High pressure gas turbine flowmeter

Abstract

This invention discloses a high-pressure gas turbine flow meter, comprising a housing, an impeller for measuring gas flow rate disposed inside the housing, and a vent seat for gas passage within the housing. The vent seat includes a first end and a second end, and a gas passage connecting the first and second ends is provided on the vent seat. The cross-sectional area of ​​the inlet end of the gas passage is larger than the cross-sectional area of ​​the outlet end of the gas passage. The impeller is disposed on the second end of the vent seat. Under the action of the vent seat, the gas inside the housing flows through the gas passage within the vent seat. Because the cross-sectional area of ​​the inlet end of the gas passage is larger than the cross-sectional area of ​​the outlet end of the gas passage, and the impeller is disposed on the vent seat corresponding to the outlet end of the gas passage, the vent seat increases the gas flow velocity, thereby increasing the gas velocity impacting the impeller. This effectively increases the impact force of the gas on the impeller, ensuring effective impeller rotation and improving the measurement accuracy of the gas flow rate.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of flow meter, in particular to a high-pressure gas turbine flow meter. BACKGROUND

[0002] The gas turbine flow meter is a speed type flow meter, which is installed in the gas flow pipeline to measure the gas flow. The structure of the existing gas turbine flow meter is shown in the figure: it includes a sleeve 1-1, which is connected in series in the gas flow pipeline during use. The inside of the sleeve 1-1 is provided with an impeller 1-2. When the flowing gas passes through the sleeve 1-1, the gas impacts the impeller 1-2, causing the impeller 1-2 to rotate. Therefore, the rotational speed of the impeller 1-2 is proportional to the gas flow through the sleeve 1-1. A sensor 1-3 is arranged on the outside of the sleeve 1-1. The sensor 1-3 measures the rotational speed of the impeller 1-2, thereby measuring the gas flow through the sleeve 1-1, achieving the purpose of measurement. In addition, flange sheets 1-4 are arranged at both ends of the sleeve 1-1, which are connected with the gas flow pipeline, thereby increasing the local connection strength and improving the sealing performance, making the use safer. Moreover, a guide vane 1-5 is arranged in front of the impeller 1-2. The impeller 1-2 is installed on the guide vane 1-5, which is installed on the inner wall of the sleeve 1-1. The guide vane 1-5 is parallel to the axial direction of the sleeve 1-1, so that the gas can directly impact the impeller 1-2. However, the above-mentioned structure of the gas turbine flow meter has certain defects in actual use: the impeller 1-2 completes rotation when the gas turbine flow meter reaches the measurement prerequisite, that is, the impact force of the gas on the impeller 1-2 reaches a certain strength. However, the density of the gas is relatively small, especially when the gas flow rate in the gas flow pipeline is low, the impact force of the gas on the impeller 1-2 cannot reach the expected strength, thereby failing to drive the impeller to rotate. Therefore, there is a certain error in actual measurement, which affects the measurement accuracy of the gas turbine flow meter. SUMMARY

[0003] The present application aims to avoid the shortcomings of the prior art and provide a high-pressure gas turbine flow meter, thereby effectively solving the shortcomings in the prior art.

[0004] In order to achieve the above object, the technical scheme adopted by the present application is as follows: a high-pressure gas turbine flowmeter, comprising a shell, an impeller for measuring the flow of gas is arranged in the shell, when the gas passes through the shell, the gas impacts the impeller to rotate, a gas passage seat for the gas to pass through is further arranged in the shell, the gas passage seat comprises a first end and a second end, a gas passage for connecting the first end and the second end is arranged on the gas passage seat, one end of the gas passage corresponding to the first end of the gas passage seat is an inlet end, one end of the gas passage corresponding to the second end of the gas passage seat is an outlet end, the cross-sectional area of the inlet end of the gas passage is greater than the cross-sectional area of the outlet end of the gas passage, the impeller is arranged on the second end of the gas passage seat, and the gas sprayed out of the outlet end of the gas passage impacts the impeller to make the impeller rotate.

[0005] Further, the internal cavity of the shell is arranged in a columnar shape, the shape of the gas passage seat is matched with the internal cavity of the shell, and the axial direction of the gas passage seat is parallel to the flow direction of the gas in the shell.

[0006] Further, the cross-sectional area of the gas passage continuously changes.

[0007] Further, the gas passage comprises a front section and a rear section, the front section and the rear section are connected, the front end of the front section corresponds to the inlet end of the gas passage, the rear end of the rear section corresponds to the outlet end of the gas passage, the rear end of the front section and the front end of the rear section are connected, the cross-sectional area of the front end of the front section is greater than the cross-sectional area of the rear end of the front section, and the cross-sectional area of the front end of the rear section is greater than the cross-sectional area of the rear end of the rear section.

[0008] Further, a column seat is arranged in the region corresponding to the rear section in the internal cavity of the gas passage seat, a gap is formed between the column seat and the corresponding region of the gas passage seat to form the rear section of the gas passage.

[0009] Further, the internal cavity of the rear section and the column seat are both arranged in a conical shape, the small end of the rear section is the front end thereof, the large end of the rear section is the rear end thereof, the small end of the column seat corresponds to the front end of the rear section, and the large end of the column seat corresponds to the rear end of the rear section.

[0010] Further, the front section of the gas passage is arranged in a conical shape, the large end of the gas passage corresponds to the front end of the front section, and the small end of the gas passage corresponds to the rear end of the front section.

[0011] Further, the inner wall of the rear section and the outer wall of the column seat are arranged in an arc shape along the gas flow direction.

[0012] Further, the impeller comprises a shaft seat, a plurality of blades are arranged on the shaft seat, the blades have a first surface and a second surface, the first surface faces the direction of the gas, and the second surface faces away from the direction of the gas, when the gas impacts the blades, the impeller rotates.

[0013] Further, the first surface and the second surface are both arranged in an arc shape and are curved towards the direction of rotation of the impeller.

[0014] The above technical scheme of the present application has the following beneficial effects: under the action of the vent seat, the gas in the shell flows through the gas passage in the vent seat, since the cross-sectional area of the gas inlet end of the gas passage is larger than the cross-sectional area of the gas outlet end of the gas passage, and the impeller is arranged at the end of the vent seat corresponding to the gas outlet end of the gas passage, the vent seat plays a role in increasing the flow rate of the gas, thereby making the flow rate of the gas impacting the impeller larger, effectively increasing the impact force of the gas on the impeller, thereby ensuring effective rotation of the impeller and improving the measurement accuracy of the gas flow. BRIEF DESCRIPTION OF DRAWINGS

[0015] Figure 1 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0016] Figure 2 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0017] Figure 3 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0018] Figure 4 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art; Figure 3

[0019] Figure 5 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0020] Figure 6 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0021] Figure 7 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0022] Figure 8 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0023] Figure 9 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art;

[0024] Figure 10 Fig. 1 is a structural schematic diagram of a gas turbine flowmeter in the prior art; Figure 9 DETAILED DESCRIPTION

[0025] The embodiments of the present application will be further described in conjunction with the drawings and examples. The following examples are used to illustrate the present application, but cannot be used to limit the scope of the present application.​​

[0026] In the description of this invention, unless otherwise stated, "a plurality of" means two or more; the terms "upper," "lower," "left," "right," "inner," "outer," "front end," "rear end," "head," "tail," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention. For those skilled in the art, the specific meaning of the above terms in this invention can be understood according to the specific circumstances.

[0027] like Figures 2-10 As shown in this embodiment, a high-pressure gas turbine flow meter is used to measure the gas flow rate in a gas flow pipeline. The high-pressure gas turbine flow meter is connected in series in the gas flow pipeline. Specifically, it includes a housing 1 with an internal cavity. Inside the housing 1, an impeller for measuring gas flow rate is installed. In practice, when gas flows through the internal cavity of the housing 1, the gas impacts the impeller, causing it to rotate. Furthermore, a measuring sensor 2 for measuring the impeller's rotational speed is installed outside the housing 1. The position of the measuring sensor 2 corresponds to the position of the impeller, thus measuring the impeller's rotational speed. When the flowing gas impacts the impeller, the impeller's rotational speed is proportional to the gas flow rate, thereby measuring the gas flow rate and achieving the measurement purpose. More specifically, a vent seat 3 for gas flow is installed inside the housing 1. The vent seat 3 is installed inside the internal cavity of the housing 1. More specifically, the vent seat 3 has a first end 4 and a second end 5. After actual installation, the gas flow... In the direction of flow, the first end 4 is located upstream of the second end 5. More specifically, an air passage is provided on the vent seat 3, which connects and penetrates the first end 4 and the second end 5 of the vent seat 3, thus forming a through cavity on the vent seat 3. The air passage has an inlet end and an outlet end. The inlet end of the air passage corresponds to the first end 4 of the vent seat 3, and the outlet end of the air passage corresponds to the second end 5 of the vent seat 3. Moreover, the cross-sectional area of ​​the inlet end of the air passage is larger than the cross-sectional area of ​​the outlet end of the air passage, and the impeller is located on the vent seat. At the second end 5 of 3, the gas ejected from the outlet end of the gas passage impacts the impeller to make it rotate. Therefore, when the gas flows through the vent seat 3, the gas velocity increases as the gas flows from the inlet end to the outlet end of the gas passage. When the gas velocity in the gas flow pipe is relatively slow, the gas flowing out from the outlet end of the gas passage can still maintain a considerable velocity, which can effectively increase the impact force of the gas on the impeller, enabling the impeller to rotate effectively. This suppresses the phenomenon that the impeller does not rotate when the gas velocity is low, which is beneficial to improving the metering accuracy.

[0028] In this embodiment, the internal cavity of the outer shell 1 is cylindrical, and the shape of the vent seat 3 is adapted to the internal shape of the outer shell 1. Furthermore, the axial direction of the vent seat 3 is parallel to the gas flow direction within the outer shell 1, thus avoiding corners and other structural features on the cavity wall that come into contact with the gas, preventing any impact on the gas flow rate. In this embodiment, the cross-sectional area of ​​the air passage continuously changes. Specifically, along the gas flow direction, that is, along the direction from the inlet end to the outlet end, the internal cross-sectional area of ​​the air passage gradually decreases, gradually increasing the gas flow velocity, which is beneficial for increasing the impact force on the impeller. More specifically, the air passage includes a front section 6 and a rear section 7. The front section of the air passage... Section 6 and section 7 are connected by a transitional link. The front end of section 6 corresponds to the air inlet of the air passage, and the rear end of section 7 corresponds to the air outlet of the air passage. The rear end of the front section and the front end of section 7 are connected. The cross-sectional area of ​​the front end of section 6 is larger than that of the rear end of section 6, and the cross-sectional area of ​​the front end of section 7 is larger than that of the rear end of section 7. In this embodiment, along the direction of air flow, that is, along the direction from the first end 4 of the vent seat 3 to the second end 5, the cross-sectional area of ​​the internal cavity of section 6 gradually and continuously decreases, and the cross-sectional area of ​​the internal cavity of section 7 gradually and continuously decreases. The flowing gas is continuously accelerated by section 6 and section 7 to improve the impact. The gas flow velocity on the impeller enables its effective rotation. More specifically, regarding the structure of the front section 6 and the rear section 7 of the air passage, preferably, a column seat 8 is provided inside the vent seat 3 in the region corresponding to the rear section 7. A gap is formed between the column seat 8 and the inner wall of the vent seat 3, which forms the rear section 7 of the air passage. Specifically, the internal cavity of the vent seat 3 corresponding to the rear section 7 and the column seat 8 are both conical. The small end of the rear section 7 is its front end, and the large end of the rear section 7 is its rear end. The small end of the column seat 8 corresponds to the front end of the rear section 7, and the large end of the column seat 8 corresponds to the rear end of the rear section 7. Moreover, the virtual axis of the internal cavity of the vent seat 3 corresponding to the rear section 7 and the column seat 8 are... The virtual axes coincide, causing the rear section 7 to form a diffused annular cross-section, resembling a trumpet wall. Moreover, the gap between the column base 8 and the ventilation seat 3 in this area gradually decreases along the gas flow direction to accelerate the gas. The inner wall of the ventilation seat 3 corresponding to the rear section 7 area and the outer wall of the column base 8 are arranged in an arc shape along the gas flow direction. The closer to the second end 5 of the ventilation seat 3, the more the gap direction between the column base 8 and the ventilation seat 3 in this area tends to be parallel to the axis of the ventilation seat 3. This means that the direction of the gas ejected from the rear end of the rear section 7 tends to be more parallel to the axis of the ventilation seat 3, allowing the gas to blow vertically against the impeller, which is more conducive to the rotation of the impeller.

[0029] In this embodiment, the front section 6 of the air passage is cone-shaped, with the large end of the air passage corresponding to the front end of the front section 6 and the small end corresponding to the rear end of the front section 6. This allows the gas line flowing through the vent seat 3 to be continuously and uniformly accelerated through the cone-shaped front section 6, and then accelerated through the diffused annular cross-section of the rear section 7, causing the effective impact area of ​​the gas to tend to diffuse outward. This effect will be further explained when the impeller structure is introduced later.

[0030] In this embodiment, the impeller includes a shaft seat 9, which is mounted on the large end of a column seat 8. Multiple blades 10 are disposed on the shaft seat 9. The axial direction of the shaft seat 9 coincides with the axial direction of the column seat 8, thus making the rotation direction of the blades 10 perpendicular to the gas flow direction. Specifically, each blade 10 has a first surface 11 and a second surface 12. The first surface 11 faces the gas flow direction, and the second surface 12 faces away from the gas flow direction. That is, when the gas ejected from the vent seat 3 impacts the blades 10, it impacts the first surface 11 of the blades 10. Both the first surface 11 and the second surface 12 are inclined. In the impeller's rotation direction, the second surface 12 faces the circumferential direction of the impeller's rotation, and the first surface 11 faces away from the circumferential direction of the impeller's rotation. That is, when the impeller rotates, the second surface 12 is in front, and the first surface 11 is behind. Specifically, the blades 10 have a twisted posture. For the area of ​​the blades 10 near the shaft seat 9, the first surface 11 of the blades 10... The orientation of surface 11 and the second surface 12 is more inclined toward the circumferential direction of impeller rotation. However, in the area where gas is ejected at the rear end of the rear section 7, that is, at the end of blade 10, the first surface 11 and the second surface 12 of blade 10 in this area tend to have a certain tilt angle so that the gas impacts the first surface 11 and applies a circumferential rotational impact force to the first surface 11. The impact force of the gas applies an axial force to the first surface 11 on the one hand, and a circumferential shear force to the first surface 11 on the other hand, thereby applying a circumferential force to the blade 10, causing the impeller to rotate. In this embodiment, the rear end of the rear section 7 and the blade 10 are positioned correspondingly, so that the gas ejected from the rear end of the rear section 7 can be sprayed onto the blade 10. The effective impact area of ​​the gas mentioned above tends to diffuse outward, so that the impact force point of the gas on the blade 10 is closer to the moving end of the blade 10, increasing the torque on the blade 10 and making it more conducive to the rotation of the impeller.

[0031] More specifically, both the first surface 11 and the second surface 12 of the blade 10 are arc-shaped and curved towards the direction of impeller rotation. The two sides of the first surface 11 and the two sides of the second surface 12 are seamlessly connected to form the cross-section of the blade 10. Both sides of the first surface 11 and the second surface 12 have rounded corners, allowing gas to flow smoothly over the blade 10. Furthermore, both the first surface 11 and the second surface 12 arch towards the direction of impeller rotation; that is, the first surface 11 arches towards the interior of the blade 10, making it a concave surface, while the second surface 12 arches away from the blade 10. The directional arch makes the second surface 12 convex, and the length of the second surface 12 is greater than the length of the first surface 11 on the cross section of the blade 10. Therefore, when the gas blows over the blade 10, the travel length of the gas on the second surface 12 is greater than the travel length on the first surface 11. As a result, the gas velocity on the second surface 12 will be greater than the gas velocity on the first surface 11. According to Bernoulli's principle, the pressure at the second surface 12 is less than the pressure at the first surface 11. This creates a pressure difference between the first surface 11 and the second surface 12 of the blade 10, which is more conducive to the rotation of the impeller and improves the metering accuracy.

[0032] More specifically, for the gap between the area of ​​the rear section 7 of the vent seat 3 and the column seat 8, a baffle 13 is provided in the gap. One side of the baffle 13 is connected to the inner wall of the vent seat 3 in this area, and the other side of the baffle 13 is connected to the outer wall of the column seat 8 to realize the connection between the vent seat 3 and the column seat 8. Multiple baffles 13 are arranged circumferentially, thereby forming multiple ventilation grooves 14 in the gap. Moreover, the ventilation grooves 14 are through structures along the gas flow direction. Furthermore, the width of the ventilation grooves 14 gradually decreases. Therefore, when the gas passes through the ventilation grooves 14, the gas can be further accelerated, further increasing the gas flow velocity impacting the blades 10, which is beneficial to the rotation of the impeller.

[0033] More specifically, regarding the vent seat 3 and impeller located inside the housing 1, the vent seat 3 is detachably installed inside the housing 1. Specifically, the outer wall of the vent seat 3 is adapted to the inner wall of the housing 1. A protruding ring 15 is provided at one end of the inner wall of the housing 1, allowing the vent seat 3 to be adapted to the internal cavity of the housing 1 along the other end of the housing 1. The protruding ring 15 restricts the vent seat 3 from disengaging at that end. For this purpose, flanges 16 can be provided at both ends of the housing 1. The flanges 16 and the housing 1 can be connected by welding or by screws. For the flange 16 at the end opposite to the end where the protruding ring 15 is provided, a raised flange 1 is provided on the flange 16. 7. The protruding edge 17 can extend into the housing 1 and abut against the end of the vent seat 3, thereby fixing the vent seat 3. Furthermore, the vent seat 3 can be threaded into the housing 1. After the vent seat 3 is screwed into the housing 1, one end of the vent seat 3 abuts against the protruding ring 15. Then, the flange 16 with the protruding edge 17 is installed on the housing 1, so that the protruding edge 17 abuts against the vent seat 3, improving the installation strength of the vent seat 3. In this embodiment, the protruding edge 17 and the end of the vent seat 3 can be engaged by a toothed structure to further restrict the rotation of the vent seat 3 and improve the installation stability.

[0034] The working principle of this invention: In actual use, the vent seat 3 is first axially fitted into the internal cavity of the vent seat 3, so that the second end 5 of the vent seat 3 abuts against the side of the convex ring 15. At this time, the blade 10 will not contact the inner wall of the convex ring 15, and there is a small gap between the end of the blade 10 and the inner wall of the convex ring 15 to avoid excessive gas flowing ineffectively in this area and to increase the impact force on the blade 10. Then, a flange 16 is set on the outer shell 1 at one end corresponding to the first end 4 of the vent seat 3. The flange 17 on the flange 16 abuts against the first end 4 of the vent seat 3. If the flange 17 and the vent seat The flange 16 and the outer shell 1 have a toothed mesh structure, allowing for proper meshing. The flange 16 and the outer shell 1 can be connected by welding or screws. A similar flange 16 is then installed at the other end. The outer shell 1 is then connected in series to the gas flow pipeline via the flange 16 connection, effectively increasing local pressure resistance and facilitating operation under high pressure conditions. After installation, the first end 4 of the vent seat 3 corresponds to the upstream of the gas, and the second end 5 of the vent seat 3 corresponds to the downstream of the gas. Installation is then complete. When gas flows through the interior of the outer shell 1, it first passes through the vent seat 3. The front section 6 of the internal air passage is a constricted cone shape, which accelerates the gas. The gas then passes through the rear section 7, which also accelerates the gas. This acceleration in the rear section 7 is achieved in two ways: firstly, the gap between the inner wall of the local cavity of the vent seat 3 and the outer wall of the column seat 8 gradually decreases, causing the effective cross-sectional area of ​​the gap to decrease along the gas flow direction, thus accelerating the gas; secondly, the width of the vent groove 14 formed by the baffle 13 gradually decreases along the gas flow direction, also contributing to gas acceleration. The increased speed of the gas impact on the blades 10 further enhances the impeller's rotation. Furthermore, due to the cross-sectional structure of the blades 10, the gas impacts the first surface 11, directly applying a rotational force. Because of the arc shape of the first and second surfaces 11, and because the path length of the gas flowing through the second surface 12 is greater than that flowing through the first surface 11, the pressure at the second surface 12 is lower than that at the first surface 12, creating a pressure difference between the two sides of the blades 10. This pressure difference exerts a circumferential rotational force on the blades 10, further facilitating impeller rotation.

[0035] It should be noted that the terms "one embodiment," "embodiment," "exemplary embodiment," "some embodiments," etc., mentioned in the specification indicate that the described embodiment may include a specific feature, structure, or characteristic, but not every embodiment necessarily includes that specific feature, structure, or characteristic. Furthermore, such phrases do not necessarily refer to the same embodiment. Moreover, when a specific feature, structure, or characteristic is described in connection with an embodiment, implementing such a feature, structure, or characteristic in conjunction with other embodiments, whether explicitly described or not, is within the knowledge scope of those skilled in the art.

[0036] It should be readily understood that “on,” “above,” and “on top of” in this disclosure should be interpreted in the broadest manner, such that “on” means not only “directly on something” but also “on something” with an intermediate feature or layer therebetween, and that “above” or “on top of” means not only “on something” but also “on something” without an intermediate feature or layer therebetween (i.e., directly on something).

[0037] Furthermore, for ease of explanation, spatially relative terms such as "below," "below," "under," "above," and "above" may be used to describe the relationship of one element or feature relative to other elements or features as shown in the figures. Spatially relative terms are intended to encompass different orientations of the device in use or operation other than those shown in the figures. The device may have other orientations (rotated 90 degrees or in other orientations), and the spatially relative descriptive terms used herein may be interpreted accordingly.

[0038] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0039] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A high pressure gas turbine flowmeter characterized by: The utility model provides a gas flow meter, comprising a shell, the inside of shell is provided with vane for metering gas flow, when gas passes through the shell, gas hits vane and rotates, the shell is further provided with aeration seat for gas passing, the aeration seat comprises first end and second end, the aeration seat is provided with the gas passage that communicates first end and second end, the one end of gas passage corresponds the first end of aeration seat, and the one end of gas passage corresponds the second end of aeration seat, the cross section area of the gas inlet end of gas passage is greater than the cross section area of the gas outlet end of gas passage, the vane is arranged on the second end of aeration seat, and the gas that sprays out the gas outlet end of gas passage hits the vane to make the vane rotate. The cross section area of the gas passage continuously changes. The gas passage comprises a front section and a rear section, the front section and the rear section are communicated, the front end of the front section corresponds the gas inlet end of the gas passage, the rear end of the rear section corresponds the gas outlet end of the gas passage, the rear end of the front end is connected with the front end of the rear section, the cross section area of the front end of the front section is greater than the cross section area of the rear end of the front section, and the cross section area of the front end of the rear section is greater than the cross section area of the rear end of the rear section.

2. A high pressure gas turbine flowmeter according to claim 1 wherein: The internal cavity of the shell is in a cylindrical shape, the shape of the aeration seat is matched with the internal cavity of the shell, and the axial direction of the aeration seat is parallel to the flow direction of the gas in the shell.

3. A high pressure gas turbine flowmeter according to claim 2 wherein: The internal cavity of the aeration seat corresponding to the rear section region is in a conical shape, the small end of the rear section is the front end thereof, the large end of the rear section is the rear end thereof, the small end of the column seat corresponds to the front end of the rear section, and the large end of the column seat corresponds to the rear end of the rear section.

4. A high pressure gas turbine flowmeter according to claim 3 wherein: The front section of the gas passage is in a conical shape, the large end of the gas passage corresponds to the front end of the front section, and the small end of the gas passage corresponds to the rear end of the front section.

5. A high pressure gas turbine flowmeter according to claim 4 wherein: The inner wall of the aeration seat corresponding to the rear section region and the outer wall of the column seat are arc-shaped along the gas flow direction.

6. A high pressure gas turbine flowmeter according to claim 5 wherein: The vane comprises a shaft seat, a plurality of blades are arranged on the shaft seat, the blades have a first surface and a second surface, the first surface faces the direction of the gas, and the second surface faces away from the direction of the gas, when the gas hits the blades, the vane rotates.

7. A high pressure gas turbine flowmeter according to claim 1 wherein: The first surface and the second surface are both arc-shaped and curved towards the rotating direction of the vane.

8. A high pressure gas turbine flowmeter according to claim 7 wherein: ​

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