Composite structure sweating cooling type high-temperature water-cooling dynamic total pressure probe

Abstract

The utility model belongs to the technical field of high-temperature flow field pressure testing, and particularly relates to a sweating cooling type high-temperature water-cooling dynamic total pressure probe with a composite structure, which comprises a probe support rod, a probe head, a sleeve, a mounting seat, a cable, a cooling water inlet pipe, a water outlet pipe, a diverging wall surface, an impact wall surface, a current limiting wall surface, a dynamic pressure sensor, a diverging hole, an impact hole and the like. One part of cooling water entering the probe through the water inlet pipe flows out after impingement cooling and convective heat exchange in the axial direction, and the other part of cooling water permeates in the radial direction and seeps out through the diverging holes in the diverging wall face, so that the probe is subjected to sweating cooling. The probe cooling device has the advantages that the advantage of large phase-change heat transfer is adopted, the structure has the advantages of sweating cooling, impact cooling and convective heat transfer technologies, the probe supporting rod and the probe head are cooled at the same time, the cooling efficiency of the probe is greatly improved, and the service life of the probe is prolonged. The dynamic response capability of the probe is improved; the service life of the probe in an extreme high-temperature environment (the highest temperature can reach 2500 DEG C) is prolonged; and the reliability of a measurement result is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of dynamic pressure measurement in high-temperature flow fields, and particularly relates to a composite structure transpiration cooling type high-temperature water-cooled dynamic total pressure probe, which is applicable to measuring the dynamic pressure in extreme high-temperature environments such as aero-engine combustion chambers and turbines. This probe adopts a transpiration cooling technology with a composite structure to achieve efficient cooling of the probe strut and the probe head, ensuring that the probe can operate stably in an extreme high-temperature environment up to 2500°C. Background Art

[0002] The compressor, combustion chamber, and turbine are the three core components of an aero-engine. With the development of aerospace technology, the working environment of aero-engines has become extremely harsh. Especially in the combustion chamber and turbine parts, the temperature has been rising continuously and has reached an extremely high level (up to 2300°C). Accurately measuring the dynamic pressure in these parts is crucial for engine performance optimization, efficiency improvement, and safety guarantee. However, there are many difficulties in measuring the pressure field in such high-temperature environments. One of the main difficulties is that the pressure probe is required to have sufficient strength and reliability in harsh environments such as high temperature, that is, the probe is required to have an effective cooling structure and sufficient accuracy. Currently, there are mainly two cooling methods for pressure probes in high-temperature environments: film cooling and water cooling. Each of these two cooling methods has its own advantages, but also has certain technical defects, which affect the performance and service life of the probe.

[0003] The advantage of the film cooling type probe is that it is relatively easy to adjust the temperature and flow rate of the cooling air flow according to the mainstream temperature and flow rate. However, this structure has certain defects in the cooling of the probe head: if film holes are opened on the probe head, the ejected cooling air flow will interfere with the flow field of the probe head, affecting the test accuracy. If no film holes are opened on the leading edge of the probe strut and only internal convective heat transfer is used for cooling, the cooling effect is insufficient and the probe head is easily burned out. In addition, due to the small specific heat capacity of the gas, in an extremely high-temperature environment (above 2000°C), the cooling effect provided by film cooling is limited, and it may even be insufficient, resulting in probe damage.

[0004] The advantages of the water-cooled probe are that the flow of cooling water will not interfere with the flow field, and due to the specific heat capacity of water being much larger than that of air, the cooling effect is better. However, the complexity of the water-cooling system increases the difficulty of design and maintenance. It is difficult to quickly adjust the cooling water flow rate when the test state changes, which may lead to excessive local temperature or pressure of the probe, increasing the risk of structural damage. At the same time, most existing water-cooled probes use the method of convective heat transfer to cool the probe. Such a heat transfer process belongs to the sensible heat exchange process. When the measured ambient temperature rises, the required cooling water flow rate increases greatly. If the design of the cooling water flow channel inside the probe is unreasonable, there will be problems such as large internal resistance, insufficient contact between the cooling water and the probe strut, and dead zones, resulting in an unsatisfactory cooling effect. And due to the small size of the probe, the working difficulty of the water-cooled probe is greater.

[0005] Compared with the sensible heat exchange process of reducing the probe temperature through heat conduction, the latent heat exchange process that absorbs a large amount of heat through the phase change of substances (such as from liquid to gas, or from solid to liquid) has a more efficient cooling efficiency. And because under the same conditions, the heat exchange amount of latent heat exchange is much larger than that of the sensible heat exchange process. Sweating cooling is an effective latent heat exchange cooling technology. Using sweating cooling can reduce the requirement for the cooling water flow rate of the probe in an extremely high-temperature environment.

[0006] Two invention patents with publication numbers CN107063560A and CN107131999A respectively proposed a high-temperature water-cooled dynamic pressure probe and a high-temperature water-cooled static pressure probe; a utility model patent with publication number CN206930646U proposed a water-cooled probe. The above water-cooled probes all use the sensible heat exchange process of cooling water absorbing the heat of the probe strut to cool the probe strut. In an extremely high-temperature environment, the cooling effect may be limited, affecting the accuracy of the probe measurement data, and even causing damage to the probe. More importantly, the above water-cooled probes do not cool the probe head, greatly increasing the risk of damage to the probe head due to high temperature.

[0007] Therefore, there is an urgent need to develop a pressure probe that can work stably and reliably in an extremely high-temperature environment (above 2000 °C) and can also cool the probe head to meet the pressure test requirements in environments with increasing temperatures in components such as combustion chambers and turbines. Summary of the Invention

[0008] The object of the present invention is: aiming at the pressure test problems in extremely high-temperature environments such as combustion chambers and turbines, to provide a dynamic pressure measurement method with good cooling effect and high reliability, which can cool the probe strut and the probe head at the same time and ensure an ideal and uniform heat exchange effect.

[0009] The solution of the present invention:

[0010] A composite structure transpiration cooling type high-temperature water-cooled dynamic total pressure probe, comprising a probe rod (1), a probe head (2), a sleeve (3), a mounting seat (4), a positioning hole (5), a cooling water inlet pipe (6), a cooling water outlet pipe (7), a cable (8), a circumferential partition baffle (9), a first wall - a divergent wall (10), a second wall - an impinging wall (11), a third wall - a flow-limiting wall (12), a fourth wall - the outer wall surface of the probe rod (13), a dynamic pressure sensor (18), a pressure measuring hole (19), a hemispherical groove (20) and a number of turbulator columns (14), divergent holes (15), impinging holes (16), flow-limiting holes (17); characterized in that: the probe head (2) is located at the top of the probe rod (1), the surface of the probe head (2) is provided with the pressure measuring hole (19), the sleeve (3) is installed outside the probe rod (1), the mounting seat (4) is installed on the sleeve (3), the mounting seat (4) is provided with the positioning hole (5), the cooling water inlet pipe (6) and the cable (8) are both installed inside the probe rod (1), the cooling water outlet pipe (7) is installed on the sleeve (3) behind the mounting seat (4), and the cable (8) is installed inside the probe rod (1) and on the periphery of the cooling water inlet pipe (6) near one side of the pressure measuring hole (19).

[0011] Further, the probe rod (1) is of a double-layer structure, the inner layer is communicated with the cooling water inlet pipe (6) to form a cooling water inlet flow channel, the outer layer is divided into six chambers by the circumferential partition baffle (9), these chambers are communicated with the permeation flow channel to form the main flow channel for the axial return of the cooling water, and the chamber near the pressure measuring hole (19) is equipped with the dynamic pressure sensor (18) and the cable (8).

[0012] Further, the outer diameter of the probe rod (1) is 2 mm to 5 mm, the corresponding outer diameter of the sleeve (3) is 4 mm to 10 mm, the two are welded into a whole, and the pipe diameter of the cooling water inlet pipe (6) is 1 mm to 2 mm.

[0013] Further, the probe head (2) is a cylindrical part with an axial length from the top of the probe to the end face being 3 times the outer diameter of the probe rod (1). The pressure measuring hole (19) is opened at a place 1 time the cylinder diameter away from the top on the probe head (2). A hemispherical groove (20) is dug on the probe surface with the pressure measuring hole (19) as the center to increase the insensitive angle of the pressure measuring hole. The diameter of the hemispherical groove (20) is 3 times the diameter of the pressure measuring hole, and the diameter of the pressure measuring hole is 0.6 mm to 1.5 mm.

[0014] Further, within a range of 2 times the diameter of the pressure measuring hole from the surface of the probe head (2) to the hemispherical groove (20), no divergent holes (15) are opened to avoid the influence of steam generated by transpiration cooling on the measurement accuracy.

[0015] Further, the pressure measuring hole (19) on the probe head (2) is communicated with the dynamic pressure sensor (18), and the signal generated by the dynamic pressure sensor (18) is transmitted out through the cable (8).

[0016] Furthermore, the sleeve (3) has a three-layer structure, including a first wall surface - a divergent wall surface (10), a second wall surface - an impact wall surface (11), and a third wall surface - a flow-limiting wall surface (12). A first cooling channel is formed between the first wall surface - the divergent wall surface (10) and the second wall surface - the impact wall surface (11), a second cooling channel is formed between the second wall surface - the impact wall surface (11) and the third wall surface - the flow-limiting wall surface (12), and a third cooling channel is formed between the third wall surface - the flow-limiting wall surface (12) and the fourth wall surface - the outer wall surface of the probe support rod (13). The above three cooling channels are water-permeating channels for cooling water.

[0017] Furthermore, the mounting base (4) is in a racetrack shape, with a thickness of 2 to 5 millimeters. Two positioning holes (5) are provided on the mounting base (4), and the diameter of the positioning holes (5) is 2 to 3 millimeters.

[0018] Furthermore, 6 circumferential partition baffles (9) are evenly arranged circumferentially between the outer wall surface of the cooling water inlet pipe (6) and the first wall surface - the divergent wall surface (10) to reduce the negative impact of gravity on the uneven distribution of cooling water. The circumferential partition baffles penetrate through the second wall surface - the impact wall surface (11), the third wall surface - the flow-limiting wall surface (12), and the fourth wall surface - the outer wall surface of the probe support rod (13), dividing the first cooling channel, the second cooling channel, the third cooling channel, and the cooling water return channel into 6 independent cooling regions circumferentially. The 6 cooling water return channels correspond to the 6 independent cooling regions one by one.

[0019] Furthermore, the cooling water outlet pipe (7) is connected to the main cooling water circuit to timely discharge the cooling water that has risen to a certain temperature in the probe but has not flowed into the third flow channel between the fourth wall surface - the outer wall surface of the probe support rod (13) and the third wall surface - the flow-limiting wall surface (12). That is, through the convective heat transfer of the flowing cooling water, the part of the heat that could not be completely absorbed during the transpiration cooling process is further absorbed, thereby better protecting the dynamic pressure sensor (18).

[0020] Furthermore, inclined divergent holes (15) are formed on the surface of the first wall surface - the divergent wall surface (10), which are evenly distributed circumferentially and staggered axially in a periodic manner, forming a first wall surface - a divergent wall surface (10) with uniformly dense divergent holes (15). The divergent holes (15) penetrate through the first wall surface - the divergent wall surface (10), and the cooling water seeps out from the divergent holes to form a liquid film to evaporatively cool the outer wall surface of the sleeve (3). The inclination angle of the divergent holes is 30° to 60°.

[0021] Further, the diverging holes (15) are cylindrical holes with cloud-shaped protrusions on the inner wall, which enable the cooling water to seep out slowly to ensure a good cooling effect. The diameter of the diverging holes (15) is 0.05 mm to 0.15 mm, and the height of the protrusions on the inner wall is 0.01 mm to 0.03 mm.

[0022] Further, the second wall - the impact wall (11) is evenly distributed with impact holes (16) on its surface. The impact holes (16) connect the first cooling channel and the second cooling channel. The cooling water passes through the second wall - the impact wall (11) from the second cooling channel and enters the first cooling channel, and performs impact cooling on the first wall - the diverging wall (10). The impact holes (16) are straight holes, axially staggered and periodically distributed on the second wall - the impact wall (11). The diameter of the impact holes is 0.1 mm to 0.3 mm.

[0023] Further, on the third wall - the flow-limiting wall (12), a number of groups of flow-limiting holes (17) are evenly arranged circumferentially. Since the thermal environments at different axial positions of the probe strut (1) may vary, and the required flow rates are also different, different numbers of flow-limiting holes (17) can be opened at different axial positions of the probe strut (1) according to the thermal environment where the probe is located to control the flow rate of the cooling water entering different positions, thereby controlling the cooling effect at different positions. The diameter of the flow-limiting holes (17) is 0.2 mm to 0.4 mm.

[0024] Further, turbulators (14) are provided in the first cooling channel, which are evenly distributed circumferentially and axially staggered and periodically distributed to form a uniformly dense turbulator group. The upper and lower end surfaces of the turbulators (14) are fixedly connected to the first wall - the diverging wall (10) and the second wall - the impact wall (11) to enhance the overall heat transfer performance. The diameter of the turbulators (14) is 0.1 mm to 0.2 mm.

[0025] The composite structure transpiration cooling type high-temperature water-cooled dynamic total pressure probe of the present invention has the following beneficial effects:

[0026] Beneficial effect one: The present invention can cool the probe strut and the probe head simultaneously, effectively improving the working life and the upper limit of the working temperature of the probe in a high-temperature environment. The present invention proposes a transpiration cooling structure suitable for the probe, which combines convective heat transfer cooling and transpiration cooling. A large amount of heat is absorbed by the evaporation of the cooling water in the permeating part, and the non-permeating part of the cooling water absorbs heat and rises in temperature and then flows out through the water outlet pipe to further cool the probe and the dynamic pressure sensor. It can absorb a large amount of heat under the conditions of a small probe size and limited cooling water flow rate, effectively improving the working life and the upper limit of the working temperature of the probe in a high-temperature environment (up to 2500 °C at most).

[0027] Beneficial effect two: Compared with other total pressure probes, the present invention has higher dynamic response ability and measurement result accuracy. The present invention adopts a composite structure, which can cool the probe strut and the probe head simultaneously through reasonable layout, effectively preventing the local temperature of the probe head from being too high, enabling the dynamic pressure sensor to be installed closer to the pressure measurement hole, effectively reducing the cavity effect between the pressure measurement hole at the probe head and the dynamic pressure sensor, thereby improving the dynamic response ability of the probe in a high-temperature environment and effectively ensuring the accuracy of the probe measurement result.

[0028] Beneficial effect three: Compared with other water-cooled probes, the present invention requires a significantly reduced cooling water flow rate. The present invention adopts a cooling method mainly based on transpiration cooling, which can effectively reduce the required cooling water flow rate requirement compared with the convective heat transfer cooling method under the same cooling effect.

[0029] Beneficial effect four: Compared with other forms of total pressure probes, the present invention has a larger insensitive angle range. The present invention has a hemispherical groove around the pressure measurement hole at the probe head, which has a good stagnation effect on the oncoming flow and can effectively increase the insensitive angle of the pressure measurement hole.

[0030] Beneficial effect five: The high-temperature water-cooled pressure probe of the present invention is of an integrated design, with a stable and reliable structure, simple and accurate positioning, and is suitable for popularization and use. Description of the Drawings

[0031] Figure 1 is the overall structural schematic diagram of a composite structure transpiration cooling type high-temperature water-cooled dynamic total pressure probe in an embodiment of the present invention.

[0032] Figure 2 is Figure 1 the partial enlarged front view and side view of the probe head.

[0033] Figure 3 is Figure 1 the top view and the sectional view of the A-A section.

[0034] Figure 4 is Figure 2 the front half sectional view and the sectional view of the B-B section of the probe head shown, where the solid arrow indicates the cooling water flow direction and the hollow arrow indicates the cooling water penetration direction.

[0035] Figure 5 is the schematic diagram of the divergent hole form with protrusions on the inner wall, and the arrow represents the direction of water penetration and outflow.

[0036] Wherein: 1 - probe rod, 2 - probe head, 3 - sleeve, 4 - mounting seat, 5 - positioning hole, 6 - cooling water inlet pipe, 7 - cooling water outlet pipe, 8 - cable, 9 - circumferential partition plate, 10 - first wall surface (diverging wall surface), 11 - second wall surface (impinging wall surface), 12 - third wall surface (flow-limiting wall surface), 13 - fourth wall surface (outer wall surface of probe rod), 14 - turbulator cylinder, 15 - diverging hole, 16 - impinging hole, 17 - flow-limiting hole, 18 - dynamic pressure sensor, 19 - pressure measuring hole, 20 - hemispherical groove. Detailed implementation mode

[0037] The present invention will be described in detail below in conjunction with the accompanying drawings and a specific implementation case, so that the advantages and features of the present invention can be more easily understood by those skilled in the art, thereby making the protection scope of the present invention more clearly defined.

[0038] See Figures 1 to 5 Shown is a composite structure transpiration cooling type high-temperature water-cooled dynamic total pressure probe, including a probe rod (1), a probe head (2), a sleeve (3), a mounting seat (4), a positioning hole (5), a cooling water inlet pipe (6), a cooling water outlet pipe (7), a cable (8), a circumferential partition baffle (9), a first wall surface - diverging wall surface (10), a second wall surface - impinging wall surface (11), a third wall surface - flow-limiting wall surface (12), a fourth wall surface - outer wall surface of probe rod (13), a dynamic pressure sensor (18), a pressure measuring hole (19), a hemispherical groove (20) and a number of turbulator columns (14), diverging holes (15), impinging holes (16), flow-limiting holes (17); characterized in that: the probe head (2) is located at the top of the probe rod (1), the surface of the probe head (2) is provided with a pressure measuring hole (19), the sleeve (3) is installed outside the probe rod (1), the mounting seat (4) is installed on the sleeve (3), the mounting seat (4) is provided with a positioning hole (5), the cooling water inlet pipe (6) and the cable (8) are both installed inside the probe rod (1), the cooling water outlet pipe (7) is installed on the sleeve (3) behind the mounting seat (4), and the cable (8) is installed inside the probe rod (1) and on the periphery of the cooling water inlet pipe (6) near one side of the pressure measuring hole (19).

[0039] The probe rod (1) is of a double-layer structure. The inner layer communicates with the cooling water inlet pipe (6) to form a cooling water inlet flow channel. The outer layer is divided into six chambers by the circumferential partition baffle (9). These chambers communicate with the permeation flow channel to form the main flow channel for the axial return of the cooling water. The chamber near the pressure measuring hole (19) is equipped with a dynamic pressure sensor (18) and a cable (8).

[0040] In this embodiment, the outer diameter of the probe rod (1) is 3 mm, the corresponding outer diameter of the sleeve (3) is 5 mm, and the two are welded into a whole. The diameter of the cooling water inlet pipe (6) is 1.5 mm.

[0041] The probe head (2) is a cylindrical part where the axial length from the top of the probe to the end face is 3 times the outer diameter of the probe rod (1). A pressure measurement hole (19) is opened at a position 1 time the cylinder diameter from the top end on the probe head (2). A hemispherical groove (20) is dug on the probe surface with the pressure measurement hole (19) as the center to increase the insensitive angle of the pressure measurement hole. The diameter of the hemispherical groove (20) is 3 times the diameter of the pressure measurement hole. In this embodiment, the diameter of the pressure measurement hole is 1 mm.

[0042] Within a range of 2 times the diameter of the pressure measurement hole on the surface of the probe head (2) from the hemispherical groove (20), no divergence holes (15) are developed to avoid the influence of steam generated by transpiration cooling on the measurement accuracy.

[0043] The pressure measurement hole (19) of the probe head (2) is connected to the dynamic pressure sensor (18), and the signal generated by the dynamic pressure sensor (18) is transmitted through the cable (8).

[0044] The sleeve (3) has a three-layer structure, including the first wall - the divergence wall (10), the second wall - the impact wall (11), and the third wall - the flow-limiting wall (12). A first cooling channel is formed between the first wall - the divergence wall (10) and the second wall - the impact wall (11), a second cooling channel is formed between the second wall - the impact wall (11) and the third wall - the flow-limiting wall (12), and a third cooling channel is formed between the third wall - the flow-limiting wall (12) and the fourth wall - the outer wall surface of the probe rod (1). The above three cooling channels are water permeation channels for cooling water.

[0045] In this embodiment, the mounting base (4) is selected to be runway-shaped with a thickness of 3 mm. Two positioning holes (5) are opened on the mounting base (4), and the diameter of the positioning holes (5) is taken as 2 mm.

[0046] Six circumferential partition baffles (9) are evenly arranged circumferentially between the outer wall surface of the cooling water inlet pipe (6) and the first wall - the divergence wall (10) to reduce the negative impact of gravity on the uneven distribution of cooling water. The circumferential partition baffles penetrate through the second wall - the impact wall (11), the third wall - the flow-limiting wall (12), and the fourth wall - the outer wall surface of the probe rod (1), dividing the first cooling channel, the second cooling channel, the third cooling channel, and the cooling water return channel into 6 independent cooling regions circumferentially. The 6 cooling water return channels correspond to the 6 independent cooling regions one by one.

[0047] The cooling water outlet pipe (7) is connected to the main cooling water circuit, and timely discharges the cooling water whose temperature in the probe has risen to a certain degree but fails to flow into the third flow channel between the fourth wall - the outer wall surface of the probe strut (13) and the third wall - the flow - limiting wall surface (12). That is, through the convective heat transfer of the flowing cooling water, it further absorbs the part of the heat that cannot be completely absorbed during the transpiration cooling process, and thus better protects the dynamic pressure sensor (18).

[0048] On the surface of the first wall - the divergent wall surface (10), inclined divergent holes (15) are opened, which are evenly distributed circumferentially and staggered axially in a periodic manner, forming the first wall - the divergent wall surface (10) with uniformly dense divergent holes (15). The divergent holes (15) penetrate the first wall - the divergent wall surface (10), and the cooling water seeps out from the divergent holes to form the outer wall surface of the film evaporation cooling sleeve (3). In this embodiment, the inclination angle of the divergent holes (15) is 50°.

[0049] The divergent holes (15) are cylindrical holes with cloud - shaped protrusions on the inner wall, which enables the cooling water to seep out slowly to ensure good cooling effect. In this embodiment, the diameter of the divergent holes (15) is 0.1 mm, and the height of the protrusions on the inner wall is 0.02 mm.

[0050] On the surface of the second wall - the impact wall surface (11), impact holes (16) are evenly distributed. The impact holes (16) connect the first cooling channel and the second cooling channel. The cooling water passes through the second wall - the impact wall surface (11) from the second cooling channel and enters the first cooling channel, and conducts impact cooling on the first wall - the divergent wall surface (10). The impact holes (16) are straight holes, which are axially staggered and periodically distributed on the second wall - the impact wall surface (11). In this embodiment, the diameter of the impact holes is 0.15 mm.

[0051] Furthermore, on the surface of the third wall - the flow - limiting wall surface (12), several groups of flow - limiting holes (17) are evenly arranged circumferentially. Since the thermal environments at different axial positions of the probe strut (1) may be different, and the required flow rates are also different, different numbers of flow - limiting holes (17) can be opened at different axial positions of the probe strut (1) according to the thermal environment of the probe to control the flow rate of the cooling water entering different positions, thereby controlling the cooling effect at different positions. In this embodiment, the diameter of the flow - limiting holes (17) is 0.2 mm.

[0052] Furthermore, in the first cooling channel, turbulator columns (14) are provided, which are evenly distributed circumferentially and staggered axially in a periodic manner, forming a uniformly dense turbulator column group. The upper and lower end surfaces of the turbulator columns (14) are fixedly connected to the first wall - the divergent wall surface (10) and the second wall - the impact wall surface (11) to enhance the overall heat transfer performance. In this embodiment, the diameter of the turbulator columns (14) is 0.1 mm.

[0053] The present invention can select appropriate divergence hole layout parameters according to the actual temperature range of the high-temperature flow field, and select appropriate cooling water supply pressure according to the test environment pressure. It effectively combines three cooling methods: convective heat transfer cooling of cooling water, impingement cooling, and transpiration cooling, improving the cooling effect of the probe. It can cool both the probe strut and the probe head simultaneously, and the heat dissipation effect is sufficiently uniform and ideal, effectively improving the dynamic response ability and the upper limit of the working temperature (up to 2500 °C) of the pressure probe in a high-temperature environment.

Claims

1. A composite structure sweat cooling type high temperature water-cooled dynamic total pressure probe, comprising a probe support rod (1), a probe head (2), a sleeve (3), a mounting seat (4), a positioning hole (5), a cooling water inlet pipe (6), a cooling water outlet pipe (7), a cable (8), a circumferential partition baffle (9), a first wall surface - a diverging wall surface (10), a second wall surface - an impact wall surface (11), a third wall surface - a flow limiting wall surface (12), a fourth wall surface - an outer wall surface of the probe support rod (13), a dynamic pressure sensor (18), a pressure measuring hole (19), a hemispherical groove (20) and some interfering flow columns (14), a diverging hole (15), an impact hole (16), and a flow limiting hole (17); characterized in that: The probe head (2) is located at the top of the probe support rod (1), a pressure measuring hole (19) is opened on the surface of the probe head (2), a sleeve (3) is installed on the outside of the probe support rod (1), a mounting seat (4) is installed on the sleeve (3), a positioning hole (5) is provided on the mounting seat (4), a cooling water inlet pipe (6) and a cable (8) are both installed in the probe support rod (1), a cooling water outlet pipe (7) is installed on the sleeve (3) and behind the mounting seat (4), and the cable (8) is installed in the probe support rod (1) and on the outer side of the cooling water inlet pipe (6) close to the pressure measuring hole (19); The probe support rod (1) is a double-layer structure, the inner layer is connected to the cooling water inlet pipe (6) to form a cooling water inlet channel, and the outer layer is divided into six chambers by a circumferential partition baffle (9). These chambers are connected to the permeation channel to form the main flow channel for the axial return of cooling water. The chamber close to the pressure measuring hole (19) is equipped with a dynamic pressure sensor (18) and a cable (8); The outer diameter of the probe support rod (1) is 2 mm to 5 mm, and the outer diameter of the corresponding sleeve (3) is 4 mm to 10 mm. The two are welded into a whole, and the diameter of the cooling water inlet pipe (6) is 1 mm to 2 mm. The probe head (2) is a cylindrical part whose axial length from the top of the probe to the end face is three times the outer diameter of the probe support rod (1). A pressure measuring hole (19) is opened on the probe head (2) at a distance of one cylinder diameter from the top. A hemispherical groove (20) is dug on the probe surface with the pressure measuring hole (19) as the center to increase the insensitive angle of the pressure measuring hole. The diameter of the hemispherical groove (20) is three times the diameter of the pressure measuring hole. The diameter of the pressure measuring hole is 0.6 mm to 1.5 mm. The diffuse holes (15) are not developed within the range of 2 times the diameter of the pressure measuring hole from the surface of the probe head (2) to avoid sweating cooling to generate steam that affects the measurement accuracy; The pressure measuring hole (19) of the probe head (2) is connected to the dynamic pressure sensor (18), and the signal generated by the dynamic pressure sensor (18) is transmitted through the cable (8); The sleeve (3) has a three-layer structure, including a first wall surface-diverging wall surface (10), a second wall surface-impact wall surface (11), and a third wall surface-flow limiting wall surface (12); a first cooling channel is formed between the first wall surface-diverging wall surface (10) and the second wall surface-impact wall surface (11); a second cooling channel is formed between the second wall surface-impact wall surface (11) and the third wall surface-flow limiting wall surface (12); and a third cooling channel is formed between the third wall surface-flow limiting wall surface (12) and the fourth wall surface-probe support rod outer wall surface (13); the above three cooling channels are cooling water infiltration channels; The mounting seat (4) is in the shape of a racetrack, the thickness of the mounting seat (4) is 2 mm to 5 mm, two positioning holes (5) are formed on the mounting seat (4), and the diameter of the positioning holes (5) is 2 mm to 3 mm; Six circumferential partition baffles (9) are evenly arranged circumferentially between the outer wall surface of the cooling water inlet pipe (6) and the first wall surface—the divergent wall surface (10) to reduce the negative influence of gravity on the uneven distribution of cooling water. The circumferential partition baffles penetrate the second wall surface—the impact wall surface (11), the third wall surface—the flow limiting wall surface (12), and the fourth wall surface—the outer wall surface of the probe support rod (13), and divide the first cooling channel, the second cooling channel, the third cooling channel, and the cooling water return channel into six independent cooling areas along the circumferential direction. The six cooling water return channels correspond to the six independent cooling areas one by one. The cooling water outlet pipe (7) is connected to the cooling water main circuit, and timely discharges the cooling water whose temperature in the probe rises to a certain level but fails to flow into the third flow channel between the fourth wall surface—the outer wall surface of the probe support rod (13) and the third wall surface—the flow limiting wall surface (12), that is, the flowing cooling water further absorbs part of the heat that cannot be completely absorbed during the sweating cooling process through convective heat exchange, thereby better protecting the dynamic pressure sensor (18); The surface of the first wall surface - the diverging wall surface (10) is provided with inclined diverging holes (15), which are evenly distributed in the circumferential direction and periodically staggered in the axial direction, forming a first wall surface - the diverging wall surface (10) with evenly densely distributed diverging holes. The diverging holes (15) penetrate the first wall surface - the diverging wall surface (10), and cooling water seeps out from the diverging holes to form the outer wall surface of the liquid film evaporation cooling sleeve (3). The inclination angle of the diverging holes is 30° to 60°; The diverging hole (15) is a cylindrical hole with a cloud-shaped protrusion on the inner wall, so that the cooling water can seep out slowly to ensure a good cooling effect. The diameter of the diverging hole (15) is 0.05 mm to 0.15 mm, and the height of the inner wall protrusion is 0.01 mm to 0.03 mm. The second wall surface (impact wall surface) (11) is evenly distributed with impact holes (16), the impact holes (16) connect the first cooling channel and the second cooling channel, cooling water passes through the second wall surface (impact wall surface) (11) from the second cooling channel into the first cooling channel, and performs impact cooling on the first wall surface (divergence wall surface) (10), the impact holes (16) are straight holes, axially staggered and periodically distributed on the second wall surface (impact wall surface) (11), and the impact holes have a diameter of 0.1 mm to 0.3 mm; A plurality of groups of flow limiting holes (17) are evenly arranged on the surface of the third wall surface, the flow limiting wall surface (12), in the circumferential direction. Since the thermal environments at different axial positions of the probe support rod (1) may be different, the required flow rates may also be different. Different numbers of flow limiting holes (17) may be opened at different axial positions of the probe support rod (1) according to the thermal environments at which the probe is located, so as to control the flow rates of cooling water entering different positions, thereby controlling the cooling effects at different positions. The diameter of the flow limiting holes (17) is 0.2 mm to 0.4 mm. The first cooling channel is provided with spoiler columns (14), which are evenly distributed in the circumferential direction and staggered and periodically distributed in the axial direction to form a uniformly dense spoiler column group. The upper and lower end surfaces of the spoiler columns (14) are fixedly connected to the first wall surface (diverging wall surface) (10) and the second wall surface (impact wall surface) (11) to enhance the overall heat exchange performance. The diameter of the spoiler columns (14) is 0.1 mm to 0.2 mm.

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