Turbine flow meter

Abstract

The utility model relates to the technical field of flow detection, in particular to a turbine flowmeter. The turbine flowmeter comprises a main body, a rotating shaft, a turbine, a detection assembly and a driving assembly, an accommodating cavity for fluid to flow through is formed in the main body; the rotating shaft is located in the containing cavity and arranged in the fluid flowing direction. The rotating shaft is rotationally connected with the body. The turbine is located in the containing cavity and arranged on the rotating shaft. The detection assembly is located in the containing cavity and used for detecting the attack angle of the fluid to the blade so that the turbine flowmeter can determine the fluid flow according to the attack angle. When the turbine flowmeter is used for detection, the influence of a correction or compensation mechanism on the detection efficiency can be eliminated, the detection cost can be reduced, and the detection precision can be improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of flow detection, in particular to a turbine flowmeter. BACKGROUND

[0002] The turbine flowmeter is a very precise volumetric flow testing technology, which calculates the volumetric flow of fluid by measuring the speed of fluid driving the turbine to rotate, and has the advantages of high precision and large measurable flow range.

[0003] In actual operation, the turbine flowmeter utilizes the driving force of fluid on the turbine blades to drive the turbine to rotate. However, there is also a problem of energy loss when the turbine rotates, for example, the viscous resistance of the fluid and the friction of the mechanical parts (such as bearings) will cause energy loss, which affects the accuracy of the measurement results.

[0004] In order to improve the measurement accuracy, the turbine flowmeter usually adopts a correction or compensation mechanism, such as experimental calibration, mathematical model correction or sensor signal processing, to reduce the influence of factors such as fluid viscosity and bearing friction on the test accuracy. However, these correction or compensation mechanisms are more complicated, which is not conducive to improving the detection efficiency, and will increase the detection cost. CONTENT OF THE INVENTION

[0005] The embodiments of the present application at least provide a turbine flowmeter which can eliminate the influence of correction or compensation mechanism on detection efficiency, reduce detection cost and improve detection accuracy.

[0006] The embodiments of the present application provide a turbine flowmeter, which comprises:

[0007] a main body, a rotating shaft, a turbine and a detection assembly;

[0008] The main body is internally provided with a containing cavity for fluid flow;

[0009] The rotating shaft is located in the containing cavity and is arranged along the fluid flow direction, and the rotating shaft is rotationally connected with the main body;

[0010] The turbine is located in the containing cavity and is arranged on the rotating shaft;

[0011] The detection assembly is located in the containing cavity, and the detection assembly is used to detect the attack angle of the fluid on the blade, so that the turbine flowmeter determines the fluid flow according to the attack angle.

[0012] In an optional embodiment, the detection assembly comprises a plurality of pressure measurement holes, and the detection assembly obtains the attack angle through the pressure in the holes of the plurality of pressure measurement holes.

[0013] In an alternative embodiment, the detection assembly comprises a first pressure measuring hole, a second pressure measuring hole and a central pressure measuring hole, the first and second pressure measuring holes are symmetrically distributed relative to the central pressure measuring hole.

[0014] In an alternative embodiment, the detection assembly is arranged at the leading edge of the blade of the turbine.

[0015] In an alternative embodiment, further comprising a driving assembly, the driving assembly is located in the accommodating cavity and arranged at the rotating shaft, the driving assembly is used to drive the turbine to rotate according to the size of the angle of attack, so as to make the angle of attack zero.

[0016] In an alternative embodiment, the driving assembly is a driving motor, the driving assembly is used to output torque to the turbine to make it rotate.

[0017] In an alternative embodiment, the rotating speed of the driving assembly is consistent with the rotating speed of the turbine.

[0018] In an alternative embodiment, the driving assembly has a built-in speed measuring assembly.

[0019] In an alternative embodiment, the driving assembly is located downstream of the turbine.

[0020] In an alternative embodiment, the rotating shaft is located downstream of the turbine, one end of the rotating shaft is rotationally connected with the main body, and the other end is connected with the rear end of the turbine.

[0021] The above technical solutions of the present application have the following beneficial technical effects:

[0022] Compared with the turbine flow meter with correction or compensation mechanism, the turbine flow meter of the present application determines the fluid flow by detecting the angle of attack of the fluid on the blade. Since the force of the fluid on the blade changes when the angle of attack changes, it reflects the energy conversion efficiency and loss in the system. Therefore, by measuring the angle of attack, the energy loss in the system can be directly evaluated, and the flow rate can be determined by the angle of attack without relying on additional correction or compensation mechanism. This is conducive to eliminating the influence of correction or compensation mechanism on detection efficiency, and can improve detection accuracy and reduce detection cost.

[0023] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the following preferred embodiments are described in detail below, and the accompanying drawings are described as follows. BRIEF DESCRIPTION OF DRAWINGS

[0024] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiments. The drawings incorporated into the specification and form a part of the specification, which show the embodiments consistent with the present application, and are used to explain the technical solutions of the present application. It should be understood that the following drawings only show some of the embodiments of the present application, and therefore should not be regarded as a limitation on the scope, and for those skilled in the art, other related drawings can also be obtained without creative labor.

[0025] Figure 1 A structural schematic diagram of a turbine flowmeter provided by an embodiment of the present application is shown;

[0026] Figure 2 A structural schematic diagram of a detection assembly provided by an embodiment of the present application is shown;

[0027] Figure 3 A structural schematic diagram of another detection assembly provided by an embodiment of the present application is shown;

[0028] Figure 4 A structural schematic diagram of another turbine flowmeter provided by an embodiment of the present application is shown;

[0029] Figure 5 A structural schematic diagram of still another turbine flowmeter provided by an embodiment of the present application is shown;

[0030] Figure 6 A structural schematic diagram of a turbine flowmeter in the prior art is shown;

[0031] Figure 7 A schematic diagram of a velocity triangle based on Figure 6

[0032] A relationship diagram of fluid attack angle and lift force is shown; Figure 8

[0033] A schematic diagram of a velocity triangle based on Figure 9 Figure 8

[0034] In the drawings, 1, main body; 2, rotating shaft; 3, turbine; 31, blade; 4, detection assembly; 41, first pressure measurement hole; 42, second pressure measurement hole; 43, center pressure measurement hole; 5, driving assembly.DETAILED DESCRIPTION DETAILED DESCRIPTION

[0035] Various exemplary embodiments of the present application will now be described in detail below with reference to the drawings. It should be noted that the relative arrangement, numerical expressions and values of the components and steps set forth in these embodiments do not limit the scope of the present application unless otherwise specifically stated.​

[0036] The embodiments of the present application will be described in detail below with reference to the drawings, in which the same or similar components have the same or similar designations and functions throughout. The embodiments described below are examples in which the present application is applied. These are merely given by way of example, and the present application is not limited thereto. Based on the embodiments of the present application, all other embodiments obtained by a person skilled in the art without creative work fall within the scope of the present application.

[0037] The terms "first", "second" in the specification and claims of the present application can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise specified. In addition, "and / or" in the specification and claims means at least one of the connected objects, and the character " / ", generally means that the front and rear associated objects are in an "or" relationship.

[0038] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the purpose of facilitating the description of the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0039] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connection" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0040] Reference Figure 1 The embodiments of the present application provide a turbine flowmeter which can eliminate the influence of correction or compensation mechanism on detection efficiency, and can reduce detection cost and improve detection precision.

[0041] Specifically, the turbine flowmeter comprises:

[0042] a main body 1, an accommodation cavity for fluid flow is arranged in the inside of the main body 1;

[0043] a rotating shaft 2 located in the accommodating cavity and arranged along the fluid flow direction, and rotationally connected with the main body 1;

[0044] a turbine 3 located in the accommodating cavity and arranged on the rotating shaft 2;

[0045] a detection assembly 4 located in the accommodating cavity, and configured to detect an attack angle of the fluid to the blade 31, so that the turbine flowmeter determines the volume flow according to the attack angle.

[0046] In order to determine the volume flow, the volume flow satisfies the following formula:

[0047]

[0048] In the above formula, Q is the volume flow entering the turbine; R is the radius of the blade from the rotation center; A is the cross-sectional area of the fluid flowing in the accommodating cavity; α is the attack angle of the fluid to the blade; β is the relative fluid velocity angle of the fluid to the axial direction; and ω is the rotation speed of the turbine.

[0049] Since β is a fixed amount, R and A are both known parameters, and A can be measured in various ways, such as a traditional Hall sensor installed outside the shell to sense the magnetism of the turbine blade, or a tachometer coaxially installed with the turbine. Therefore, the flow Q can be obtained through the above formula.

[0050] It should be noted that when the fluid medium transmits driving force to the turbine blade, it must flow into the leading edge of the blade with a certain attack angle. The greater the attack angle, the greater the driving force generated. When the attack angle is zero, the driving force is zero. This is well known in the fields of aerodynamics and airfoil lift theory.

[0051] Compared with the turbine flowmeter with a correction or compensation mechanism, the turbine flowmeter of the embodiment of the application determines the volume flow by detecting the attack angle of the fluid to the blade. Since the force of the fluid to the blade changes when the attack angle changes, this reflects the energy conversion efficiency and loss in the system. Therefore, the energy loss in the system can be directly evaluated by measuring the attack angle, and the flow is determined by the attack angle, without relying on an additional correction or compensation mechanism. This is conducive to eliminating the influence of the correction or compensation mechanism on the detection efficiency, and can improve the detection precision and reduce the detection cost.

[0052] Optionally, the detection assembly 4 includes a plurality of pressure measurement holes, and the attack angle is obtained by the pressure in the holes of the plurality of pressure measurement holes. For example, the pressure measurement holes can be three, five, seven, or the like.

[0053] Reference Figure 2Optionally, the detection assembly 4 comprises three pressure measuring holes, namely a first pressure measuring hole 41, a second pressure measuring hole 42 and a center pressure measuring hole 43, the first pressure measuring hole 41 and the second pressure measuring hole 42 are symmetrically distributed relative to the center pressure measuring hole 43, and the pressures in the holes of the first pressure measuring hole 41, the second pressure measuring hole 42 and the center pressure measuring hole 43 satisfy the following formula:

[0054]

[0055] wherein C i is a constant coefficient which can be determined by theoretical analysis and experimental calibration; α is the angle of attack of the fluid to the blade; P O is the pressure in the center pressure measuring hole; P L is the pressure in the first pressure measuring hole; and P R is the pressure in the second pressure measuring hole.

[0056] That is, the detection assembly 4 is actually a three-hole angle measurement structure. The three-hole angle measurement does not need to directly contact the airflow, and has high measurement accuracy. This non-invasive measurement method has less disturbance to the airflow and can more truly reflect the airflow characteristics. Moreover, the three-hole angle measurement can realize real-time attack angle monitoring by rapidly collecting and processing pressure data, which is particularly important for systems that need to be dynamically adjusted. In addition, the design of the pressure measuring hole is relatively simple, the manufacturing cost is low, and it is easy to integrate into the existing system.

[0057] Referring to Figures 1 to 2 Optionally, the detection assembly 4 is arranged at the leading edge of the blade 31 of the turbine 3. In this way, the sensitivity and accuracy of the measurement can be improved. Specifically, the change of the attack angle is usually most significant when the fluid reaches the leading edge of the blade 31, so arranging the detection assembly 4 at the leading edge of the blade 31 of the turbine 3 can capture the subtle changes in the direction of the fluid, thereby improving the sensitivity and accuracy of the measurement. In addition, the leading edge of the blade 31 of the turbine 3 is the first part contacted by the fluid, so arranging the attack angle detection assembly 4 at this position can more directly and accurately reflect the attack angle of the airflow relative to the blade 31.

[0058] Optionally, it further comprises a driving assembly 5, the driving assembly 5 is located in the accommodating cavity and arranged on the rotating shaft 2, and the driving assembly 5 is used to drive the turbine 3 to rotate according to the size of the attack angle, so that the attack angle is zero. In this way, the measurement of the attack angle can be replaced by the measurement of the turbine speed. Compared with detecting the attack angle, detecting the turbine speed is not easily affected by the environment (temperature, pressure, etc.), and has higher accuracy, thereby facilitating the improvement of the measurement accuracy of the turbine flowmeter.

[0059] Correspondingly, the volumetric flow rate satisfies the following formula:

[0060]

[0061] In the above formula, Q is the volumetric flow rate into the turbine; R is the radius of the blade from the center of rotation; A is the cross-sectional area of the fluid flowing within the housing; β is the relative flow angle of the fluid to the axial direction; and ω is the rotational speed of the turbine.

[0062] In a specific implementation, the angle of attack can be determined by the pressure within the first pressure measuring hole 41 and the second pressure measuring hole 42. Specifically, when the pressure within the first pressure measuring hole 41 and the second pressure measuring hole 42 is equal, the angle of attack of the fluid to the blade 31 is zero. Accordingly, in a specific arrangement, the detection assembly 4 can cancel the pressure measuring hole 43, as shown, so as to reduce the design difficulty and cost. Figure 3

[0063] Optionally, the driving assembly 5 is a driving motor, and the driving assembly 5 is configured to output torque to the turbine 3 to rotate the turbine 3. Of course, the driving assembly 5 can also be other types of structures, such as a compressed air driving structure, a steam driving structure, etc.

[0064] Optionally, the rotational speed of the driving assembly 5 is consistent with the rotational speed of the turbine 3. That is, the rotational speed of the turbine 3 can be determined by measuring the rotational speed of the driving motor.

[0065] Optionally, the driving assembly 5 has a built-in speed measuring assembly. That is, the driving assembly 5 can detect the rotational speed of the turbine 3 through the built-in speed measuring assembly. Compared with an external speed measuring assembly, the built-in speed measuring assembly can provide more accurate speed feedback, which helps to improve the control accuracy of the system.

[0066] With reference to Figure 1 Optionally, the driving assembly 5 is located downstream of the turbine 3, so as to avoid occupying the space upstream of the turbine 3, thereby reducing the pressure loss and flow interference of the fluid when passing through, and avoiding affecting the detection accuracy of the detection assembly 4.

[0067] With reference to Figure 4 Optionally, the rotating shaft 2 is located downstream of the turbine 3, and one end of the rotating shaft 2 is rotationally connected to the main body 1, and the other end is connected to the rear end of the turbine 3. That is, the inlet of the housing can cancel the flow guide and support structure, which can reduce the turbulence at the inlet position, thereby eliminating the influence of the inlet turbulence on the angle of attack measurement.

[0068] Optionally, the turbine flowmeter further comprises a flow guide, and the flow guide is located within the housing and located upstream of the turbine 3. That is, the flow guide can be installed as an independent flow control device upstream of the turbine 3, which not only meets the requirement of inlet flow guide, but also reduces the turbulence at the inlet position, thereby eliminating the influence of the inlet turbulence on the angle of attack measurement. ​

[0069] Reference is made to Figure 5 Optionally, the blades 31 of the turbine 3 can be cylindrical or elliptical cylindrical, etc. In this way, the structure design of the blades 31 of the turbine 3 can be more flexible. Specifically, since the turbine 3 is driven by the driving assembly 5, the blades 31 are no longer needed to convert energy between the turbine 3 and the fluid, so the structure design of the blades 31 of the turbine 3 can be more flexible, which is conducive to reducing the design difficulty of the blades 31.

[0070] Optionally, the number of blades 31 of the turbine 3 is two, and the two blades 31 are symmetrically arranged relative to the axial direction of the turbine 3, which can keep the turbine 3 in balance. In this way, the cost can be reduced. Specifically, since the turbine 3 is driven by the driving assembly 5, the blades 31 are no longer needed to convert energy between the turbine 3 and the fluid, so the number of blades 31 of the turbine 3 can be reduced, which is conducive to reducing the cost.

[0071] For the sake of understanding, we will analyze the central idea of the present application as follows.

[0072] Reference is made to Figure 6 And Figure 7 , Figure 6 shows a cross section of a single-rotor turbine flowmeter, Figure 7 shows a velocity triangle of a single-rotor turbine flowmeter. Generally, we use the following notes in the description of the velocity triangle:

[0073] ω: turbine rotational speed;

[0074] R: radius of the blade from the center of rotation;

[0075] T: torque of the fluid medium acting on the turbine cascade;

[0076] work done by the turbine on the fluid flow per unit mass flow;

[0077] V: fluid velocity in the absolute coordinate system;

[0078] V x : axial component of V, using subscript x;

[0079] V t : tangential component of V, using subscript t;

[0080] W: flow velocity relative to the turbine cascade;

[0081] U: tangential wheel speed, equal to the radius R multiplied by the rotational speed w;

[0082] α: absolute fluid velocity angle of the fluid with the axial direction;

[0083] β: angle of relative fluid velocity to axial direction;

[0084] 1 : flow station representing single or first turbine stage inlet;

[0085] 2: flow station representing single or first turbine stage outlet.

[0086] Using a well-known theorem in turbomachinery, the "Euler turbine" equation, to describe the energy imparted by a turbine to the fluid medium passing through it:

[0087]

[0088] Under the current model assumption that the turbine cross-sectional radius is constant, R, the turbine inlet and outlet tangential velocities are the same, then:

[0089] U1 = U2 = ωR (2)

[0090] In the current analysis, the fluid enters the turbine cascade in the axial direction, and the tangential component of the absolute velocity at station 1 is zero. Therefore,

[0091] V 1t = 0 (3)

[0092] Or,

[0093]

[0094] In the above equation, Q is the volumetric flow rate into the turbine; A is the cross-sectional area of the fluid flowing in the containment cavity.

[0095] For simplicity, without loss of generality of the current analysis, we will assume that the cross-sectional area A of the flow into and out of the turbine cascade is the same. Then, the axial component of the absolute fluid velocity at the turbine machine outlet should be equal to the axial component at the turbine machine inlet, then:

[0096]

[0097] We consider the ideal case of zero loss and assume that the flow angle at the turbine machine blade outlet is the same as the turbine machine blade outlet metal flow angle, then, 2x , V 2t , ω, R and β form the following relationship:

[0098]

[0099] Combining equations (1) to (6), then:

[0100]

[0101] Or,

[0102]

[0103] Equation (8) is a well-known linear relationship between volumetric flow rate and turbine rotational speed.

[0104] If there are system losses in the turbine flowmeter, including blade profile viscous losses and bearing friction losses, etc., the accuracy of the linear relationship of equation (8) will be affected. That is, under steady conditions, the power transferred from the fluid medium to the turbine is equal to the losses associated with the rotation of the turbine.

[0105] In order to make the fluid medium transmit driving force to the turbine blade, it must flow into the blade leading edge with a certain angle of attack, which is well known in the field of aerodynamics, airfoil lift theory, etc., as shown in Figure 8 And the greater the angle of attack, the greater the driving force generated, and when the angle of attack is zero, the driving force is zero.

[0106] According to Figure 8 , the velocity triangle upstream of the turbine cascade can be drawn, as shown in Figure 9 .

[0107] According to Figure 9 , the following formula can be derived:

[0108] β1=β-α1 (9)

[0109] U1=ωR=V 1x tanβ1=V 1x tan(β-α) (10)

[0110]

[0111] In equation (12), the blade angle β is a fixed amount, R and A are known parameters, and ω can be measured. Accordingly, if the fluid angle of attack α is measured, the volumetric flow rate Q can be obtained through equation (12).

[0112] In this application, the fluid angle of attack can be obtained by using the three-hole angle measurement method. The three-hole angle measurement concept is embodied in the leading edge of the turbine blade, that is, the leading edge of the turbine blade has three pressure measurement holes, as shown in Figure 2 .

[0113] Figure 2 The first pressure measurement hole, the second pressure measurement hole and the center pressure measurement hole are shown, the first pressure measurement hole and the second pressure measurement hole are symmetrically distributed with respect to the center pressure measurement hole, and the pressures in the first pressure measurement hole, the second pressure measurement hole and the center pressure measurement hole satisfy the following formula:

[0114]

[0115] where C i is a constant coefficient that can be determined by theoretical analysis and experimental calibration; P O is the pressure inside the central pressure measurement hole; P L is the pressure inside the first pressure measurement hole; P R is the pressure inside the second pressure measurement hole.

[0116] It is further contemplated that if the rotation of the turbine is driven by a drive motor and the rotational speed of the motor (i.e. the rotational speed of the turbine) is controlled such that the measured angle of attack is zero, then the equation for calculating the flow rate is a regression to equation (8). In this state, the rotation of the turbine is driven by the motor instead of the fluid. This means that the relationship between the rotational speed of the turbine flow meter and the flow rate is no longer affected by any system losses. Because these losses require energy that is offset by the drive motor.

[0117] It is further contemplated that because the rotational speed of the drive motor is related to the rotational speed of the turbine, in a specific implementation, a drive motor with a built-in speed sensor can be used. The built-in speed sensor of the drive motor can be used to measure the rotational speed of the drive motor, and thus the rotational speed of the turbine. In this way, there is no need to add an additional speed measurement component, which helps to reduce cost and structural complexity.

[0118] It is further contemplated that because the purpose of controlling the rotational speed of the drive motor is to make the angle of attack zero, in a specific implementation, when the angle of attack is zero, the pressure inside the first pressure measurement hole 41 and the pressure inside the second pressure measurement hole 42 are equal. Therefore, the detection component 4 can cancel the pressure measurement hole 43 to reduce the design difficulty and cost.

[0119] It is further contemplated that if the guide and / or support structure of the inlet is removed, the turbine rotor is supported by the downstream structure alone, as shown in Figure 4 This design eliminates the influence of turbulence in the turbine rotor inlet on the measurement of the angle of attack, further improving the flow conditions into the turbine, so that the angle of attack measurement and motor control are more accurate and undisturbed. Of course, if the inlet guide is still needed, the guide can be installed as a separate flow control device upstream of the turbine rotor.

[0120] It is further contemplated that because of the introduction of the drive motor, there is no longer any energy conversion between the fluid and the turbine, and the number of turbine blades can be reduced. For example, the number of turbine blades can be reduced to two, maintaining the dynamic balance of rotation. Of course, the number of turbine blades can also be other numbers.

[0121] It is further contemplated that since the turbine is no longer a tool for exchanging energy with the fluid, the streamlining of the blade shape becomes unimportant. For example, each blade is a cylinder or an ellipse, as shown in Figure 5The blades can of course also take other easily machinable shapes.

[0122] It is intended that all such additional substitutions, modifications and variations be included within the scope of the application, which is defined by the following claims. Accordingly, any one or more of the above-described embodiments can be combined with any other embodiment(s), and the application is applicable to any apparatus producing a similar result.

[0123] The above description is only specific embodiments of the present application, but the protection scope of the present application is not limited thereto, and any person skilled in the art can easily think of changes or replacements within the technical scope disclosed by the present application, which should be included in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A turbine flow meter characterized by, The utility model relates to a kind of vortex flowmeter, including: Main body, rotating shaft, turbine and detection component; The inside of the main body is provided with containing cavity for fluid flow; The rotating shaft is located in the containing cavity and is arranged along the fluid flow direction, and the rotating shaft is rotationally connected with the main body; The turbine is located in the containing cavity and is arranged on the rotating shaft; The detection component is located in the containing cavity, and the detection component is used to detect the angle of attack of the blade by the fluid, so that the turbine flowmeter determines the fluid flow according to the angle of attack.

2. The turbine flow meter of claim 1, wherein, The detection component includes a plurality of pressure measuring holes, and the detection component obtains the angle of attack by the pressure in the holes of the plurality of pressure measuring holes.

3. The turbine flow meter of claim 2, wherein, The detection component includes a first pressure measuring hole, a second pressure measuring hole and a center pressure measuring hole, and the first pressure measuring hole and the second pressure measuring hole are symmetrically distributed with respect to the center pressure measuring hole.

4. The turbine flow meter of claim 1, wherein, The detection component is arranged at the leading edge of the blade of the turbine.

5. The turbine flow meter of claim 1, wherein, Further comprising: A driving component is located in the containing cavity and is arranged on the rotating shaft, and the driving component is used to drive the turbine to rotate according to the size of the angle of attack, so that the angle of attack is zero.

6. The turbine flow meter of claim 5, wherein, The driving component is a driving motor, and the driving component is used to output torque to the turbine to make it rotate.

7. The turbine flow meter of claim 6, wherein, The rotational speed of the driving component is consistent with the rotational speed of the turbine.

8. The turbine flow meter of claim 7, wherein, The driving component has an internal speed measurement component.

9. The turbine flow meter of claim 5, wherein, The driving component is located downstream of the turbine.

10. The turbine flow meter of claim 1, wherein, The rotating shaft is located downstream of the turbine, one end of the rotating shaft is rotationally connected with the main body, and the other end is connected with the rear end of the turbine.

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