chimney

Abstract

To provide a chimney capable of improving exhaust efficiency. [Solution] The chimney 100 has a pipeline through which exhaust gas G flows from a sub-pipe 30 to a main pipe 20. The sub-pipe 30 is connected to the main pipe 20, and the axis P2 of the sub-pipe 30 intersects the axis P1 of the main pipe 20 without sharing the same plane. An exhaust pipe E is connected to the sub-pipe 30 to guide exhaust gas G from an exhaust source. The exhaust gas G flowing from the sub-pipe 30 to the main pipe 20 forms a swirling flow within the main pipe 20, and the main pipe 20 constitutes a horizontal pipe that guides the exhaust gas G to the chimney body 10 which forms an upward flue 11, and is also connected to a pipeline that communicates with the chimney body 10.

Description

Technical Field

[0001] The present invention relates to a chimney, and particularly relates to improvement of exhaust efficiency.

Background Art

[0002] In chimneys that treat exhaust discharged from exhaust sources such as gas turbine engines, diesel engines, boilers, and waste incinerators installed in buildings, the exhaust from the exhaust source is guided through an exhaust pipe to a horizontal duct, and the horizontal duct guides the exhaust to the chimney main body that forms an upward flue. For this type of chimney, smoothly turning the direction of the exhaust to make it rise in the curved exhaust flow path extending from the horizontal duct flow path to the upward flue formed by the chimney main body is considered beneficial for reducing the resistance acting on the exhaust and improving the exhaust efficiency of the chimney.

[0003] Conventionally, in order to increase the discharge efficiency of the exhaust introduced into the flue, devices designed to swirl the exhaust inside the flue have been proposed. In the chimney disclosed in Patent Document 1, a plurality of flat flow deflectors are arranged at the outlet of the horizontal introduction pipe for introducing the exhaust sent from the exhaust source into the flue, in a vertical posture spaced at predetermined intervals and oriented obliquely forward, and an inclined surface is formed at the bottom of the flue. According to such a chimney, the exhaust sent from the exhaust source is converted into a swirling flow by the action of the flow deflectors while turning its direction from horizontal to upward, and is introduced into the flue. Thereby, the exhaust introduced into the flue rises through the flue while swirling, and the exhaust efficiency (discharge efficiency) of the chimney is considered to be improved.

[0004] Furthermore, conventionally, there are cases where the exhaust path from the exhaust source is a single system and cases where it is a multi-system system. In chimneys equipped with a multi-system exhaust path, the exhaust gases flowing from each exhaust path are sometimes collected into a single horizontal pipe and guided into a single chimney body. Patent document 2 describes an exhaust gas duct system for a gas turbine. In this system, exhaust gases from two exhaust sources, a gas turbine and a generator, are guided to a multi-system duct through separate exhaust gas ducts, and then collected in a confluence duct through two partitioned passages inside this multi-system duct before being introduced into the core of the chimney. [Prior art documents] [Patent Documents]

[0005] [Patent Document 1] Japanese Public Gazette No. 63-44667 [Patent Document 2] Japanese Patent Publication No. 64-57021 [Overview of the Initiative] [Problems that the invention aims to solve]

[0006] However, in the chimney proposed in Patent Document 1, the exhaust changes direction from sideways to upward and is converted into a swirling flow by the action of the deflection plate. This is thought to generate significant resistance that obstructs the exhaust flow, causing the momentum of the swirling flow to decay within a short time after it is generated.

[0007] Furthermore, in the exhaust gas duct system shown in Patent Document 2, if one attempts to process exhaust gas from more than two exhaust sources, it becomes necessary to increase the number of partitioned passages inside the multi-system duct according to the number of exhaust sources. This is considered to be a problem in that the structure of the multi-system duct becomes complex and exhaust resistance increases.

[0008] This invention has been made in view of the above circumstances, and aims to provide a chimney with good exhaust efficiency by enabling a swirling action to be imparted to the exhaust flow without the need for a flow deflector that obstructs the exhaust flow. Furthermore, it aims to provide a chimney with good exhaust efficiency by enabling a swirling action to be imparted to the exhaust flow without causing exhaust stagnation or backflow, even when exhaust is from two or more exhaust sources. [Means for solving the problem]

[0009] The chimney according to the present invention is a chimney having a pipeline through which exhaust gas flows from a secondary pipe to a main pipe, wherein the inner diameter of the main pipe is larger than the inner diameter of the secondary pipe, and the main In the pipe In contrast, the second The pipe At least one sub-pipe is connected to the main pipe, with an intersecting relationship at an angle smaller than a right angle. The axis of the secondary pipe is positioned relative to the axis of the main pipe with a displacement in the radial direction of the main pipe, The axis of the secondary pipe does not share the same plane with respect to the axis of the main pipe. The main pipe and the sub-pipe are The pipes intersect, and an exhaust pipe is connected to the sub-pipe to guide exhaust from the exhaust source. The exhaust flowing from the sub-pipe to the main pipe forms a swirling flow within the main pipe, and the main pipe forms a horizontal pipe that guides the exhaust to the chimney body, which forms an upward flue. It is also connected to a pipeline that communicates with the chimney body, and the swirling flow formed within the main pipe is guided to the chimney body through the main pipe.

[0010] With a chimney constructed in this way, the axis of the secondary pipe does not share the same plane with respect to the axis of the main pipe. The main pipe and the sub-pipe are Because they intersect, the axes are in a twisted position, so when exhaust flows from the secondary pipe to the main pipe, a swirling action is applied to the exhaust within the main pipe. Furthermore, the inner diameter of the main pipe is larger than the inner diameter of the secondary pipe, and the main In the pipe In contrast, the second The pipeThe intersecting relationship, which is at an angle smaller than a right angle, ensures a smooth exhaust flow path, maintains an appropriate flow velocity, and promotes the formation of a swirling flow. Furthermore, by connecting this to a pipeline that leads to the chimney body forming an upward flue, it is possible to exhaust the exhaust while maintaining its momentum. This allows for efficient exhaust processing without obstruction of the exhaust flow from the exhaust source.

[0011] In this invention, it is possible to adopt a configuration in which multiple sub-pipes are connected to the main pipe, such that their axes do not share the same plane. With this configuration, the exhaust pipes of multiple exhaust sources can be connected to the sub-pipes, and since the axes of each are in a twisted position, when exhaust flows from the multiple sub-pipes into the main pipe, a swirling action is applied to the exhaust from each sub-pipe within the main pipe, allowing for efficient exhaust processing even if there are multiple exhaust sources.

[0012] Furthermore, in the present invention, an elbow pipe is provided at the connection point between the chimney body and the main pipe, which has a lateral passage that communicates with the main pipe, an arc-shaped passage that communicates with the lateral passage, and a rising passage that communicates with the arc-shaped passage and discharges exhaust into an upward flue. The length from the connection point between the sub-pipe and the main pipe to the connection point between the main pipe and the elbow pipe is set so that the exhaust flowing from the sub-pipe into the main pipe maintains a swirling flow even within the elbow pipe. With this, in order to maintain a swirling flow of exhaust even within the bent elbow pipe, the length from the connection point between the sub-pipe and the main pipe to the connection point between the main pipe and the elbow pipe can be set to create an ideal swirling flow path. [Effects of the Invention]

[0013] According to the chimney of the present invention, by forming a swirling flow within the main pipe, the exhaust flow becomes smoother and exhaust resistance can be reduced. As a result, exhaust efficiency is improved, and the force of the exhaust is more easily maintained compared to conventional chimneys using a flow deflector. Furthermore, by adopting a configuration in which an elbow pipe is used at the connection point between the main pipe and the chimney body, the swirling flow formed in the main pipe can be easily maintained in the elbow pipe as well, allowing the exhaust flow to be guided more smoothly to the chimney body. Moreover, the length from the connection point between the sub-pipe and the main pipe to the connection point between the main pipe and the elbow pipe can be set so that the swirling flow of the exhaust within the elbow pipe becomes an ideal flow path. This reduces resistance when the exhaust changes direction, making it possible to improve the overall exhaust efficiency of the chimney. In addition, because the axes do not share the same plane, the exhaust flowing in from multiple sub-pipes is less likely to interfere with each other, and each can easily form an appropriate swirling flow within the main pipe. As a result, even if there are multiple exhaust sources, the exhaust is processed efficiently without exhaust stagnation or backflow. The chimney of the present invention generates a swirling flow without using members that obstruct the exhaust flow, such as deflection plates, resulting in a relatively simple structure and contributing to reduced manufacturing costs. Furthermore, it allows for flexibility in exhaust path design and is easily applicable to exhaust sources with different configurations. As described above, the chimney of the present invention reduces exhaust resistance by utilizing the swirling flow of exhaust, improves exhaust efficiency, and smoothly integrates exhaust from multiple exhaust sources. [Brief explanation of the drawing]

[0014] [Figure 1] This is a schematic perspective view showing a first embodiment of the chimney according to the present invention. [Figure 2] This is a view from arrow II in Figure 1. [Figure 3] This is a view from arrow III in Figure 1. [Figure 4] This is a view from arrow IV in Figure 1. [Figure 5] This is a schematic perspective view showing a second embodiment of the chimney according to the present invention. [Figure 6] This is a view from arrow V in Figure 5. [Figure 7] This is a view from arrow VI in Figure 5. [Figure 8] It is a view taken in the direction of arrow VII in Figure 5. [Figure 9] It is a schematic perspective view showing the third embodiment of the chimney according to the present invention. [Figure 10] It is a view taken in the direction of arrow VIII in Figure 9. [Figure 11] It is a view taken in the direction of arrow IX in Figure 9. [Figure 12] It is a view taken in the direction of arrow X in Figure 9. [Figure 13] It is a schematic front view of a chimney according to a comparative example. [Figure 14] It is a schematic plan view of the chimney according to the comparative example in Figure 13. [Figure 15] It is a graph showing a comparison of the diameter distribution of the axial exhaust gas flow velocity of the "central type chimney" and the "side end type chimney" in the main pipe. [Figure 16] It is a graph showing a comparison of the flow rates of the "central type chimney" and the "side end type chimney" in the main pipe. [Figure 17] It is a graph showing a comparison of the diameter distribution of the axial exhaust gas flow velocity of the "central type chimney" and the "side end type chimney" in the chimney body. [Figure 18] It is a graph showing a comparison of the flow rates of the "central type chimney" and the "side end type chimney" in the chimney body. [Figure 19] (A) is a schematic half-cut side view showing a "central type chimney" which is a chimney as a comparison object (comparative example), and (B) is a schematic half-cut side view showing a "side end type chimney" which is the chimney according to the first embodiment. [Modes for Carrying Out the Invention]

[0015] Figure 1 is a schematic perspective view showing a first embodiment of the chimney 100 according to the present invention, Figure 2 is a view taken along arrow II in Figure 1, Figure 3 is a view taken along arrow III in Figure 1, and Figure 4 is a view taken along arrow IV in Figure 1. In Figures 1 to 4, the upper part of the chimney body 10 that forms the upward flue 11 is omitted by the broken lines of the dashed-dots. The chimney body 10 is constructed by stacking multiple chimney units, each 4 to 5 meters high, in stages, and connecting adjacent chimney units by flange couplings or the like. Similarly, the exhaust pipes E, E on the exhaust source (not shown) side are omitted by the broken lines of the dashed-dots.

[0016] As shown in Figures 1 to 4, in the chimney 100 according to the first embodiment, one end of the main pipe 20 is connected via flanges F1, F1 to a pipeline communicating with the chimney body 10 which forms an upward flue 11. The other end of the main pipe 20 is closed, and one end of two sub-pipes 30, 30 that guide exhaust gases G, G from an exhaust source (not shown) to the main pipe 20 are welded to a location near the other end. Exhaust pipes E, E extending from an exhaust source (not shown) are connected to the other ends of the sub-pipes 30, 30 via flanges F2, F2 using bolts and nuts (not shown).

[0017] Furthermore, an elbow pipe 40 is provided at the connection point between the chimney body 10 and the main pipe 20, which is a pipeline that communicates with the chimney body 10. Specifically, one end of the elbow pipe 40 is connected to the lower end of the chimney body 10 via flanges F3, F3, and the other end of the elbow pipe 40 is connected to one end of the main pipe 20 via flanges F1, F1.

[0018] As shown in Figure 4, the elbow pipe 40 is equipped with a lateral passage 40a communicating with the main pipe 20, an arc-shaped passage 40b communicating with the lateral passage 40a, and a rising passage 40c communicating with the arc-shaped passage 40b. It redirects the exhaust gases G, G from the main pipe 20, which constitutes a lateral pipe connected to the chimney body at approximately a right angle, and guides them to the upward flue 11.

[0019] Thus, the chimney 100 has a pipeline that guides exhaust gas G, G from exhaust pipes E, E extending from an exhaust source (not shown) through sub-pipes 30, 30 to the main pipe 20, which is composed of horizontal pipes, and further guides it through an elbow pipe 40 to the cylindrical chimney body 10 which forms an upward flue 11. As shown in Figure 2, the inner diameter D1 of the main pipe 20 is larger than the inner diameter D2 of the sub-pipe 30. Also, as shown in Figure 3, the axes P2, P2 of the sub-pipes 30, 30 are at an angle θ smaller than a right angle with respect to the axis P1 of the main pipe 20. Main and sub-managers The sub-pipes 30, 30 are connected to the main pipe 20 in an intersecting configuration. Furthermore, as shown in Figure 2, the axes P2, P2 of the sub-pipes 30, 30 do not share the same plane with respect to the axis P1 of the main pipe 20. Main and sub-managers They intersect. In other words, the axes P2, P2 of the sub-pipes 30, 30 are offset by a distance a in the radial direction of the main pipe 20 with respect to the axis P1 of the main pipe 20. Here, the intersection angle θ between the axis P1 of the main pipe 20 and the axes P2, P2 of the sub-pipes 30 is called the "intersection angle θ," and the distance a of the above-mentioned displacement is called the "displacement width a."

[0020] As shown in Figures 1 to 4 of the first embodiment, the axes P2, P2 of the sub-pipes 30, 30 intersect at an angle θ with respect to the axis P1 of the main pipe 20. Main and sub-managers When the main pipe 20 and its sub-pipes 30, 30 have a misalignment of P2, P2 relative to the axis P1 of the main pipe 20, it can be said that the axis P1 of the main pipe 20 and the axes P2, P2 of the sub-pipes 30, 30 cannot exist on the same plane; in other words, they are in a twisted position where they cannot share the same plane. In the first embodiment shown in Figures 1 to 4, the two sub-pipes 30, 30 are provided at two locations that are rotationally symmetrical around the axis P1 of the main pipe 20. The axes of these two sub-pipes 30, 30 do not share the same plane and are in a twisted position.

[0021] Next, a second embodiment of the present invention will be described. Figure 5 is a schematic perspective view showing the second embodiment of the chimney 100 according to the present invention, Figure 6 is a view taken along arrow V in Figure 5, and Figure 7 is a view taken along arrow VI in Figure 5. Figure 8 is a view taken along arrow VII in Figure 5. Note that parts identical to those in the first embodiment are denoted by the same reference numerals, and redundant explanations are omitted.

[0022] In the chimney 100 according to the second embodiment shown in Figures 5 to 8, the difference from the chimney 100 of the first embodiment described above is that the two sub-pipes 30, 30 of the chimney 100 of the first embodiment are replaced with a single sub-pipe 30. Specifically, one end of a single sub-pipe 30 that guides exhaust G from an exhaust source (not shown) to the main pipe 20 is welded to a location near the other end of the closed main pipe 20, and the other end of the sub-pipe 30 is connected to an exhaust pipe E extending from an exhaust source (not shown) via a flange F2 using bolts and nuts (not shown).

[0023] Furthermore, as shown in Figure 6, the inner diameter D1 of the main pipe 20 is larger than the inner diameter D2 of the sub-pipe 30. Also, as shown in Figure 7, the axis P2 of the sub-pipe 30 intersects the axis P1 of the main pipe 20 at an angle θ smaller than a right angle. Main and sub-managers The sub-pipe 30 is connected to the main pipe 20 in an intersecting configuration. Furthermore, the axis P2 of the sub-pipe 30 has a displacement width a relative to the axis P1 of the main pipe 20.

[0024] As shown in the second embodiment in Figures 5 to 8, the axis P2 of the sub-pipe 30 intersects the axis P1 of the main pipe 20 at an angle θ. Main and sub-managers When the pipes intersect and the axis P2 of the sub-pipe 30 has a displacement of a relative to the axis P1 of the main pipe 20, as explained with reference to Figures 1 to 4, the axis P1 of the main pipe 20 and the axis P2 of the sub-pipe 30 cannot exist on the same plane; in other words, they are in a twisted position where they cannot share the same plane.

[0025] Next, a third embodiment of the present invention will be described. Figure 9 is a schematic perspective view showing the second embodiment of the chimney 100 according to the present invention, Figure 10 is a view taken along arrow VIII in Figure 5, and Figure 11 is a view taken along arrow IX in Figure 5. Figure 12 is a view taken along arrow X in Figure 5. Note that parts identical to those in the first embodiment are denoted by the same reference numerals, and redundant explanations are omitted.

[0026] As shown in Figures 9 to 12, in the third embodiment, the chimney 100 has a cylindrical chimney body 10 forming an upward flue 11, to which one end of the main pipe 20, which constitutes a horizontal pipe that guides exhaust G to the chimney body 10, is connected at approximately a right angle via a flange F1 using bolts and nuts (not shown). The other end of the main pipe 20 is closed, and near the other end, one end of two sub-pipes 30, 30 that guide exhaust G, G from an exhaust source (not shown) to the main pipe 20 is connected by welding. Exhaust pipes E, E extending from an exhaust source (not shown) are connected to the other ends of the sub-pipes 30, 30 via flanges F2, F2 using bolts and nuts (not shown).

[0027] Furthermore, an elbow pipe 40, indicated by a dashed line, is provided at the connection point between the main pipe 20 and the chimney body 10. As shown in Figure 12, the elbow pipe 40 has a lateral passage 40a communicating with the main pipe 20, an arc-shaped passage 40b communicating with the lateral passage 40a, and a rising passage 40c communicating with the arc-shaped passage 40b and releasing exhaust gas G into the upward flue 11. The elbow pipe 40 redirects the exhaust gas G, G from the main pipe 20, which is a lateral pipe connected to the chimney body at approximately a right angle, and guides it to be released into the upward flue 11 from the outlet 40d of the elbow pipe 40.

[0028] Other aspects, such as the intersection angle θ and the positional displacement width a, are the same as those described in the first embodiment in Figures 1 to 4.

[0029] Next, a comparative example will be described. Figure 13 is a schematic front view showing chimney 100 (comparative example) as a comparison, and Figure 14 is a schematic top view of the same. Note that parts identical to those in the first embodiment are denoted by the same reference numerals, and redundant explanations are omitted.

[0030] The comparative example chimney 100 shown in Figures 13 and 14 has a configuration similar to that of the chimney 100 of the first embodiment described above, and the intersection angle θ is also similar as shown in Figure 14. However, the difference in this comparative example is that it does not have the positional displacement width a found in the chimney 100 of the first embodiment. Specifically, as shown in Figure 13, there is no positional displacement width a between the axis P1 of the main pipe 20 and the axes P2, P2 of the auxiliary pipes 30, 30, as shown in Figure 2. In this comparative example, although the axes P2, P2 of the auxiliary pipes 30, 30 intersect the axis P1 of the main pipe 20 at an intersection angle θ, if there is no positional displacement width between the axis P1 of the main pipe 20 and the axes P2, P2 of the auxiliary pipes 30, 30, then it can be said that the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipes 30 can exist on the same plane, or in other words, they can share the same plane (a relationship that is not a twisted position).

[0031] In the first to third embodiments described above, the axis P2 of the auxiliary pipe 30 intersects the axis P1 of the main pipe 20 with an intersection angle θ, and the axis P2 of the auxiliary pipe 30 has a positional displacement a relative to the axis P1 of the main pipe 20, so that the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipe 30 cannot share the same plane (they are in a twisted position). This state of the chimney 100 is referred to as a "side-end type chimney 100". In contrast, in the comparative examples shown in Figures 13 and 14, although the axis P2 of the auxiliary pipe 30 intersects the axis P1 of the main pipe 20 with an intersection angle θ, there is no positional displacement between the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipe 30, that is, the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipe 30 can share the same plane (they are not in a twisted position). This configuration of chimney 100 will be referred to as "central type chimney 100".

[0032] Next, we will consider the exhaust flow between the side-end type chimney 100 and the central type chimney 100. In the side-end type chimney 100 shown in each of the first to third embodiments, the axis P2 of the auxiliary pipe 30 intersects the axis P1 of the main pipe 20 at an angle θ. Main and sub-managersBecause the pipes intersect and the axis P2 of the sub-pipe 30 has a positional misalignment a relative to the axis P1 of the main pipe 20, and the axis P1 of the main pipe 20 and the axis P2 of the sub-pipe 30 are in a relationship where they cannot share the same plane (they are in a twisted position), the exhaust G introduced from the sub-pipe 30 into the main pipe 20 becomes a swirling flow along the inner surface of the main pipe 20, and is thought to exert a propulsive effect toward the downstream side.

[0033] In contrast, in the central chimney 100 shown in the comparative example, although the axis P2 of the auxiliary pipe 30 intersects the axis P1 of the main pipe 20 at an angle θ, there is no positional misalignment between the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipe 30. In other words, the axis P1 of the main pipe 20 and the axis P2 of the auxiliary pipe 30 share the same plane (they are not in a twisted position). Therefore, it is thought that the exhaust G introduced from the auxiliary pipe 30 into the main pipe 20 exerts a propulsive effect toward the downstream side. However, in terms of whether the exhaust G becomes a swirling flow along the inner surface of the main pipe 20, it is unlikely that a swirling flow will occur, and it is thought that it will be a normal linear flow.

[0034] In the case of the central chimney 100 shown in the comparative example, if the exhaust G is a normal linear flow, boundary layers and turbulence are likely to occur along the inner surface of the main pipe 20, etc., which is thought to reduce exhaust efficiency. In contrast, if the exhaust G is a swirling flow, as in the side-end chimney 100 shown in the first to third embodiments, the development of boundary layers and fine turbulence along the inner surface of the main pipe 20, etc. is suppressed, and exhaust efficiency is likely to be maintained. From this, it can be inferred that the exhaust efficiency of the side-end chimney 100 will surpass that of the central chimney 100.

[0035] Therefore, the diameter distribution of the axial exhaust flow velocity in the main pipe 20 was compared between the side-end type chimney 100 and the central type chimney 100, and the results are shown in Figure 15. Figure 15 is a graph comparing the diameter distribution of the axial exhaust flow velocity in the "central type chimney 100" and the "side-end type chimney 100" in the main pipe 20, with the vertical axis representing wind speed and the horizontal axis representing radius (distance from the central axis of the main pipe). The measurement method was performed using experimental models manufactured based on the chimney 100 type with a combination of two sub-pipes 30 and a main pipe 20 common to the chimney 100 of the first or third embodiment, and the comparative example type shown in Figures 13 and 14. Specifically, the main pipe 20 and the two sub-pipes 30 were made as cylindrical bodies, and one end of the cylindrical body corresponding to the main pipe 20 was left open. Furthermore, a motor-driven first blower and a second blower were installed at the other end of the cylindrical bodies corresponding to each sub-pipe 30, and air was supplied. Inverters were used to control the first and second blowers, and the input frequencies were controlled using operating patterns with combinations of 17Hz-00Hz, 34Hz-00Hz, 00Hz-17Hz, 00Hz-34Hz, 17Hz-17Hz, 34Hz-17Hz, and 34Hz-34Hz. The flow velocity in each operating pattern was measured using an ultrasonic anemometer by placing a probe at the outlet of the cylindrical body corresponding to each main pipe 20. The graph in Figure 15 shows the measurement results for the 34Hz-34Hz operating pattern among the operating patterns with combinations of input frequencies for each blower.

[0036] According to the measurement results for the 34Hz-34Hz operating pattern shown in Figure 15, the diameter distribution of exhaust velocity in the main pipe 20 shows that the central chimney 100 has a slightly faster wind velocity in the center than the side-end chimney 100, but the wind velocity decreases significantly as you move away from the center. Since the main pipe 20 is a cylindrical body and its cross-sectional area increases as you move away from the center, even if the wind velocity is high in the center, it does not necessarily translate to an advantage in exhaust efficiency, and if the wind velocity decreases significantly as you move away from the center, the overall exhaust efficiency may decrease. On the other hand, although the wind velocity in the center of the side-end chimney 100 is slightly lower than that of the central chimney 100, the decrease in wind velocity is less even at points away from the center, and the exhaust distribution is more uniform, so the overall exhaust efficiency may be better than that of the central chimney 100. This trend was also observed in other operating patterns.

[0037] Then, using measurement data of the diameter distribution of the axial exhaust flow velocity in the main pipe 20 for each of the above combinations of input frequencies to the blower, the exhaust flow rate in the main pipe 20 obtained for each operation pattern was compared between the side-end type chimney 100 and the central type chimney 100, and the results are shown in Figure 16. Figure 16 is a graph comparing the flow rates of the "central type chimney 100" and the "side-end type chimney 100" in the main pipe 20. According to this, in all operation patterns of the blower, the exhaust flow rate in the main pipe 20 tends to be higher for the side-end type chimney 100 than for the central type chimney 100.

[0038] Based on the exhaust flow rate shown in Figure 16, which was obtained using measurement data of the diameter distribution of exhaust flow velocity in the axial direction of the main pipe 20, it can be said that the side-end type chimney 100 is superior to the central type chimney 100 in terms of exhaust efficiency.

[0039] Next, the diameter distribution of the axial exhaust flow velocity in the chimney body 10 was compared between the side-end type chimney 100 and the central type chimney 100, and the results are shown in Figure 17. Figure 17 is a graph comparing the diameter distribution of the axial exhaust flow velocity in the "central type chimney 100" and the "side-end type chimney 100" in the chimney body 10, with the vertical axis representing wind speed and the horizontal axis representing radius (distance from the central axis of the chimney body). The type of side-end type chimney 100 used in this measurement is the type of chimney 100 of the first embodiment. The measurement method was performed using experimental models made based on the type of chimney 100 of the first embodiment shown in Figures 1 to 4 and the comparative example types shown in Figures 13 and 14. Specifically, two branch pipes 30, a main pipe 20, an elbow pipe 40, and a chimney body 10 with the same inner diameter as the elbow pipe 40 were made as cylindrical bodies. Furthermore, at the other end of each cylindrical body corresponding to the sub-pipes 30, 30, a motor-driven first blower and a second blower were installed via a honeycomb for flow rectification purposes to supply air. An inverter was used to control the first and second blowers, and the input frequency was controlled using operating patterns with combinations of 17Hz-00Hz, 34Hz-00Hz, 00Hz-17Hz, 00Hz-34Hz, 17Hz-17Hz, 34Hz-17Hz, and 34Hz-34Hz. The flow velocity in each operating pattern was measured using an ultrasonic anemometer by placing a probe at the outlet of the cylindrical body corresponding to each chimney body 10. The graph in Figure 17 shows the measurement results for the 34Hz-34Hz operating pattern among the operating patterns with combinations of input frequencies to each blower.

[0040] According to the measurement results for the 34Hz-34Hz operating pattern shown in Figure 17, the diameter distribution of exhaust velocity in the chimney body 10 shows that the central chimney 100 has a slightly slower wind velocity in the center than the side-end chimney 100, and the wind velocity decreases as it moves away from the center. On the other hand, the side-end chimney 100 has a slightly faster wind velocity in the center than the central chimney 100, and the decrease in wind velocity is less even at points further away from the center than the central chimney 100, suggesting that its exhaust efficiency is superior to that of the central chimney 100. This trend was also observed in other operating patterns.

[0041] Then, using measurement data of the diameter distribution of the axial exhaust flow velocity in the chimney body 10 for each of the above combinations of input frequencies to the blower, the exhaust flow rate in the chimney body 10 obtained for each operation pattern was compared between the side-end type chimney 100 and the central type chimney 100, and the results are shown in Figure 18. Figure 18 is a graph comparing the flow rates of the "central type chimney 100" and the "side-end type chimney 100" in the chimney body 10. According to this, except for the 34Hz-00Hz operation pattern, for the other blower operation patterns, the exhaust flow rate in the chimney body 10 tends to be higher for the side-end type chimney 100 than for the central type chimney 100. In the 34Hz-00Hz operation pattern, the reason why the exhaust flow rate of the side-end type chimney 100 was lower than that of the central type chimney 100 is thought to be due to the flow path design for maintaining the swirling flow, which will be described later. Specifically, it is presumed that the cause was an inappropriate setting of the length from the connection point between the sub-pipe 30 and the main pipe 20 to the point where the main pipe 20 and the elbow pipe 40 connect, and therefore this measurement result is considered exceptional.

[0042] Based on the exhaust flow rate shown in Figure 18, which was obtained using measurement data of the diameter distribution of exhaust flow velocity in the axial direction of the cylindrical body of the chimney body 10, it can be said that the side-end type chimney 100 is superior to the central type chimney 100 in terms of exhaust efficiency.

[0043] Next, regarding the exhaust flow, we will explain the difference in the exhaust flow path from the main pipe 20 to the cylindrical chimney body 10 that forms the upward flue 11, which is considered to be another factor that affects exhaust efficiency.

[0044] Figure 19(A) is a schematic half-cut side view of a "central type chimney 100" which is a comparative example of chimney 100, and Figure 19(B) is a schematic half-cut side view of a "side-end type chimney 100" which is a chimney 100 according to the first embodiment. In each figure, the flow path of exhaust gas G that flows from the sub-pipe 30 to the main pipe 20 via the exhaust pipe E is schematically shown by flow path R1 and flow path R2.

[0045] In the "central chimney 100" shown in Figure 19(A), if the exhaust G is a normal linear flow, then in the flow path of the exhaust G from the main pipe 20 through the elbow pipe 40 to the chimney body 10, there is a difference in flow path between flow path R1 and flow path R2. On the other hand, in the "side-end chimney 100" shown in Figure 19(B), a swirling flow is generated in the exhaust G, so there is no large difference in flow path between flow path R1 and flow path R2. Therefore, the exhaust G flows into the chimney body 10, which forms an upward flue, while maintaining its swirling flow. The presence or absence of this difference in flow path of the exhaust G is thought to affect exhaust efficiency, and in this respect as well, the side-end chimney 100 can be said to be superior to the central chimney 100 in terms of exhaust efficiency.

[0046] Next, we will explain how the length from the connection point between the sub-pipe 30 and the main pipe 20 to the point where the main pipe 20 and the elbow pipe 40 connect creates a flow path in which the exhaust gas G flowing from the sub-pipe 30 into the main pipe 20 maintains a swirling flow even within the elbow pipe 40.

[0047] In the "side-end type chimney 100" shown in Figure 19(B), it is desirable to appropriately set the length D3 from the connection point between the sub-pipe 30 and the main pipe 20 to the point where the main pipe 20 and the elbow pipe 40 connect, in order to create ideal flow paths R1 and R2 for the exhaust G as it passes through the elbow pipe 40. When the length D3 is appropriate, the exhaust G flows smoothly in a swirling motion through the elbow pipe 40. However, if the length D3 is inappropriate, the inner corner of the elbow pipe 40 can become an obstacle, potentially forming a flow path where the exhaust G does not flow smoothly. Thus, whether the swirling flow of the exhaust G flows smoothly through the elbow pipe 40 is influenced by the length D3 from the connection point between the sub-pipe 30 and the main pipe 20 to the point where the main pipe 20 and the elbow pipe 40 connect. In particular, the effects become significant in the case of the chimney 100 according to the second embodiment, where there is only one sub-pipe 30, or in the first and third embodiments, when only one gas turbine engine or the like is driven, or when two gas turbine engines or the like are driven at different outputs, and there is a difference in the flow velocity of the two exhaust gases G, G flowing into the two sub-pipes 30, 30. Therefore, it is desirable that the length D3 from the connection point between the sub-pipe 30 and the main pipe 20 to the communication point between the main pipe 20 and the elbow pipe 40 be set to be a flow path that maintains a swirling flow within the elbow pipe 40.

[0048] The chimney 100 shown in the first to third embodiments described above has the excellent effect of stabilizing the exhaust flow and improving exhaust efficiency by forming a swirling flow, minimizing the flow path difference, and appropriately setting the length D3 from the connection point between the sub-pipe 30 and the main pipe 20 to the communication point between the main pipe 20 and the elbow pipe 40. It also eliminates the need for members that obstruct the exhaust flow, such as flow deflectors, and allows for the smooth integration of exhaust from multiple exhaust sources.

[0049] Furthermore, although the first to third embodiments described above have explained cases in which one or two sub-pipes 30 are connected to the main pipe 20, within the scope of the present invention, it is also possible to connect more than two sub-pipes 30 to the main pipe 20. [Explanation of symbols]

[0050] 10 Chimney body 11 Upward flue 20 Master 30 Secondary pipe 40 Elbow pipe 100 Chimneys D1 Inner diameter of the main pipe D2 Inner diameter of the auxiliary pipe D3 Length from the connection point between the branch pipe and the main pipe to the connection point between the main pipe and the elbow pipe. P1 Main pipe axis P2 Axis of the auxiliary pipe θ is the intersection angle (the angle at which the axis of the main pipe intersects with the axis of the secondary pipe). a. The degree of misalignment between the axis of the secondary pipe and the axis of the main pipe. E Exhaust pipe G Exhaust R1 channel R2 channel

Claims

1. It is a chimney with a pipeline through which exhaust flows from the secondary pipe to the main pipe. The inner diameter of the main pipe is larger than the inner diameter of the secondary pipe, and the secondary pipe intersects the main pipe at an angle less than a right angle, with at least one secondary pipe connected to the main pipe. The axis of the secondary pipe is positioned relative to the axis of the main pipe with a displacement in the radial direction of the main pipe, The axis of the main pipe and the axis of the secondary pipe do not share the same plane, and the main pipe and the secondary pipe intersect. The aforementioned sub-pipe is connected to an exhaust pipe that guides exhaust gas from the exhaust source. The exhaust gas flowing from the secondary pipe into the main pipe forms a swirling flow within the main pipe. The main pipe constitutes a horizontal pipe that guides exhaust to the chimney body which forms an upward flue, and is connected to a pipeline that communicates with the chimney body. A chimney characterized in that the swirling flow formed within the main pipe is guided through the main pipe to the chimney body.

2. A chimney according to claim 1, wherein multiple sub-pipes are connected to a main pipe, and the axes of the sub-pipes do not share the same plane.

3. An elbow pipe is provided at the connection point between the chimney body and the main pipe, the elbow pipe having a horizontal passage communicating with the main pipe, an arc-shaped passage communicating with the horizontal passage, and a rising passage communicating with the arc-shaped passage and releasing exhaust into an upward flue. The chimney according to claim 1 or claim 2, wherein the length from the connection point between the branch pipe and the main pipe to the connection point between the main pipe and the elbow pipe is set such that the exhaust flowing from the branch pipe into the main pipe maintains a swirling flow path even within the elbow pipe.

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