Turbine, fluid supply system, and gas supply system

Abstract

To highly efficiently acquire energy from a pipe in which a compressive fluid circulates.SOLUTION: A turbine includes first and second blades which are supported in a pipe so as to be rotatable around a rotating axis direction orthogonal to a pipe axial direction of the pipe in which a compressive fluid circulates, and which are formed into hollow semi-spherical shapes having recessed curved faces for receiving a flow of the compressive fluid. In a state that the recessed curved face of the first blade is oriented to one side in the pipe axial direction, the recessed curved face of the second blade is oriented to the other side in the pipe axial, the first and second blades are arranged to be displaced in an orthogonal direction with respect to the pipe axial direction and the rotating axis direction while being partially overlapped on each other, and the overlap ratio of the first blade and the second blade with respect to the whole is set to an overlap ratio at which a choking phenomenon is not generated in the compressive fluid which circulates between the first and second blades.SELECTED DRAWING: Figure 6

Description

[Technical Field]

[0001] The present invention relates to a turbine and a fluid supply system. [Background technology]

[0002] Non-Patent Document 1 discloses a configuration in which a Savonius turbine is arranged on a water supply pipe to extract energy. [Prior art documents] [Non-patent literature]

[0003] [Non-Patent Document 1] S. Abdolkarim Payambarpour, Amir F. Najafi, Franco Magagnato, Investigation of deflector geometry and turbine aspect ratio effect on 3D modified in-pipe hydro Savonius turbine: Parametric study:, Renewable Energy 148(2020)44-59 Summary of the Invention [Problem to be solved by the invention]

[0004] There is no known configuration for extracting energy by placing a Savonius turbine in a pipe through which a compressible fluid such as gas flows, and when a turbine is placed in the pipe, it is desirable to obtain energy from the pipe with high efficiency.

[0005] In consideration of the above, an object of the present invention is to obtain energy with high efficiency from a pipe through which a compressible fluid flows. [Means for solving the problem]

[0006] A turbine according to a first aspect includes first and second blades each formed in a hollow hemispherical shape and having a concave curved surface that receives the flow of compressible fluid, the first and second blades being supported within a pipe through which a compressible fluid flows so as to be rotatable about a rotation axis direction that is perpendicular to a pipe axis direction of the pipe, the first and second blades having a concave curved surface that receives the flow of the compressible fluid, the first and second blades being arranged such that when the concave curved surface of the first blade faces one side in the pipe axis direction, the concave curved surface of the second blade faces the other side in the pipe axis direction, the first and second blades are arranged so as to be shifted in a direction perpendicular to the pipe axis direction and the rotation axis direction while partially overlapping each other, and the overall overlap ratio of the first and second blades is set to an overlap ratio that does not cause choking in the compressible fluid flowing between the first and second blades.

[0007] According to the first aspect, the concave curved surfaces of the first and second blades receive the flow of compressible fluid, causing the turbine to rotate in a predetermined direction of rotation, with the compressible fluid flowing between the first and second blades in an S-shape.

[0008] This allows not only the kinetic energy (dynamic pressure) of the compressible fluid in the pipe but also the pressure energy (static pressure) to be converted into rotational force. As a result, the configuration of the first aspect makes it possible to obtain energy with high efficiency from the pipe through which the compressible fluid flows.

[0009] In the configuration of the first aspect, the overlap ratio of the first and second blades relative to the entirety is set to an overlap ratio that does not cause choking in the compressible fluid flowing between the first and second blades.

[0010] The choking phenomenon is a phenomenon in which the flow velocity of the compressible fluid flowing between the first blade and the second blade reaches the sonic speed, causing the mass flow rate to plateau. Note that the choking phenomenon is specific to compressible fluids and does not occur in incompressible fluids.

[0011] In this way, in the configuration of the first aspect, the overlap rate is set to a level that prevents the mass flow rate from reaching a plateau, and therefore energy can be obtained with high efficiency from the pipe through which the compressible fluid flows.

[0012] A turbine according to a second aspect includes first and second blades each formed in a hollow hemispherical shape and having a concave curved surface that receives the flow of compressible fluid, the first and second blades being supported within a pipe through which a compressible fluid flows so as to be rotatable about a rotation axis direction that is perpendicular to a pipe axis direction of the pipe, the first and second blades having a concave curved surface that receives the flow of the compressible fluid, the first and second blades being arranged such that when the concave curved surface of the first blade faces one side in the pipe axis direction, the concave curved surface of the second blade faces the other side in the pipe axis direction, the first and second blades are arranged so as to be shifted in a direction perpendicular to the pipe axis direction and the rotation axis direction while partially overlapping each other, and the overlap rate of the first and second blades relative to the entirety of the first and second blades is 1% or more and 80% or less.

[0013] According to the second aspect, the concave curved surfaces of the first and second blades receive the flow of compressible fluid, causing the turbine to rotate in a predetermined rotation direction. At this time, the compressible fluid flows between the first and second blades in an S-shape.

[0014] This allows not only the kinetic energy (dynamic pressure) of the compressible fluid in the pipe but also the pressure energy (static pressure) to be converted into rotational force. As a result, the configuration of the first aspect makes it possible to obtain energy with high efficiency from the pipe through which the compressible fluid flows.

[0015] In the second aspect of the configuration, the overlap ratio of the first and second blades to the entire blade is 1% or more and 80% or less.

[0016] When the overlap rate exceeds 80%, the flow rate of the compressible fluid flowing between the first blade and the second blade increases, which is presumed to result in the following: A fluid pool is formed between the first blade and the second blade, which acts as resistance to the flow of the compressible fluid.

[0017] On the other hand, if the overlap ratio is less than 1%, the flow velocity of the compressible fluid flowing between the first blade and the second blade increases, leading to the following inference: That is, if the flow velocity of the compressible fluid flowing between the first blade and the second blade increases and the flow velocity reaches the speed of sound, it is inferred that a state in which the mass flow rate plateaus (i.e., choking) will occur. For this reason, it is inferred that if the overlap ratio is less than 1%, the efficiency of converting the energy of the compressible fluid in the pipe through which the compressible fluid flows into rotational force will decrease.

[0018] In the configuration of the second aspect, as described above, the overlap rate is 1% or more and 80% or less, so that energy can be obtained with high efficiency from the pipe through which the compressible fluid flows.

[0019] A turbine according to a third aspect is the turbine of the first or second aspect, wherein spacers are provided on one and the other sides of the first and second blades in the rotation axis direction.

[0020] In the turbine according to the third aspect, the spacer reduces the gap between the turbine and the inner wall of the pipe through which the compressible fluid flows, allowing the compressible fluid to flow efficiently between the first blade and the second blade. This allows not only the kinetic energy (dynamic pressure) of the compressible fluid in the pipe but also its pressure energy (static pressure) to be converted into rotational force. As a result, the configuration of the third aspect allows energy to be obtained with high efficiency from the pipe through which the compressible fluid flows.

[0021] The turbine of the fourth aspect is the turbine of the third aspect, wherein the first and second blades and the spacer are formed into a circular shape when viewed in the pipe axis direction, with the concave curved surface of the first blade facing one side in the pipe axis direction.

[0022] In the turbine according to the fourth aspect, the first and second blades and the spacer form a circular shape when viewed in the pipe axial direction. This allows the gap between the turbine and the inner wall of the pipe through which the compressible fluid flows to be small throughout the entire circumferential direction. Therefore, the compressible fluid flows efficiently between the first and second blades. This allows not only the kinetic energy (dynamic pressure) of the compressible fluid in the pipe but also its pressure energy (static pressure) to be converted into rotational force. As a result, the configuration of the fourth aspect allows energy to be obtained with high efficiency from the pipe through which the compressible fluid flows.

[0023] A fluid supply system according to a fifth aspect includes a pipe through which a compressible fluid flows, and the turbine according to any one of the first to fourth aspects, which is disposed in the pipe.

[0024] In this way, since the turbine according to any one of the first to fourth aspects is provided in a pipe through which a compressible fluid flows, energy is obtained with high efficiency from the pipe through which the compressible fluid flows.

[0025] A sixth aspect of the present invention provides the fluid supply system of the fifth aspect, wherein the turbine is disposed in the pipe provided upstream of a component that decompresses the compressible fluid in a governor.

[0026] Therefore, compared to a configuration in which the turbine is disposed in a pipe provided downstream of a component in the governor that decompresses the compressible fluid, energy can be obtained more efficiently from the pipe through which the compressible fluid flows. [Effects of the Invention]

[0027] The present invention has the above-mentioned configuration, and therefore has the excellent effect of being able to obtain energy with high efficiency from a pipe through which a compressible fluid flows. [Brief explanation of the drawings]

[0028] [Figure 1] 1 is a schematic diagram illustrating a configuration of a gas supply system according to an embodiment of the present invention. [Figure 2]FIG. 2 is a perspective view showing the configuration of the turbine according to the embodiment. [Figure 3] FIG. 2 is a front view showing the configuration of the turbine according to the embodiment. [Figure 4] FIG. 2 is a plan view showing the configuration of the turbine according to the embodiment. [Figure 5] FIG. 2 is a side view showing the configuration of the turbine according to the embodiment. [Figure 6] FIG. 2 is a cross-sectional plan view showing the configuration of the turbine according to the present embodiment. [Figure 7] FIG. 2 is a schematic diagram showing the flow of gas in the turbine according to the present embodiment and a comparative example. [Figure 8] 10 is a graph showing the evaluation results. DETAILED DESCRIPTION OF THE INVENTION

[0029] An example of an embodiment of the present invention will be described below with reference to the drawings.

[0030] <Gas Supply System 10> The configuration of a gas supply system 10 according to this embodiment will be described. Fig. 1 is a schematic diagram showing the configuration of a gas supply system 10 according to this embodiment. The gas supply system 10 is an example of a fluid supply system.

[0031] The gas supply system 10 is a system that supplies gas (i.e., gas). Specifically, the gas supply system 10 is a system that supplies city gas from a supply source (e.g., a gas manufacturing plant) to consumers (e.g., ordinary homes, commercial facilities, industrial facilities, etc.), and as shown in FIG. 1, includes a first gas pipe 11, a second gas pipe 12, a governor 20, and a turbine 50. In the gas supply system 10, the direction in which gas flows is referred to as the gas flow direction. Gas is an example of a compressible fluid. Liquids such as water are not considered to be compressible fluids.

[0032] The first gas pipe 11 is disposed on the supply source side (i.e., upstream side in the gas flow direction) of the second gas pipe 12 in the gas supply system 10. The first gas pipe 11 is a gas pipe through which city gas having a higher pressure than the gas pressure in the second gas pipe 12 flows.

[0033] The second gas pipe 12 is arranged on the consumer side (i.e., downstream in the gas flow direction) of the first gas pipe 11 in the gas supply system 10. The second gas pipe 12 is a gas pipe through which city gas having a lower pressure than the gas pressure in the first gas pipe 11 flows.

[0034] The governor 20 is disposed between the first gas pipe 11 and the second gas pipe 12 in the gas supply system 10. That is, the governor 20 is disposed downstream of the first gas pipe 11 in the gas flow direction and upstream of the second gas pipe 12 in the gas flow direction in the gas supply system 10.

[0035] The governor 20 functions as a pressure regulator that regulates the pressure of the gas flowing from the first gas pipe 11 to the second gas pipe 12 between the first gas pipe 11 and the second gas pipe 12. Specifically, the governor 20 reduces the pressure of the gas from the first gas pipe 11 and sends it to the second gas pipe 12.

[0036] The governor 20 has a gas flow component 26 including the gas pipe 22 and the governor body 24, and a housing 28. The housing 28 is a component that houses the gas flow component 26 including the gas pipe 22 and the governor body 24. The gas pipe 22 is an example of a pipe through which a compressible fluid flows.

[0037] The gas flow component 26 is a component that allows gas to flow, and includes the gas pipe 22, the governor body 24, and other components such as gas pipes and valves. The gas flow component 26 allows gas to flow from an inlet 25 to which the first gas pipe 11 is connected to an outlet 27 to which the second gas pipe 12 is connected (see arrows 20A, 20B, 20C, and 20D).

[0038] The governor body 24 is a component that reduces the pressure of the gas flowing through the gas flow component 26. The gas pipe 22 is provided upstream of the governor body 24 in the gas flow direction. Specifically, the gas pipe 22 is connected to the governor body 24 on the upstream side of the governor body 24 in the gas flow direction. The gas pipe 22 has a smaller flow path diameter (i.e., a cross-sectional area of ​​the flow path) than the components connected upstream of the gas pipe 22 in the flow direction and the components connected downstream of the gas pipe 22 in the flow direction (specifically, the governor body 24).

[0039] As will be described later, in the governor 20, a turbine 50 is disposed relative to the gas pipe 22. The gas flowing through the governor 20 is depressurized in the turbine 50 and then further depressurized in the governor body 24. Therefore, in the governor 20, the gas in the flow paths indicated by arrows 20A and 20B, the gas in the flow path indicated by arrow 20C, and the gas in the flow path indicated by arrow 20D gradually become lower in pressure in this order.

[0040] <Turbine 50> 2 to 6 are diagrams showing the configuration of the turbine 50. In order to show the configuration of the turbine 50, a part of the gas pipe 22 is cut away in FIG.

[0041] 2 to 6 is a prime mover that converts the energy of the gas flowing through the governor 20 into rotational force and extracts the energy. As shown in FIGS. 1 and 2, the turbine 50 is disposed in a gas pipe 22 provided in the governor 20.

[0042] In this embodiment, the turbine 50 is configured as a so-called Savonius turbine. Specifically, as shown in Figures 2 to 6, the turbine 50 has first blades 51, second blades 52, a first spacer 53, a second spacer 54, and a rotating shaft 55. Hereinafter, the first blades 51 and the second blades 52 may be referred to as "first and second blades 51, 52," and the first spacer 53 and the second spacer 54 may be referred to as "first and second spacers 53, 54."

[0043] The turbine 50 is a vertical-axis turbine, and its rotation axis 55 is disposed along a rotation axis direction Y that is perpendicular to the pipe axis direction X of the gas pipe 22. The first and second blades 51, 52 and the first and second spacers 53, 54 are supported in the gas pipe 22 by the rotation axis 55 so as to be rotatable around the rotation axis direction Y.

[0044] In each drawing, the tube axis direction X is indicated by an arrow X, and the rotation axis direction Y is indicated by an arrow Y. Furthermore, in each drawing, the orthogonal direction Z perpendicular to the tube axis direction X and the rotation axis direction Y is indicated by an arrow Z.

[0045] The first and second blades 51 and 52 are formed in a hollow hemispherical shape having concave curved surfaces 513 and 523 that receive the gas flow. That is, the first and second blades 51 and 52 have hemispherical spaces 518 and 528, the concave curved surfaces 513 and 523 (i.e., inner peripheral surfaces), convex curved surfaces 515 and 525 (i.e., outer peripheral surfaces), and end surfaces 514 and 524.

[0046] The first and second blades 51, 52 (including the concave curved surfaces 513, 523 and the convex curved surfaces 515, 525) are formed in an arc shape in a horizontal cross section (i.e., XZ cross section) as shown in Fig. 6. The inner diameters (i.e., the diameters of the concave curved surfaces 513, 523) and outer diameters (i.e., the diameters of the convex curved surfaces 515, 525) of the first and second blades 51, 52 are maximum at the center in the rotation axis direction Y and gradually decrease from the center in the rotation axis direction Y to one side (i.e., the upper side in Figs. 3 and 4) and the other side (i.e., the lower side in Figs. 3 and 4).

[0047] The thickness of the first and second blades 51, 52 is constant. However, the thickness of the first and second blades 51, 52 may vary. For example, the thickness of the first and second blades 51, 52 may be greatest at the center in the rotation axis direction Y and gradually decrease from the center in the rotation axis direction Y to one side (i.e., the upper side in Figures 3 and 4) and the other side (i.e., the lower side in Figures 3 and 4).

[0048] The first and second blades 51, 52 do not need to be perfectly hemispherical. For example, as described above, the first and second blades 51, 52 may be formed in an arc shape in horizontal cross section, with the inner and outer diameters being maximum at the center in the rotation axis direction Y and gradually decreasing from the center in the rotation axis direction Y to one side (i.e., the upper side in Figures 3 and 4) and the other side (i.e., the lower side in Figures 3 and 4).

[0049] As shown in FIG. 6 , in a state where the concave curved surface 513 and the end face 514 of the first blade 51 face one side in the tube axis direction X (hereinafter referred to as the first state), the concave curved surface 523 and the end face 524 of the second blade 52 face the other side in the tube axis direction X, and the first and second blades 51, 52 are arranged so as to be shifted in the perpendicular direction Z while partially overlapping each other.

[0050] The overlap ratio of the first and second blades 51, 52 relative to the entirety is set to an overlap ratio that does not cause choking in the gas flowing between the first and second blades 51, 52. Specifically, the overlap ratio of the first and second blades 51, 52 relative to the entirety is set in the range of 1% to 80%.

[0051] The choking phenomenon is a phenomenon in which the mass flow rate reaches a plateau when the flow velocity of the gas flowing between the first blade 51 and the second blade 52 reaches the speed of sound. The choking phenomenon is specific to compressible fluids such as gas, and does not occur with incompressible fluids (for example, liquids such as water).

[0052] Specifically, the overlap ratio is calculated by S / D×100 (see FIG. 6 ). S is the dimension of the gap between the first blade 51 and the second blade 52 in the orthogonal direction Z when the turbine 50 is in the first state. D is the overall dimension of the first blade 51 and the second blade 52 in the orthogonal direction Z when the turbine 50 is in the first state. Therefore, D can be understood as the diameter of the rotational trajectory of the turbine 50.

[0053] The first spacer 53 is provided on one side in the rotation axis direction Y (i.e., the upper side in Figures 3 and 4) of the first and second blades 51, 52. The first spacer 53 has a surface 536 on that side formed as a curved surface that is convex toward that side.

[0054] The second spacer 54 is provided on the other side in the rotation axis direction Y (i.e., the lower side in FIGS. 3 and 4) of the first and second blades 51, 52. The second spacer 54 has a surface 546 on the other side formed as a curved surface that is convex toward the other side.

[0055] 3, the turbine 50 is formed into a circular shape by the first and second blades 51, 52 and the first and second spacers 53, 54 when viewed in the pipe axis direction X. Specifically, the circular shape is preferably coaxial with the gas pipe 22. That is, it is preferable that the gap E between the turbine 50 and the inner wall of the gas pipe 22 has a constant dimension in the circumferential direction. Note that D is, for example, 110 mm or more and 120 mm or less, the inner diameter DA of the gas pipe 22 is, for example, 114 mm or more and 124 mm or less, and the gap E is, for example, about 2 mm.

[0056] In the turbine 50, the concave curved surfaces 513 and 523 of the first and second blades 51 and 52 receive the gas flow and rotate in a predetermined rotation direction (clockwise direction in FIG. 6). That is, the gas supply system 10 uses a system in which the turbine 50 rotates due to the drag force it receives from the gas in the gas pipe 22.

[0057] Furthermore, as described above, in the first state of the turbine 50, the concave curved surface 523 and the end surface 524 of the second blade 52 face the other side in the pipe axis direction X, and the first and second blades 51, 52 are arranged to be partially overlapping but shifted in the orthogonal direction Z (see FIG. 6 ). With this configuration, unlike when the turbine 50 does not have an overlapping portion (see FIG. 7C ), an S-shaped gas passage 59 through which gas flows is formed between the first and second blades 51, 52 (see FIG. 7B ). By forming the S-shaped gas passage 59 between the first and second blades 51, 52 in this way, the gas path reverses twice as shown in FIG. 7B , and the resulting reaction force can increase the torque of the first and second blades 51, 52.

[0058] Furthermore, unlike when the turbine 50 is arranged in an open space (see FIG. 7(A)), when the turbine 50 is arranged in the gas pipe 22, which is a closed space (see FIG. 7(B)), the flow is constrained by the gas pipe 22, causing the gas to flow intensively in the gas passage 59. At this time, the expansion of the compressed gas causes the gas flow in the gas passage 59 to become even faster, and a large reaction force is obtained.

[0059] Furthermore, because the gas flow is concentrated in the gas passage 59, the first and second blades 51, 52 have a self-starting property in that they start rotating naturally without the need for a running start from an external motor.

[0060] (Effects of this embodiment) In the gas supply system 10, the turbine 50 is a vertical axis turbine, and its rotation axis 55 is disposed along a rotation axis direction Y that is perpendicular to the pipe axis direction X of the gas pipe 22.

[0061] Here, when an axial flow turbine is used as the turbine 50, the rotation axis must be aligned with the central axis of the gas pipe 22. Therefore, in order to extract rotational energy from the gas pipe 22, it is necessary to take measures such as inserting a generator body into the gas pipe 22 or providing a device for converting the rotation axis.

[0062] In contrast, in the gas supply system 10, the turbine 50 is a vertical axis turbine, so the above measures are not necessary and the turbine 50 is easy to install in the gas pipe 22.

[0063] In the gas supply system 10, the concave curved surfaces 513 and 523 of the first and second blades 51 and 52 of the turbine 50 receive the flow of gas, causing the turbine 50 to rotate in a predetermined rotation direction (clockwise direction in FIG. 6). At this time, the gas flows between the first blade 51 and the second blade 52 in an S-shape (see FIG. 7(B)).

[0064] This makes it possible to convert into rotational force not only the kinetic energy (dynamic pressure) of the gas in the gas pipe 22 but also the pressure energy (static pressure). As a result, according to the configuration of the gas supply system 10, energy can be obtained from the gas pipe 22 with high efficiency.

[0065] In the configuration of this embodiment, the overlap ratio of the first and second blades 51, 52 relative to the entirety is set to an overlap ratio that does not cause a choking phenomenon in which the mass flow rate of the gas flowing between the first and second blades 51, 52 reaches a plateau. Therefore, energy can be obtained from the gas pipe 22 with high efficiency.

[0066] Specifically, in the configuration of this embodiment, the overlap ratio of the first and second blades 51, 52 to the entire blades is set in the range of 1% to 80%.

[0067] When the overlap rate exceeds 80%, the flow rate of gas flowing between the first blade 51 and the second blade 52 increases, which leads to the following: A gas pocket is formed between the first blade 51 and the second blade 52, which acts as a resistance to the gas flow.

[0068] On the other hand, if the overlap ratio is less than 1%, the flow velocity of the gas flowing between the first blade 51 and the second blade 52 increases, and the following is presumed to occur. That is, if the flow velocity of the gas flowing between the first blade 51 and the second blade 52 increases and the flow velocity reaches the speed of sound, it is presumed that a state in which the mass flow rate plateaus (i.e., choking) occurs. For this reason, it is presumed that if the overlap ratio is less than 1%, the conversion efficiency of converting the energy of the gas in the gas pipe 22 into rotational force decreases.

[0069] In the configuration of this embodiment, as described above, the overlap rate is 1% or more and 80% or less, so energy can be obtained from the gas pipe 22 with high efficiency.

[0070] In this embodiment, the first spacer 53 is provided on one side in the rotational axis direction Y (i.e., the upper side in FIGS. 3 and 4) of the first and second blades 51, 52. Furthermore, the second spacer 54 is provided on the other side in the rotational axis direction Y (i.e., the lower side in FIGS. 3 and 4) of the first and second blades 51, 52.

[0071] As a result, in the turbine 50, the first and second spacers 53, 54 reduce the gap E between the turbine 50 and the inner wall of the gas pipe 22, allowing the gas to flow efficiently between the first blade 51 and the second blade 52. This makes it possible to convert not only the kinetic energy (dynamic pressure) of the gas in the gas pipe 22 but also the pressure energy (static pressure) into rotational force. As a result, according to the configuration of this embodiment, energy can be obtained from the gas pipe 22 with high efficiency.

[0072] Furthermore, in this embodiment, in the first state, the turbine 50 is formed into a circular shape by the first and second blades 51, 52 and the first and second spacers 53, 54 when viewed in the pipe axis direction X, as shown in FIG.

[0073] This allows the gap E between the inner wall of the gas pipe 22 and the turbine 50 to be small over the entire circumferential direction. Therefore, the gas flows efficiently between the first blade 51 and the second blade 52. This allows not only the kinetic energy (dynamic pressure) of the gas in the gas pipe 22 but also the pressure energy (static pressure) to be converted into rotational force. As a result, according to the configuration of this embodiment, energy can be obtained from the gas pipe 22 with high efficiency.

[0074] Furthermore, in this embodiment, the turbine 50 is disposed in the gas pipe 22 provided upstream of the governor body 24, which is a component that depressurizes the gas in the governor 20. Therefore, energy can be obtained from the gas pipe more efficiently than in a configuration in which the turbine 50 is disposed in the gas pipe provided downstream of the governor body 24 in the governor 20.

[0075] <Modification> In this embodiment, the turbine 50 is formed in a circular shape when viewed in the pipe axis direction X as shown in Fig. 3 in the first state, but is not limited to this. It may be formed in a non-circular shape. Therefore, the gap E between the turbine 50 and the inner wall of the gas pipe 22 does not need to have a constant dimension in the circumferential direction.

[0076] In addition, in this embodiment, the turbine 50 includes the first and second spacers 53, 54, but this is not limitative. At least one of the first and second spacers 53, 54 may be omitted.

[0077] In addition, in this embodiment, the turbine 50 is disposed in the gas pipe 22 provided upstream of the governor body 24 in the governor 20, but this is not limiting. The turbine 50 may be disposed in another gas pipe in the governor 20, or in a gas pipe provided outside the governor 20, and the turbine 50 can be applied to various gas pipes.

[0078] In addition, in this embodiment, the turbine 50 has two blades, namely, the first and second blades 51 and 52, but this is not limiting. The turbine 50 may have three or more blades.

[0079] <Evaluation> In the turbine 50 according to this embodiment, the momentum multiplication factor was defined as an index that represents performance when the overlap ratio is changed, and evaluation was performed (see FIG. 8). Note that the "momentum multiplication factor" refers to the "ratio of the momentum of the fluid flowing in the overlap portion to the momentum of the fluid flowing in the general portion of the pipe," and the "overlap portion" refers to the "region between the first blade 51 and the second blade 52."

[0080] As a result, in the range where the overlap rate is 1% or more and 80% or less, the momentum multiplication factor exceeds 1.0 (see FIG. 8). Therefore, energy can be obtained from the gas pipe 22 with high efficiency.

[0081] The present invention is not limited to the above-described embodiment, and various modifications, changes, and improvements are possible without departing from the spirit of the present invention. For example, the above-described modified examples may be appropriately combined to form a configuration. [Explanation of symbols]

[0082] 10 Gas Supply System 11 First Gas Pipe 12 Second Gas Pipe 20 Governor 22 Gas Pipe 24 Governor body 25 Entrance 26 Gas flow component 27 Exit 28 Case 50 Turbine 51 First Blade 52 Second Blade 53 First spacer 54 Second spacer 55 Rotation axis 59 Gas passage 513 concave surface 514 end face 515 Convex Surface 518 Space 523 concave surface 524 end face 536 sides 546 sides

Claims

1. a first blade and a second blade each formed in a hollow hemispherical shape and having a concave curved surface that receives a flow of the compressible fluid, the first blade and the second blade being supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to a pipe axis direction of the pipe through which a compressible fluid flows, When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, an overlap ratio of the first and second blades relative to the entirety of the first and second blades is set to an overlap ratio at which a choking phenomenon does not occur in a compressible fluid flowing between the first and second blades, Spacers are provided on one and the other sides of the first and second blades in the rotation axis direction. Turbine.

2. a first blade and a second blade each formed in a hollow hemispherical shape and having a concave curved surface that receives a flow of the compressible fluid, the first blade and the second blade being supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to a pipe axis direction of the pipe through which a compressible fluid flows, When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, an overlap ratio of the first and second blades to the entire surface is 1% or more and 80% or less; Spacers are provided on one and the other sides of the first and second blades in the rotation axis direction. Turbine.

3. When the concave curved surface of the first blade faces one side in the pipe axis direction, the first blade, the second blade, and the spacer form a circular shape when viewed in the pipe axis direction. A turbine according to claim 1 or 2.

4. A pipe through which a compressible fluid flows; a turbine disposed within the pipe; Equipped with The turbine is disposed in the pipe upstream of a component in the governor that reduces the pressure of the compressible fluid; Further, the turbine a first blade and a second blade supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to the pipe axis direction, the first blade and the second blade having a hollow hemispherical shape and each having a concave curved surface that receives the flow of the compressible fluid; When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, an overlap ratio of the first and second blades relative to the entirety of the first and second blades is set to an overlap ratio that does not cause a choking phenomenon in the compressible fluid flowing between the first and second blades; Fluid supply system.

5. a pipe through which a compressible fluid flows; a turbine disposed within the pipe; Equipped with The turbine is disposed in the pipe upstream of a component in the governor that reduces the pressure of the compressible fluid; Further, the turbine a first blade and a second blade supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to the pipe axis direction, the first blade and the second blade having a hollow hemispherical shape and each having a concave curved surface that receives the flow of the compressible fluid; When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, The overlap rate of the first and second blades relative to the entire surface is 1% or more and 80% or less. Fluid supply system.

6. A gas supply system for supplying gas from a supply source to a consumer, comprising: A pipe through which gas flows; a turbine disposed within the pipe; Equipped with The turbine is the first and second blades are supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to the pipe axis direction, and are formed in a hollow hemispherical shape with a concave curved surface that receives the gas flow; When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, an overlap ratio of the first and second blades relative to the entirety of the first and second blades is set to an overlap ratio that does not cause a choking phenomenon in gas flowing between the first and second blades; Gas supply system.

7. A gas supply system for supplying gas from a supply source to a consumer, comprising: A pipe through which gas flows; a turbine disposed within the pipe; Equipped with The turbine is the first and second blades are supported within the pipe so as to be rotatable about a rotation axis direction perpendicular to the pipe axis direction, and are formed in a hollow hemispherical shape with a concave curved surface that receives the gas flow; When the concave curved surface of the first blade faces one side in the tube axis direction, the concave curved surface of the second blade faces the other side in the tube axis direction, and the first and second blades are arranged to be shifted in a direction perpendicular to the tube axis direction and the rotation axis direction while partially overlapping each other, The overlap rate of the first and second blades relative to the entire surface is 1% or more and 80% or less. Gas supply system.

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