteristics. This is because the dependence of heat conduction problems on the mesh primarily lies in the accurate representation of geometry and the spatial resolution of the temperature field. However, the core and challenge of mesh generation are concentrated in the fluid domain. This is because the flow behavior in the fluid domain (such as turbulence, separation, and vortices) is extremely sensitive to mesh quality, directly affecting the accuracy and reliability of numerical simulations. Fluid domain meshes need to accurately capture the details of the flow, including boundary layer development, vortex formation and evolution, and phenomena such as flow separation and reattachment. These all place higher demands on the mesh density, distribution, and arrangement.

[0045] Structured meshes, with their orderly arrangement, facilitate the verification of mesh independence in the fluid domain. Thanks to the clear arrangement of structured meshes, the verification of fluid domain mesh independence can be divided into a systematic analysis of three mesh parameters: the height of the first layer, the number of radial meshes, and the height of the axial mesh, thereby comprehensively evaluating the impact of the mesh on the simulation results. Among these, the height of the first layer mesh, Δs, is a crucial parameter, determining the mesh resolution in the near-wall region and playing a decisive role in capturing flow details near the wall (such as boundary layer development). The height of the first layer mesh, Δs, can be determined by the dimensionless wall distance y+, as shown in the following formula: To ensure the heat transfer accuracy between the solid wall and the first layer of the fluid mesh, assuming y+≈1, the calculated height of the first layer of the mesh on the wall of the pulsating heat pipe 1 is 0.75mm. Figure 7 This is a schematic diagram of Fluent mesh generation.

[0046] The wall boundary conditions for the cooling medium are: Reynolds number Re = 5000 - 40000, and inlet temperature = 298 K. The convective heat transfer coefficient of the cooling wall hot surface 201 is 232 W / m². 2 K, incoming flow temperature is 1200℃; the convective heat transfer coefficient of the cold surface 202 of the cooling wall is 11 W / m 2 K, incoming flow temperature is 25℃.

[0047] The evaluation indicators for the heat transfer performance of cooling walls mainly include the maximum temperature, the pipe wall heat transfer coefficient, and the comprehensive heat transfer factor η. The lower the maximum temperature, the better the heat transfer performance of the cooling wall. The higher the pipe wall heat transfer coefficient, the stronger the heat transfer effect of the pipe. A comprehensive heat transfer factor η greater than 1 indicates that the new composite structure has better comprehensive heat transfer performance.

[0048] Simulation results: The flow temperature distribution in a copper cooling wall with a pulsating heat pipe structure and a copper cooling wall with a smooth pipe structure is as follows: Figure 8 As shown, under the same boundary conditions, the fluid temperature change trends in the pulsating heat pipe structure and the smooth pipe structure are basically the same, but the changes in the maximum wall temperature are significantly different. The pulsating heat pipe structure has a lower maximum wall temperature, indicating that the cooling performance of the pulsating heat pipe structure is better than that of the smooth pipe structure.

[0049] The simulation results for the highest temperature of the copper cooling wall in this embodiment are as follows: Figure 8 As shown, the maximum temperature of a copper cooling wall with a pulsating heat pipe structure and a copper cooling wall with a smooth pipe structure are compared under the same boundary conditions. The Reynolds number ranges from 5000 to 40000. As shown in the figure, the cooling wall 2 equipped with a pulsating heat pipe 1 achieves more efficient heat transfer due to its closed-loop structure. This mechanism effectively improves the heat exchange efficiency between the inner wall of the pipe and the cooling medium, thereby enhancing the heat dissipation capacity of the cooling wall 2 and the heat transfer coefficient of the pipe. Compared to the cooling wall with a smooth pipe structure, the cooling wall with a pulsating heat pipe structure has better heat transfer capacity and can meet the high heat transfer efficiency requirements of furnace cooling walls.

[0050] In summary, this invention improves the overall heat exchange capacity of the high-heat-load zone of the cooling wall of metallurgical furnaces by incorporating a composite structure with pulsating heat pipes in the copper cooling wall, utilizing the excellent heat transfer characteristics of the pulsating heat pipes. This composite structure further enhances the overall cooling efficiency by strengthening the interfacial heat transfer between the heat pipes and the copper substrate, effectively preventing the risk of shutdown and maintenance due to insufficient cooling capacity of the cooling wall in the high-heat-load zone.

[0051] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A cooling wall for a metallurgical furnace with a pulsating heat pipe structure, comprising a cooling wall (2), characterized in that, A pulsed heat pipe assembly is fixedly installed inside the cooling wall (2); the pulsed heat pipe assembly consists of several pulsed heat pipes (1) arranged parallel to each other at equal intervals and inclined relative to the cooling wall (2); The pulsating heat pipe (1) is composed of four interconnected pipe sections (101). Each pipe section (101) is U-shaped and arranged radially parallel and equidistantly. The bottom of the pipe sections (101) is connected by a U-shaped structure, and the two outermost pipe sections (101) are connected by an inverted U-shaped structure, so that all pipe sections (101) form a continuous and closed annular flow path.

2. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 1, characterized in that: The cooling wall (2) is made of pure copper, and the outer wall of the pulsating heat pipe (1) is plated with nickel.

3. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 2, characterized in that: The geometric dimensions of the cooling wall (2) are 400 mm × 300 mm × 110 mm. The distance d1 between the center of the pulsating heat pipe (1) and the hot surface of the cooling wall is 70 mm. The distance d2 between the center of the pulsating heat pipe (1) and the cold surface of the cooling wall is 40 mm. The length L of a single pipe section (101) of the pulsating heat pipe (1) is 108 mm.

4. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 3, characterized in that: The pulsating heat pipe assembly and the cooling wall (2) are integrally cast.

5. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 4, characterized in that: The lengths of the evaporation section, condensation section and adiabatic section of the pulsating heat pipe (1) account for 50%, 30% and 20% of the total length of the pulsating heat pipe (1), respectively.

6. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 5, characterized in that: A third temperature measuring hole (109) is provided on the side of the cooling wall hot surface (201), a first temperature measuring hole (105) and a first pressure measuring hole (106) are provided at the condensation section of the pulsating heat pipe (1), and a second temperature measuring hole (107) and a second pressure measuring hole (108) are provided at the evaporation section of the pulsating heat pipe (1).

7. A metallurgical furnace cooling wall with a pulsating heat pipe structure according to claim 6, characterized in that: The installation tilt angle α of the pulsating heat pipe (1) is 50°-90°, where the installation tilt angle refers to the angle between the central plane of the pulsating heat pipe (1) and the vertical direction of the cooling wall (2).

8. A cooling wall for a metallurgical furnace with a pulsating heat pipe structure according to claim 7, characterized in that: The pulsating heat pipe (1) has an inner diameter D of 2 mm, an outer diameter De of 4 mm, and a pipe section (101) spacing H of 10 mm.

9. A cooling wall for a metallurgical furnace with a pulsating heat pipe structure according to claim 8, characterized in that: The cooling medium inside the pulsating heat pipe (1) is ethanol.

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