JP2017040440A - High-temperature exhaust cylinder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve strength and service life of a high-temperature exhaust cylinder by suppressing contact of high-temperature exhaust gas without using a heat insulating material.SOLUTION: A high-temperature exhaust cylinder unit 1 includes a cylinder body 2 in which three cylinder members on which a first cylindrical portion, a second cylindrical portion and a third cylindrical portion are formed, are axially arranged to circulate an exhaust gas G, and rectifiers 7A, 7B, 7C for circulating a gas circulated inside of the cylinder members as laminar flow. When the cylinder member at a basic end side of the cylinder body 2 is regarded as a basic end-side cylinder member, and the cylinder member at a tip side of the cylinder body 2 is regarded as a tip-side cylinder member, the third cylindrical portion of the basic end-side cylinder member is disposed inside of the first cylindrical portion of the tip-side cylinder member while forming a clearance in which the outside air flows, with the first cylindrical portion of the tip-side cylinder member, each of the second cylindrical portions has a cylinder inner face gradually reduced in diameter from the basic end side toward the tip side, so that the outside air flows therein through the clearance, and circulates as laminar flow along the cylinder inner face of each cylinder member inside of each of the cylinder members.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a high-temperature exhaust pipe for discharging high-temperature exhaust gas by combustion of a gas turbine or the like used in a power plant such as an engine generator.

In a facility that uses an engine generator, high-temperature exhaust gas generated when the engine generator is operated is released and diluted into the outside air using an exhaust pipe including a chimney or the like. In order to reduce the influence on the surroundings of the facility, the discharge of the exhaust gas is often performed at a height as much as possible. Therefore, a long and narrow exhaust pipe is used.
Further, the temperature and exhaust pressure of the exhaust gas vary depending on the type of the generator, and it is necessary to have an exhaust cylinder specification corresponding to each. At present, the generators that are becoming mainstream use a gas turbine engine as the engine. Therefore, the exhaust gas temperature and flow velocity are higher than those of the conventional diesel engines, and in one example, the exhaust gas temperature is 600 ° C. The exhaust gas wind speed reaches 40 m / s.

As a high-temperature exhaust pipe used for combustion exhaust gas such as a gas turbine, conventionally, an exhaust pipe unit in which, for example, an exhaust pipe loaded with a heat insulating material between metal double pipes is vertically stacked is known. The heat insulating material is made of, for example, a fibrous or foamed material made of an inorganic material. In this high-temperature exhaust pipe, a plurality of metal double pipes sandwiching a heat insulating material are connected in the vertical direction at a joint portion to form an exhaust pipe unit.
In other high-temperature exhaust gas chimneys, a chimney cylinder of the outer wall is formed of structural carbon steel, and a heat insulating material is formed on the inner surface thereof. However, the outer surface temperature of the chimney cylinder of carbon steel needs to be suppressed to 60 ° C. to 70 ° C. or less, so that the heat insulating material has to be lined thickly.
In the high-temperature exhaust gas chimney described in Patent Document 1 that has improved this, the heat insulating material on the inner surface of the chimney cylinder is separated into a first layer and a second layer, and an air flow passage is formed between them, and the chimney cylinder An introduction space is formed between the lower inner surface and the first layer of heat insulating material to communicate with the air flow passage. And since the outside air introduced from the space for introducing the chimney cylinder flows through the air flow passage and can cool the inner and outer walls of the chimney, the thickness of the heat insulating material by the first layer and the second layer is reduced to reduce the weight of the chimney. I can do it.

Japanese Patent No. 3511216

By the way, in the above-described conventional high-temperature exhaust pipe and high-temperature exhaust gas chimney, rainwater or the like is likely to enter through the joint portion or the upper end opening of the chimney, and thus there is a high possibility that the internal heat insulating material becomes wet. When the motor generator is continuously operating continuously, the water that has entered the heat insulating material evaporates immediately due to the exhaust heat, so that it does not stay inside the double pipe or the chimney or in the heat insulating material.
However, when the generator is operated intermittently, for example, when it is operated intermittently during emergency and inspection, such as an emergency generator, it has entered a high-temperature exhaust pipe or chimney of a double pipe Water is easily impregnated in the heat insulating material. If the engine generator is operated intermittently in this state, moisture will evaporate due to a rapid rise in temperature, especially when high-temperature exhaust gas passes through a double-tube high-temperature exhaust stack or chimney, as in a gas turbine engine. However, there is a possibility that the heat insulating material may be damaged due to a rapid pressure rise inside the heat insulating material.
On the other hand, when a simple metal exhaust stack or chimney is used without the heat insulating material, the portion supporting the structure of the exhaust stack or chimney is directly affected by the exhaust heat and the temperature is about 600 ° C., for example. If the steel metal is used, the strength is reduced to about half when the steel metal is used.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a high-temperature exhaust pipe having a high strength and a long life by suppressing contact with high-temperature exhaust gas without using a heat insulating material.

  In order to solve the above-described problems, a high-temperature exhaust pipe according to a first aspect of the present invention has a first cylindrical part and a second inner face that is smaller in diameter than the inner surface of the first cylindrical part. A cylindrical member and a third cylindrical part having a cylindrical inner surface whose diameter is reduced below the cylindrical inner surface of the second cylindrical part, and a plurality of cylindrical members formed in this order are arranged side by side in the axial direction, A cylinder main body that circulates high-temperature exhaust gas inside the cylinder member, and a rectifier that is installed in each of the cylinder members and circulates the gas that circulates inside the cylinder member as a laminar flow. Of the cylindrical members adjacent to each other in the above, the cylindrical member positioned on the proximal end side of the cylindrical main body is referred to as the proximal end side cylindrical member, and the cylindrical member positioned on the distal end side of the cylindrical main body is referred to as the distal end side cylindrical member. The third cylindrical portion of the proximal end side cylindrical member is located in front of the first cylindrical portion of the distal end side cylindrical member. Between the first cylindrical portion of the distal end side cylindrical member, a gap is formed to allow outside air to flow in, and at least one of the second cylindrical portions is gradually reduced in diameter from the proximal end side toward the distal end side. The outside air flows in through the gap, and the outside air circulates as a laminar flow along each cylinder inside surface of the cylinder member.

In this case, when the high temperature exhaust gas flows into the proximal end of the cylinder body, the high temperature exhaust gas is rectified through each rectifier, and flows inside the cylinder body toward the distal end side without becoming a turbulent flow or a diffusion flow. . At that time, the high-temperature exhaust gas flows in the vicinity of the opening of the gap at high speed in the axial direction, so that the gap becomes a negative pressure due to the venturi effect, and outside air flows from the gap. The inflowing outside air flows as a laminar flow toward the front end side by the action of the rectifier, so that the inflowing outside air flows along the cylinder inner surface of the cylinder member to the front end side. That is, the inflowing outside air flows along the cylinder inner surface of the cylinder member along the outer peripheral area of the cylinder member, and the high-temperature exhaust gas flows as a laminar flow in the center area. As a result, since the high temperature exhaust gas does not contact the cylinder inner surface of the cylinder member and the low temperature external airflow contacts, the temperature rise of the cylinder member is suppressed.
Further, when the outside air and the high-temperature exhaust gas pass through the second cylindrical portion having the cylindrical inner surface that gradually decreases in diameter from the proximal end side toward the distal end side, the flow passage cross-sectional area gradually decreases. Outside air and hot exhaust gases are accelerated. For this reason, even if the outside air in the cylinder main body and the high-temperature exhaust gas are decelerated due to the flow path resistance on the upstream side of the second cylindrical part, the second cylindrical part can accelerate the engine, so It is possible to suppress a decrease in the amount of outside air sucked.

In the high-temperature exhaust pipe, the first cylindrical portion and the third cylindrical portion may be tapered portions that reduce in diameter from the proximal end side toward the distal end side.
In this case, the outside air is accelerated when the outside air passes through the first tubular portion, and the outside air and the high temperature exhaust gas are accelerated when the outside air and the high temperature exhaust gas pass through the third tubular portion. For this reason, it can further suppress that the suction | attraction amount of external air falls.

In the high-temperature exhaust pipe, the rectifier may include a rectifying plate arranged in a lattice shape or a concentric shape in a cross section orthogonal to the axial direction of the cylindrical member and extending in the axial direction.
In this case, since the rectifier is formed in a lattice shape or a concentric shape in a cross section orthogonal to the axial direction of the cylindrical member, the hot exhaust gas and the outside air are respectively guided along the lattice of the rectifier or the concentric opening. For this reason, it becomes difficult to disturb a flow and a good laminar flow is formed.

  According to the high-temperature exhaust pipe of the present invention, since the high-temperature exhaust gas contacts the outside air without contacting the cylinder inner surface in the cylinder main body, the temperature rise is suppressed, and the contact of the high-temperature exhaust gas is suppressed without using a heat insulating material. In addition, there is an effect that a high-temperature exhaust pipe having a high strength and a long life can be provided.

It is a typical fragmentary perspective view which shows the structural example of the high temperature exhaust pipe unit of 1st embodiment of this invention. It is a typical fragmentary perspective view which shows an example of the cylinder member used for the high temperature exhaust cylinder unit of 1st embodiment of this invention. It is AA sectional drawing in FIG. It is BB sectional drawing in FIG. It is operation | movement explanatory drawing of the high temperature exhaust pipe unit of 1st embodiment of this invention. It is typical sectional drawing which shows the structure of the principal part of the modification (1st modification) of the high temperature exhaust pipe unit of 1st embodiment of this invention. It is typical sectional drawing which shows the structure of the principal part of the modification (2nd modification) of the high temperature exhaust pipe unit of 1st embodiment of this invention. It is typical sectional drawing which shows the structural example of the modification (3rd modification) of the high temperature exhaust pipe unit of 1st embodiment of this invention. It is a typical fragmentary perspective view which shows the structural example of the high temperature exhaust pipe unit of 2nd embodiment of this invention.

  Embodiments of the present invention will be described below with reference to the accompanying drawings. In all the drawings, even if the embodiments are different, the same or corresponding members are denoted by the same reference numerals, and common description is omitted.

[First embodiment]
The high-temperature exhaust pipe unit of the first embodiment of the present invention will be described.
FIG. 1 is a schematic partially broken perspective view showing a configuration example of a high-temperature exhaust stack unit according to the first embodiment of the present invention. FIG. 2 is a schematic partially broken perspective view showing an example of a cylinder member used in the high-temperature exhaust cylinder unit according to the first embodiment of the present invention. 3 is a cross-sectional view taken along the line AA in FIG. 4 is a cross-sectional view taken along the line BB in FIG.

As shown in FIG. 1, the high-temperature exhaust cylinder unit 1 (high-temperature exhaust cylinder) of the present embodiment includes a cylinder body 2 in which a plurality of cylinder members are arranged in the axial direction, and rectifiers 7A, 7B, and 7C. Prepare.
The high-temperature exhaust stack unit 1 may be disposed to be inclined with respect to the vertical axis, but will be described below with an example in which it is disposed along the vertical axis. The base end of the cylinder body 2 is an end portion in the vertically lower direction, and the tip end is an end portion in the upper vertical direction.
Hereinafter, with respect to each member in the high temperature exhaust stack unit 1, when describing the relative position in the axial direction, the position (part) near the base end of the high temperature exhaust stack unit 1 is referred to as the position (part) on the base end side, The position (part) near the tip may be referred to as the position (part) on the tip side.

The high-temperature exhaust pipe unit 1 is a chimney for releasing exhaust gas G (high-temperature exhaust gas) after burning fuel with a gas turbine (not shown) as an engine generator, for example.
The exhaust gas G has a high temperature of about 650 ° C. to 600 ° C., for example, and flows into the base end of the high-temperature exhaust cylinder unit 1 through the exhaust outlet 8 communicating with the base end portion of the cylinder main body 2. The exhaust gas G that has passed through the inside of the high temperature exhaust pipe unit 1 is released to the atmosphere from the tip of the high temperature exhaust pipe unit 1.
The exhaust outlet 8 is bent upward in a substantially L shape from a horizontal exhaust pipe, for example, and opens upward.

The number of tube members included in the tube body 2 is not particularly limited as long as it is plural, but the tube body 2 shown in FIG. 1 is, for example, the first tube member 2A, the second tube member 2B, and the third tube member. It has 3C members of 2C.
The first cylinder member 2A, the second cylinder member 2B, and the third cylinder member 2C are arranged in this order from the proximal end side to the distal end side of the cylinder body 2. The first cylinder member 2A, the second cylinder member 2B, and the third cylinder member 2C are arranged in series so that the central axes are coaxial.

  As shown in FIG. 2, the single first cylindrical member 2A is a cylindrical member having a substantially constant plate thickness (including a constant case), and the first cylindrical portion extends from the proximal end side toward the distal end side. 5A (tapered part), 2nd cylindrical part 3A, and 3rd cylindrical part 4A (tapered part) are formed.

In the first cylindrical portion 5A, a circular opening 5a is formed at the base end portion, and the inner diameter of the inner surface 5b (cylinder inner surface) and the outer diameter of the outer surface 5c are gradually reduced from the proximal end side toward the distal end side. It is a truncated cone-shaped cylindrical part.
The distal end of the first cylindrical portion 5A is connected to the opening 3a on the proximal end side of the second cylindrical portion 3A.
The second cylindrical portion 3A has a circular opening 3a formed at the base end, and a cone in which the inner diameter of the inner surface 3b (cylinder inner surface) and the outer diameter of the outer surface 3c are gradually reduced from the proximal end side toward the distal end side. It is a trapezoidal cylindrical part.
The distal end of the second cylindrical portion 3A is connected to the opening 4a on the proximal end side of the third cylindrical portion 4A.
The third cylindrical portion 4A has a circular opening 4a formed at the proximal end, and a cone in which the inner diameter of the inner surface 4b (cylinder inner surface) and the outer diameter of the outer surface 4c gradually decrease from the proximal end toward the distal end. It is a trapezoidal cylindrical part.
A circular opening 4d is formed at the tip of the third cylindrical portion 4A.

  In the first cylindrical member 2A, the inner diameters of the openings 5a, 3a, 4a, and 4d are d5a, d3a, d4a, and d4d, respectively, and the outer diameters are D5a, D3a, D4a, and D4d, respectively. In this embodiment, d5a> d3a> d4a> d4d and D5a> D3a> D4a> D4d.

  The lengths in the axial direction of the first cylindrical portion 5A, the second cylindrical portion 3A, and the third cylindrical portion 4A are not particularly limited. In the present embodiment, as an example, the axial length is increased in the order of the second cylindrical portion 3A, the third cylindrical portion 4A, and the first cylindrical portion 5A.

As shown in FIG. 1, the second cylinder member 2B (third cylinder member 2C) has substantially the same shape as the first cylinder member 2A, except for the size of the inner diameter and the outer diameter.
As shown in FIG. 2, the single second cylindrical member 2B (third cylindrical member 2C) is a cylindrical member having a substantially constant plate thickness (including a constant case), and extends from the proximal end side toward the distal end side. Thus, the first cylindrical portion 5B (5C), the second cylindrical portion 3B (3C), and the third cylindrical portion 4B (4C) are formed.

As shown in FIG. 1, the third cylindrical portion 4A of the first cylindrical member 2A (base end side cylindrical member) is the first cylindrical portion of the second cylindrical member 2B (front end side cylindrical member) adjacent to the distal end side. It is inserted inside 5B and arranged with a gap 9a. The relative positions of the first cylindrical member 2A and the second cylindrical member 2B are fixed by a support portion (not shown).
As shown in FIG. 3, the gap 9a is formed between the inner surface 5b of the first cylindrical portion 5B and the outer surface 4c of the third cylindrical portion 4A.
The gap between the inner surface 5b of the first cylindrical portion 5B and the outer surface 4c of the third cylindrical portion 4A in the gap 9a (hereinafter referred to as “the size of the gap 9a”) is constant in the circumferential direction, but is axial. May vary. For example, the size of the gap 9a is h1 at the position of the opening 5a on the proximal end side of the gap 9a, and h2 at the position of the opening 4d on the distal end side of the gap 9a.

The sizes of h1 and h2 may be such that the flow rate of the outside air K1 flowing into the first cylindrical member 2A through the gap 9a can be appropriately secured.
More preferably, the relative sizes of h1 and h2 are such that the flow path cross-sectional area of the gap 9a gradually decreases from the proximal end side opening 5a toward the distal end side opening 4d.
For example, if h2 <h1, the flow path cross-sectional area of the gap 9a gradually decreases reliably from the opening 5a toward the opening 4d as the distance from the opening 5a toward the opening 4d gradually decreases from h1 to h2.

For example, when h2 = h1, the size of the gap 9a is constant, but the entire gap 9a has a truncated cone shape whose diameter decreases from the proximal end side to the distal end side. That is, the flow path cross-sectional shape of the gap 9a is a ring with a constant width, and gradually decreases in diameter from the proximal end side toward the distal end side. For this reason, even if h2 = h1, the flow path cross-sectional area of the gap 9a gradually decreases gradually from the opening 5a toward the opening 4d.
On the other hand, even in the case of h2> h1, depending on the degree of diameter reduction (taper size) of the third cylindrical portion 4A and the first cylindrical portion 5B, the channel cross-sectional area gradually increases from the opening 5a toward the opening 4d. It is possible to decrease.

As shown in FIG. 1, the third cylindrical portion 4B of the second cylindrical member 2B (base end side cylindrical member) is a first cylindrical shape of the third cylindrical member 2C (tip side cylindrical member) adjacent to the base end side. It is inserted inside the part 5C and arranged with a gap 9b. The relative positions of the second cylindrical member 2B and the third cylindrical member 2C are fixed by a support portion (not shown).
The gap 9b is formed between the inner surface 5b of the first cylindrical portion 5C and the outer surface 4c of the third cylindrical portion 4B.
An interval between the inner surface 5b of the first cylindrical portion 5C and the outer surface 4c of the third cylindrical portion 4B in the gap 9b (hereinafter referred to as “the size of the gap 9b”) is constant in the circumferential direction, but is axial. May vary. In the present embodiment, the size of the gap 9b is set to h1 at the position of the opening 5a on the proximal end side and h2 at the position of the opening 4d on the distal end side, like the gap 9a. However, the dimensions of h1 and h2 in the gap 9b may be changed from h1 and h2 in the gap 9a.

The first cylinder member 2A, the second cylinder member 2B, and the third cylinder member 2C are made of metal such as steel, for example.
As a structure of the support part that supports the first cylinder member 2A, the second cylinder member 2B, and the third cylinder member 2C, for example, each cylinder member is individually fixed to an unillustrated fixing part outside the high-temperature exhaust cylinder unit 1. The structure connected to (for example, a housing, a wall surface, a support | pillar, etc.) may be sufficient. Or as a structure of a support part, between 3rd cylindrical part 4A (4B) and 1st cylindrical part 5B (5C) which mutually oppose through the clearance gap 9a (9b), columnar shape, plate shape, etc. The structure which arrange | positioned the connection member at intervals in the circumferential direction may be sufficient.

As shown in FIG. 1, for example, a distal end portion of a cylindrical exhaust outlet 8 is disposed with a gap 10 inside the first cylindrical portion 5A of the first cylindrical member 2A. The relative positions of the exhaust outlet 8 and the first cylindrical member 2A are fixed by a support portion (not shown).
The gap 10 is formed in the same shape as the gap 9a, for example.
The exhaust outlet 8 is not limited to a cylindrical shape, and may be formed in a tapered shape with a diameter decreasing from the proximal end side toward the distal end side.

The rectifiers 7A, 7B, and 7C are disposed inside the first cylinder member 2A, the second cylinder member 2B, and the third cylinder member 2C, respectively, and distribute the gas that flows through each cylinder member as a laminar flow.
The rectifiers 7A, 7B, and 7C are made of metal such as steel.
The rectifiers 7A, 7B, and 7C are configured in the same manner except that the outer shape differs according to the difference in the inner diameter of the cylindrical member at each arrangement position. Therefore, hereinafter, an example of the rectifier 7A will be mainly described.

As shown in FIG. 2, the rectifier 7 </ b> A includes a long plate-like plate portion 7 a (rectifier plate) extending in the axial direction and incorporated in a lattice shape when viewed from the axial direction. The position of the rectifier 7A in the axial direction may be any position as long as it is within the range of the second cylindrical portion 3A. However, in order to efficiently rectify the outside air K1 (see FIG. 1) flowing in along the first cylindrical portion 5A, the base end of the rectifier 7A may be disposed at the base end portion of the second cylindrical portion 3A.
Further, the axial length of the rectifier 7A can be appropriately set within a range equal to or shorter than the length of the second cylindrical portion 3A so that good rectification performance can be obtained.
In the example shown in FIG. 2, the rectifier 7A is formed shorter than the length of the second cylindrical portion 3A, and is disposed on the proximal end side of the second cylindrical portion 3A.
The rectifier 7A may be disposed away from the inner surface 3b of the second cylindrical portion 3A, but it is more preferable that the outer side surface of the rectifier 7A is in contact with the inner surface 3b in consideration of manufacturing costs.
The rectifier 7A may be fixed to the inner surface 3b of the second cylindrical portion 3A by, for example, welding. Alternatively, as in the example shown in FIG. 2, when the rectifier 7A is disposed on the proximal end side of the second cylindrical portion 3A, the rectifier 7A is the tip of the exhaust outlet 8 (see FIG. 1) not shown in FIG. It may be seated and fixed.

At the tip of the rectifier 7A, a large number of substantially rectangular openings 7b including a square and a shape lacking a part of the square are formed (see FIG. 4). At the base end of the rectifier 7A, openings 7c are formed corresponding to the openings 7b.
Between each opening part 7b, 7c, the cross section orthogonal to an axial direction is extended in the axial direction by the substantially square-shaped cross section.
The channel cross-sectional area of one channel may be constant in the axial direction or may vary. When the cross-sectional area of the flow path changes, in order to reduce pressure loss, the cross-sectional area of the opening 7c on the proximal end side is larger than the cross-sectional area of the opening 7b on the distal end side. A change that gradually reduces from the side to the tip side is preferable.

In the configuration of the present embodiment, for example, the plate thickness of the plate portion 7a may be constant. In this case, the cross-sectional area of the channel can be made constant in the channel having a square cross section.
A flow path having a shape lacking a part of a quadrangle at the outer peripheral portion of the rectifier 7A is formed between the plate portion 7a and the inner surface 3b of the second cylindrical portion 3A. In this case, since the inner surface 3b of the second cylindrical portion 3A is reduced in diameter from the proximal end side toward the distal end side, the flow path cross-sectional area gradually decreases from the proximal end side toward the distal end side.
In the configuration of the present embodiment, for example, the plate thickness of the plate portion 7a may gradually increase from the proximal end side toward the distal end side. In this way, the channel cross-sectional area can be configured to gradually decrease from the base end side toward the tip end side, regardless of whether the channel has a quadrangular cross section or a part of the quadrangular shape. .

The operation of the high temperature exhaust stack unit 1 of this embodiment will be described.
FIG. 5 is an operation explanatory diagram of the high-temperature exhaust stack unit according to the first embodiment of the present invention.

For example, when fuel is burned by a gas turbine (not shown) as an engine generator, high-temperature exhaust gas G flows from the exhaust outlet 8 into the first cylinder member 2A of the high-temperature exhaust cylinder unit 1 above as shown in FIG.
The exhaust gas G flows to the second cylindrical portion 3A through the first cylindrical portion 5A of the first cylindrical member 2A. At this time, since the first cylindrical portion 5A is a tapered portion that decreases in diameter from the proximal end side to the distal end side, the exhaust gas G increases in flow rate and travels toward the second cylindrical portion 3A.
The flow rate of the exhaust gas G is increased by the first cylindrical portion 5A, so that the outside air K1 having a temperature lower than that of the exhaust gas G from the gap 10 between the exhaust outlet 8 and the first cylindrical portion 5A is within the first cylindrical member 2A. Flow into. The outside air K1 flows upward along the inner surface 5b of the first cylindrical portion 5A.

Since the rectifier 7A is installed in the second cylindrical portion 3A, the outside air K1 and the exhaust gas G are rectified into a laminar flow by passing through the rectifier 7A.
At this time, since the outside air K1 travels along the inner surface 5b of the first tubular portion 5A, it travels along the inner surface 3b of the second tubular portion 3A adjacent to the tip side of the inner surface 5b. For this reason, as shown in FIG. 4, the outside air K1 flows into the outer peripheral portion 7d of the rectifier 7A.
The exhaust gas G flows above the exhaust outlet 8 and is concentrated in the center of the second cylindrical portion 3A in a state where the outer periphery is surrounded by the outside air K1 flowing in from the gap 10. For this reason, as shown in FIG. 4, the exhaust gas G flows into the central part 7e of the rectifier 7A.

Since the outer peripheral portion 7d and the central portion 7e of the rectifier 7A are formed with a plurality of flow paths, the outside air K1 and the exhaust gas G passing through different flow paths are rectified through separate flow paths without being mixed. Is done. When the outside air K1 and the exhaust gas G pass through the same flow path, there is a possibility that a part thereof is mixed in the flow path. However, by forming the plurality of openings 7b and 7c within the range through which the outside air K1 passes, it is possible to form a flow path in which only the outside air K1 passes and the exhaust gas G is not mixed with each other.
Out of the flow path of the rectifier 7A, the outside air K1 and the exhaust gas G passing through the flow path whose diameter decreases from the base end side toward the front end side are rectified and accelerated.

The outside air K1 and the exhaust gas G that have flowed into the outer peripheral portion 7d of the rectifier 7A and the opening portion 7c of the center portion 7e flow from the respective upper opening portions 7b to the distal end side of the second cylindrical portion 3A. For this reason, the exhaust gas G passing through the central portion 7e is surrounded by the outside air K1 passing through the outer peripheral portion 7d even above the rectifier 7A. Since both the outside air K1 and the exhaust gas G are rectified and become a laminar flow, they proceed to the leading end side with little mixing with each other.
In the present embodiment, since the inner surface 3b of the second cylindrical portion 3A has a tapered shape that decreases in diameter from the proximal end side toward the distal end side, both the outside air K1 and the exhaust gas G are accelerated. For this reason, if the taper of the inner surface 3b is formed to an appropriate size, the flow rates of the outside air K1 and the exhaust gas G are recovered even if the flow rates of the outside air K1 and the exhaust gas G are reduced by the resistance when passing through the rectifier 7A. be able to.

The outside air K1 and the exhaust gas G accelerated by the second cylindrical portion 3A further pass through the third cylindrical portion 4A that gradually decreases in diameter from the opening 4a having the same diameter as the distal end portion of the second cylindrical portion 3A. The flow rate is increased and flows into the first cylindrical portion 5B of the second cylindrical member 2B.
Thus, in the first cylindrical member 2A, a laminar flow of the hot exhaust gas G flows in the center, and the outer peripheral portion surrounding the exhaust gas G has a lower temperature along the inner surfaces 5b, 3b, 4b. There is a laminar flow of outside air K1 close to room temperature. For this reason, the exhaust gas G is not in contact with each inner surface of the first cylindrical member 2A, and the low temperature outside air K1 is in contact, so that the temperature rise is suppressed even if the exhaust gas G flows through the central portion.

When the outside air K1 whose speed has been increased by passing through the third tubular portion 4A passes through the front end side of the gap 9a, the gap 9a becomes negative pressure due to the venturi effect. For this reason, the outside air K2 flows into the second cylindrical member 2B through the gap 9a. The outside air K2 flows upward along the inner surface 5b of the first cylindrical portion 5B.
The rectified outside air K1 and exhaust gas G flow inside the outside air K2. The outside air K1 is heated by the exhaust gas G and has risen in temperature to some extent. However, since the outside air K2 flows in from the outside of the high-temperature exhaust cylinder unit 1, the outside air reaches the second cylinder member 2B equal to the outside temperature. The temperature is lower than K1.

Since the rectifier 7B is installed in the second cylindrical portion 3B, the outside air K2, the outside air K1, and the exhaust gas G pass through the rectifier 7B and are the same as when passing through the rectifier 7A. Rectified into laminar flow.
At this time, since the outside air K2 travels along the inner surface 5b of the first tubular portion 5B, it travels along the inner surface 3b of the second tubular portion 3B adjacent to the tip side of the inner surface 5b. For this reason, the outside air K2 flows into the outer peripheral portion of the rectifier 7B.
The outside air K1 and the exhaust gas G are concentrated in the center of the second cylindrical portion 3B in a state where the outer periphery is surrounded by the outside air K2 that travels above the opening 4d of the first cylindrical member 2A and flows in from the gap 9a. Flowing. For this reason, the outside air K1 and the exhaust gas G flow into the center of the rectifier 7B.
In the rectifier 7B, as with the rectifier 7A, the outside air K2 flows to the outer periphery of the rectifier 7B, and the outside air K1 and the exhaust gas G flow to the center of the rectifier 7B. Rectified.
Out of the flow paths of the rectifier 7B, the outside air K2, K1, and the exhaust gas G passing through the flow path whose diameter decreases from the base end side toward the front end side are rectified and accelerated.

  The outside air K2, the outside air K1, and the exhaust gas G that have flowed into the opening 7c of the rectifier 7B flow from the respective upper openings 7b to the distal end side of the second cylindrical portion 3B. For this reason, the outer air K1 and the exhaust gas G that pass through the center are surrounded by the outer air K2 that passes through the outer periphery even above the rectifier 7B. Since the outside air K2, the outside air K1, and the exhaust gas G are all rectified and are in a laminar flow, they proceed to the leading end side with little mixing with each other.

In the rectifier 7A, a two-layer laminar flow is formed by the exhaust gas G and the outside air K1 surrounding the exhaust gas G in a ring shape. On the other hand, in the rectifier 7B, an exhaust gas G, an outside air K1 surrounding the exhaust gas G in a ring shape, and a three-layer laminar flow surrounding the outside air K1 in a ring shape are formed.
However, it is important that a laminar flow of the outside air K2 surrounding the outside air K1 and the exhaust gas G in a ring shape is formed inside the second cylindrical member 2B. The outside air K1 and the exhaust gas G need only be in a laminar flow as a whole, and do not necessarily have a laminar flow divided into two layers.

  In the present embodiment, the inner surface 3b of the second cylindrical portion 3B has a tapered shape that decreases in diameter from the proximal end side toward the distal end side, so that the outside air K2, the outside air K1, and the exhaust gas G are all accelerated. . For this reason, if the taper of the inner surface 3b is formed to an appropriate size, the flow rate can be recovered even if the flow rates of the outside air K2, the outside air K1, and the exhaust gas G decrease due to the resistance when passing through the rectifier 7B. Can do.

The outside air K2 accelerated by the second tubular portion 3B, and the outside air K1 and the exhaust gas G pass through the third tubular portion 4B that gradually decreases in diameter from the opening 3a having the same diameter as the tip of the second tubular portion 3B. By passing, the flow rate is further increased, and flows into the first cylindrical portion 5B of the third cylindrical member 2C (not shown).
As described above, in the second cylindrical member 2B, a laminar flow of the outside air K1 including the high temperature exhaust gas G and the exhaust gas G flows in the center, and the outer surface surrounding the outside air K1 and the exhaust gas G has an inner surface 5b. A laminar flow of the outside air K2 that is cooler and close to room temperature flows along 3b and 4b. For this reason, the outside air K1 and the exhaust gas G are not in contact with the inner surfaces of the second cylindrical member 2B, and the low temperature outside air K2 is in contact with the inner surface of the second cylinder member 2B, so that an increase in temperature is suppressed even when the exhaust gas G flows through the center. Is done.

  The outside air K2, K1, and the exhaust gas G flowing into the third cylinder member 2C flows in the ring shape by the outside air K3 as the outside air K3 (see FIG. 1) flows from the gap 9b in the same manner as in the second cylinder member 2B. In the enclosed state, the current is rectified by the rectifier 7C. The exhaust gas G is exhausted to the outside from the opening 4a of the third cylindrical portion 4C without contacting the inner surface of the third cylindrical member 2C, as in the case of passing through the second cylindrical member 2B.

As described above, according to the high temperature exhaust pipe unit 1 of the present embodiment, when the exhaust gas G flows from the exhaust outlet 8, the exhaust gas G is sequentially rectified by the rectifiers 7A, 7B, 7C, and the gaps 10, 9a, 9b By flowing at high speed in the vicinity, the outside air K1, K2, and K3 flows from the gaps 10, 9a, and 9b, respectively. For this reason, a laminar flow composed of any of the outside air K1, K2, and K3, which is much lower in temperature than the exhaust gas G, is formed between the inner surface of the cylinder body 2 and the exhaust gas G, so that the exhaust gas G Does not contact the inner surface of the cylinder body 2. As a result, in the high temperature exhaust pipe unit 1, the temperature rise of the cylinder main body 2 can be suppressed without using a heat insulating material.
Furthermore, since the temperature rise of the cylinder main body 2 is suppressed, strength reduction due to the cylinder main body 2 being exposed to a high temperature is suppressed. For this reason, the high temperature exhaust pipe unit 1 has a long life.
If the flow velocity of the exhaust gas G or the like flowing through the cylinder main body 2 decreases, the inflow amount of outside air may decrease, and the temperature rise of the cylinder main body 2 may not be suppressed successfully. Since the two cylindrical portions 3A, 3B, and 3C are all reduced in diameter from the proximal end side to the distal end side, the exhaust gas G and the like are accelerated when passing through the second cylindrical portions 3A, 3B, and 3C. For this reason, the high temperature exhaust pipe unit 1 can stabilize the inflow amount of outside air.

In the high-temperature exhaust pipe unit 1, since the temperature rise of the cylinder main body 2 can be suppressed without using a heat insulating material, even when rainwater enters the high-temperature exhaust pipe unit 1 or condensation occurs, It will not cause damage to the heat insulating material due to rapid heating of water.
The high-temperature exhaust stack unit 1 does not need to use a heat insulating material, a double pipe, or the like in order to suppress a temperature rise, so that the manufacturing cost can be reduced.
Even if rainwater enters or condenses in the high-temperature exhaust pipe unit 1, moisture travels along the inner surface of the cylinder body 2 and is discharged from the first cylindrical portions 5A, 5B, and 5C to the external environment. The adverse effect of water due to condensation can be avoided.

[First Modification]
Next, a first modification of the first embodiment will be described.
FIG. 6 is a schematic cross-sectional view showing a configuration of a main part of a modified example (first modified example) of the high-temperature exhaust stack unit according to the first embodiment of the present invention.

As shown in FIG. 1, the high-temperature exhaust cylinder unit 11 (high-temperature exhaust cylinder) of the present modification includes a first cylinder member 2A, a second cylinder member 2B, and a third cylinder member of the high-temperature exhaust cylinder unit 1 of the first embodiment. Instead of the cylinder member 2C, three cylinder members, a first cylinder member 12A, a second cylinder member 12B, and a third cylinder member 12C are provided. The first cylinder member 12 </ b> A, the second cylinder member 12 </ b> B, and the third cylinder member 12 </ b> C constitute a cylinder body 12.
Hereinafter, a description will be given centering on differences from the first embodiment.

As shown in FIG. 6, the first cylinder member 12A (second cylinder member 12B, third cylinder member 12C) is replaced with a rectifier 17A (17B, 17C) instead of the rectifier 7A (7B, 7C) of the first embodiment. ).
In the rectifier 17A (17B, 17C), a long plate-like plate portion 17a (rectifier plate) having a constant plate thickness is incorporated in a lattice shape when viewed from the axial direction. At the tip of the rectifier 17A (17B, 17C), many substantially rectangular openings 17b similar to the rectifier 7A (7B, 7C) are formed (see FIG. 4). At the base end of the rectifier 17A (17B, 17C), an opening 17c is formed corresponding to each opening 17b.
Between each opening part 17b and 17c, the flow path in which the cross section orthogonal to an axial direction is substantially square shape is extended in the axial direction.
The cross-sectional shape of one flow path is a shape whose cross-sectional area is proportional to the cross-sectional area of the opening 3a at the same position in the axial direction and is similar to each other at different positions in the axial direction. For this reason, the channel cross-sectional area of each channel changes linearly from the cross-sectional area of the opening 17c on the base end side to the cross-sectional area of the opening 17b on the tip end side. Each channel has a frustum shape having the opening 17c as a bottom surface and the opening 17b as an upper surface. The central axis C of each flow path is generally skewed with respect to the central axis O of the second cylindrical portion 3A (3B, 3C).
Due to the shape of the rectifier 17A (17B, 17C), the plate portions 17a are arranged non-parallel to each other.

According to the high-temperature exhaust cylinder unit 11 of this modification, the outside air and the exhaust gas G flowing into the second cylindrical portion 3A (3B, 3C) are rectified into a laminar flow by the rectifier 17A (17B, 17C), and the second cylinder The flow velocity is accelerated by the inner surface 3b of the shaped portion 3A (3B, 3C).
Therefore, outside air K1, K2, and K3 flowing from the gaps 10, 9a, and 9b flow as laminar flows on the inner surfaces of the first cylinder member 12A, the second cylinder member 12B, and the third cylinder member 12C, respectively, and exhaust gas G does not contact the inner surface. Thereby, the high-temperature exhaust pipe unit 11 of this modification is a high-temperature exhaust pipe with high strength and long life by suppressing the contact of the high-temperature exhaust gas without using a heat insulating material, as in the first embodiment. .
Furthermore, in this modification, the flow path cross-sectional area of each flow path of the rectifier 17A (17B, 17C) changes in proportion to the cross-sectional area perpendicular to the axial direction of the second cylindrical portion 3A (3B, 3C). . For this reason, the flow velocity of the outside air or exhaust gas G passing through the rectifier 17A (17B, 17C) changes in the same manner in the second cylindrical portion 3A (3B, 3C) including the rectifier 17A (17B, 17C). As a result, the outside air and the exhaust gas G passing through the inside of the second cylindrical portion 3A (3B, 3C) are uniformly accelerated within the cross section of the flow path, and laminar flow occurs in the second cylindrical portion 3A (3B, 3C). The rectification performance is improved.

[Second Modification]
Next, a second modification of the first embodiment will be described.
FIG. 7 is a schematic cross-sectional view showing the configuration of the main part of a modified example (second modified example) of the high-temperature exhaust stack unit according to the first embodiment of the present invention.

As shown in a cross section orthogonal to the axial direction in FIG. 7, the high-temperature exhaust pipe unit 21 (high-temperature exhaust pipe) of the present modification is the first cylinder member 2A (second second) of the high-temperature exhaust pipe unit 1 of the first embodiment. Instead of the cylindrical member 2B and the third cylindrical member 2C), a first cylindrical member 22A (second cylindrical member 22B and third cylindrical member 22C) which is a cylindrical member is provided. The first cylinder member 22 </ b> A, the second cylinder member 22 </ b> B, and the third cylinder member 22 </ b> C constitute a cylinder body 22.
Hereinafter, a description will be given centering on differences from the first embodiment.

The first cylinder member 22A (second cylinder member 22B, third cylinder member 22C) includes rectifiers 27A, 27B, and 27C instead of the rectifiers 7A (7B and 7C) of the first embodiment.
The rectifier 27A (27B, 27C) includes a plurality of concentric cylindrical plate portions 27a (rectifier plates) extending in the axial direction and a plurality of connecting plates 27d (rectifier plates) that connect the plate portions 27a in the radial direction.
The number of the plate portions 27a is not particularly limited (four in the example of FIG. 7). The radial intervals of the plate portions 27a may be equal intervals or unequal intervals. Further, the number of plate portions 27a and the radial interval may be different between the rectifiers 27A, 27B, and 27C. The outermost plate portion 27a in the radial direction is located at a position where an opening 27b is formed between the inner surface 3b of the second cylindrical portion 3A (3B, 3C) at the tip of the rectifier 27A (27B, 27C). Be placed.
The number of connecting plates 27d is not particularly limited. In FIG. 7, as an example, the connecting plate 27d is extended in the radial direction at four locations that divide the circumferential direction into four equal parts. However, the connecting plate 27d that connects the plate portions 27a may not be continuous in the radial direction. For example, the connecting plate 27d may be arranged so that the circumferential separation length is constant in an annular region sandwiched between radially adjacent plate portions 27a.
The plate portion 27a and the connecting plate 27d are joined to each other at, for example, welding.
The connecting plate 27d at the outermost periphery is fixed to the inner surface 3b of the second cylindrical portion 3A (3B, 3C) by, for example, welding.

With such a configuration, the opening 27b in the rectifier 27A (27B, 27C) is formed in a substantially arc shape in which concentric annular regions are partitioned in the circumferential direction by the connecting plate 27d when viewed from the axial direction. .
In a region sandwiched between the plate portions 27a, a flow channel is formed in which the flow channel cross section of the opening 27b extends in the axial direction.
In a region sandwiched between the plate portion 27a and the inner surface 3b of the second cylindrical portion 3A (3B, 3C) on the outermost periphery, a flow path that widens as the radial width of each opening portion 27b moves toward the base end side. Is formed.

According to the high-temperature exhaust cylinder unit 21 of this modification, the outside air and the exhaust gas G flowing into the second cylindrical portion 3A (3B, 3C) are rectified into a laminar flow by the rectifier 27A (27B, 27C), and the second cylinder The flow velocity is accelerated by the inner surface 3b of the shaped portion 3A (3B, 3C).
For this reason, the outside air K1, K2, and K3 flowing in from the gaps 10, 9a, and 9b flow as laminar flows on the inner surfaces of the first cylinder member 22A, the second cylinder member 22B, and the third cylinder member 22C, respectively, and exhaust gas G does not contact the inner surface. Thereby, the high-temperature exhaust pipe unit 21 of this modification is a high-temperature exhaust pipe with high strength and long life by suppressing the contact of the high-temperature exhaust gas without using a heat insulating material, as in the first embodiment. .
Furthermore, the flow path cross-sectional area of each flow path of the rectifier 27A (27B, 27C) of the present modification is a substantially arc shape concentric with respect to the central axis of the inner surface 3b of the second cylindrical portion 3A (3B, 3C). . Therefore, the rectifier 27A (27B, 27C) can rectify the substantially axisymmetric flow of the outside air and the exhaust gas G flowing through the second cylindrical portion 3A (3B, 3C) into a substantially axisymmetric laminar flow. Performance will be better.

[Third Modification]
Next, a third modification of the first embodiment will be described.
FIG. 8 is a schematic cross-sectional view showing a configuration example of a modified example (third modified example) of the high-temperature exhaust stack unit according to the first embodiment of the present invention.

As shown in FIG. 8, the high-temperature exhaust cylinder unit 31 (high-temperature exhaust cylinder) of the present modification includes a first cylinder member 2A, a second cylinder member 2B, and a third cylinder member of the high-temperature exhaust cylinder unit 1 of the first embodiment. Instead of the cylinder member 2C, three cylinder members of a first cylinder member 32A, a second cylinder member 32B, and a third cylinder member 32C are provided. The first cylinder member 32 </ b> A, the second cylinder member 32 </ b> B, and the third cylinder member 32 </ b> C constitute a cylinder body 32.
Hereinafter, a description will be given centering on differences from the first embodiment.

The first cylindrical member 32A (second cylindrical member 32B, third cylindrical member 32C) is arranged on the third cylindrical portion 4A (4B, 4C) and the first cylindrical portion 5A (5B, 5C) of the first embodiment. Instead, a third cylindrical portion 34A (34B, 34C) and a first cylindrical portion 35A (35B, 35C) are provided.
The first cylinder member 32A, the second cylinder member 32B, and the third cylinder member 32C constitute a cylinder main body 32 of this modification.

The third cylindrical portion 34A (34B, 34C) is a cylinder having the same inner diameter as the opening 4a, whereas the third cylindrical portion 4A (4B, 4C) of the first embodiment is a tapered portion. It is different in that it is formed into a shape.
A circular opening 34d having the same diameter as the opening 4a is formed at the tip of the third cylindrical portion 34A (34B, 34C).
The inner diameter and outer diameter of the third cylindrical portion 34A (34B, 34C) are at least larger than the inner diameter and outer diameter of the second cylindrical portion 3A (3B, 3C). In this modification, as an example, the inner diameter and the outer diameter of the third cylindrical portion 34A (34B, 34C) are equal to the inner diameter and the outer diameter at the proximal end portion of the second cylindrical portion 3A (3B, 3C).

The first cylindrical portion 35A (35B, 35C) includes a flange portion 35e and a cylindrical portion 35d.
The flange portion 35e is an annular plate-like portion that is extended radially outward from the opening 3a of the second cylindrical portion 3A (3B, 3C) as viewed from the axial direction.
The cylindrical part 35d is extended from the outer peripheral part of the flange part 35e to the base end side. A circular opening 35a having a larger diameter than the opening 3a is formed at the base end of the cylindrical portion 35d.

The third cylindrical portion 34A of the first cylindrical member 32A is inserted into the first cylindrical portion 35B of the second cylindrical member 32B adjacent to the distal end side, and is disposed with a gap 39a. The relative positions of the first cylinder member 32A and the second cylinder member 32B are fixed by a support portion (not shown).
The gap 39a is formed between the inner surface 35b (cylinder inner surface) of the first cylindrical portion 35B and the outer surface 34c of the third cylindrical portion 34A.
The gap between the inner surface 35b of the first cylindrical portion 35B and the outer surface 34c of the third cylindrical portion 34A in the gap 39a is a constant value H1 in the circumferential direction. On the other hand, the distance between the third cylindrical portion 4A and the flange portion 35e in the first cylindrical portion 35B is H2 (where H2 <H1).
The sizes of H1 and H2 may be such that the flow rate of the outside air K2 flowing into the first cylindrical member 2A through the gap 9a can be appropriately ensured.

Similarly, the third cylindrical portion 34B of the second cylindrical member 32B is inserted into the first cylindrical portion 35C of the third cylindrical member 32C adjacent to the proximal end side, and is disposed with a gap 39b. . The relative positions of the second cylindrical member 32B and the third cylindrical member 32C are fixed by a support portion (not shown).
The gap 39b is formed between the inner surface 35b of the first cylindrical portion 35C and the outer surface 34c of the third cylindrical portion 34B.
The gap between the inner surface 5b of the first cylindrical portion 35C and the outer surface 4c of the third cylindrical portion 34B in the gap 39b is a constant value H1. The distance between the third cylindrical portion 4B and the flange portion 35e in the first cylindrical portion 35C is H2 (where H2 <H1).
However, the dimensions of H1 and H2 in the gap 39b may be changed from those of H1 and H2 in the gap 39a.

Similarly, the front end portion of the exhaust outlet 8 is disposed with a gap 40 inside the first cylindrical portion 35A of the first cylindrical member 32A. The relative positions of the exhaust outlet 8 and the first cylinder member 32A are fixed by a support portion (not shown).
The gap 40 is formed in the same shape as the gap 39a, for example.

According to such a configuration, since the flow paths of the outside air and the exhaust gas G are cylindrical in the third cylindrical portions 34A, 34B, and 34C, the outside air and the exhaust gas are exhausted in the third cylindrical portions 34A, 34B, and 34C. The point from which the gas G is not accelerated differs from the said 1st embodiment.
Furthermore, since the flow paths of the outside air K1, K2, and K3 are substantially cylindrical, the outside air K1, K2, and K3 are only generated by reducing the width H1 of the flow path on the proximal end side to the width H2 of the flow path on the distal end side. The point that is accelerated is different from the first embodiment.

According to the high-temperature exhaust cylinder unit 31 of this modification, the outside air and the exhaust gas G flowing into the second cylindrical portion 3A (3B, 3C) are rectified into a laminar flow by the rectifier 7A (7B, 7C), and the second cylinder The flow velocity is accelerated by the inner surface 3b of the shaped portion 3A (3B, 3C).
For this reason, the outside air K1, K2, K3 flowing from the gaps 40, 39a, 39b flows as laminar flows on the inner surfaces of the first cylinder member 32A, the second cylinder member 32B, and the third cylinder member 32C, respectively, and exhaust gas G does not contact the inner surface. Thereby, the high-temperature exhaust pipe unit 31 of this modification is a high-temperature exhaust pipe with high strength and long life by suppressing the contact of the high-temperature exhaust gas without using a heat insulating material, as in the first embodiment. .

[Second Embodiment]
Next, the high temperature exhaust pipe of the second embodiment will be described.
FIG. 9 is a schematic partially broken perspective view showing a configuration example of the high-temperature exhaust stack unit according to the second embodiment of the present invention.

As shown in FIG. 9, the high temperature exhaust cylinder unit 41 (high temperature exhaust cylinder) of the present embodiment includes a first cylinder member 2A, a second cylinder member 2B, and a third cylinder of the high temperature exhaust cylinder unit 1 of the first embodiment. Instead of the member 2C and the rectifiers 7A, 7B, and 7C, a first cylinder member 42A, a second cylinder member 42B, a third cylinder member 42C, and rectifiers 47A, 47B, and 47C are provided. The three cylindrical members of the first cylindrical member 42A, the second cylindrical member 42B, and the third cylindrical member 42C constitute a cylindrical main body 42.
Hereinafter, a description will be given centering on differences from the first embodiment.

The first cylinder member 42A, the second cylinder member 42B, and the third cylinder member 42C are only the point that the cross-sectional shape orthogonal to the axial direction is a substantially square shape. Different from the cylindrical member 2B and the third cylindrical member 2C. The cross-sectional shape of the “substantially square” in the first cylinder member 42A, the second cylinder member 42B, and the third cylinder member 42C is not limited to a convex quadrangle including a square and a rectangle, A shape in which the four sides are curved in an arc shape is included.
Hereinafter, as an example, as shown in FIG. 9, an example in which the cross-sectional shape orthogonal to the axial direction is a square will be described.

The first cylindrical member 42A (second cylindrical member 42B, third cylindrical member 42C) includes the first cylindrical part 5A (5B, 5C), the second cylindrical part 3A (3B, 3C) in the first embodiment, Instead of the third cylindrical part 4A (4B, 4C), the first cylindrical part 45A (45B, 45C), the second cylindrical part 43A (43B, 43C), the third whose section perpendicular to the axial direction is square A cylindrical portion 44A (44B, 44C) is provided.
The third cylindrical portion 44B is inside the first cylindrical portion 45C, the third cylindrical portion 44C is inside the first cylindrical portion 45B, and the first cylindrical portion 45A is orthogonal to the axial direction inside the first cylindrical portion 45B. Exhaust outlets 48 having a square cross section are arranged with gaps 49b, 49a, and 50, respectively.
The first cylindrical member 42A, the second cylindrical member 42B, the third cylindrical member 42C, and the exhaust outlet 48 are fixed to each other in the axial direction as in the first embodiment.
In the cylinder main body 42 of the present embodiment, the shape of the vertical cross section orthogonal to the opposite side of the square of the cross section orthogonal to each axial direction is the same as the shape of the vertical cross section including the central axis of the cylinder main body 2 of the first embodiment. It is.
For this reason, the first cylindrical portion 45A (45B, 45C), the second cylindrical portion 43A (43B, 43C), and the third cylindrical portion 44A (44B, 44C) are reduced in diameter from the proximal end side to the distal end side. It consists of a square frustum-shaped square tube.

The rectifier 47A (47B, 47C) has an outer shape corresponding to that of the second cylindrical portion 43A (43B, 43C), corresponding to the fact that the second cylindrical portion 43A (43B, 43C) is a quadrangular pyramid-shaped square tube. It is the same member as the rectifier 7A (7B, 7C) except that it has a quadrangular frustum shape that comes into contact with the inner surface 43b (cylinder inner surface).
The rectifier 47A (47B, 47C) is fixed to the inner surface 43b of the second cylindrical portion 43A (43B, 43C) in the same manner as the rectifier 7A (7B, 7C) of the first embodiment.

With such a configuration, the high-temperature exhaust pipe unit 41 of the present embodiment has the same configuration as the high-temperature exhaust pipe unit 1 of the first embodiment except that the cross-sectional shape orthogonal to the central axis is a square.
Therefore, according to the high temperature exhaust pipe unit 41, the outside air K1 (K2, K3) and the exhaust gas G flowing into the second cylindrical portion 43A (43B, 43C) are rectified into a laminar flow by the rectifier 47A (47B, 47C). The flow velocity is accelerated by the inner surface 43b of the second cylindrical portion 43A (43B, 43C).
For this reason, outside air K1, K2, and K3 flowing in from the gaps 50, 49a, and 49b flow as laminar flows on the inner surfaces of the first cylinder member 42A, the second cylinder member 42B, and the third cylinder member 42C, respectively, and exhaust gas G does not contact the inner surface. As a result, the high-temperature exhaust pipe unit 41 of the present embodiment is a high-temperature exhaust pipe having a high strength and a long life by suppressing the contact of the high-temperature exhaust gas without using a heat insulating material, as in the first embodiment. .

  In the first embodiment, an example in which the first cylindrical portion and the third cylindrical portion are tapered portions will be described. In the third modified example, the first cylindrical portion and the third cylindrical portion are described. As described above, an example in the case of a cylindrical portion. However, only one of the first cylindrical portion and the third cylindrical portion may be configured with a tapered portion.

In the description of each of the above-described embodiments and modifications, the cylinder main body includes three cylindrical members, and all the three cylindrical members have an example in which the second cylindrical portion has a diameter reduced from the proximal end side to the distal end side. explained. However, the 2nd cylindrical part diameter-reduced from the base end side to the front end side should just be formed in the at least 1 cylinder member arrange | positioned in the site | part which needs to accelerate the gas which passes through an inside.
For example, you may provide the 2nd cylindrical part diameter-reduced from the base end side to the front end side only at the base end side of a cylinder main body, and only at the front end side. For example, a second cylindrical portion that decreases in diameter from the proximal end side to the distal end side may be provided in a cylindrical member that is appropriately spaced in the axial direction.

  In the description of the second embodiment, the example in the case where the outer shape in the cross section orthogonal to the axial direction of the cylinder main body 42 and the rectifiers 47A, 47B, 47C has been substantially rectangular has been described. However, these outer shapes may be substantially polygonal shapes other than substantially rectangular shapes.

As mentioned above, although preferable embodiment of this invention was described, this invention is not limited to these embodiment and its modification. Additions, omissions, substitutions, and other modifications can be made without departing from the spirit of the present invention.
Further, the present invention is not limited by the above description, and is limited only by the appended claims.
For example, by applying the first modification to the rectifier of the second modification, the cross-sectional area of the flow path of the rectifier is reduced from the proximal end side to the distal end side in the same manner as the second tubular portion and the flow passage cross-sectional area. You may make it diameter.
For example, only the outer peripheral portion of the rectifier of the first embodiment may be replaced with a concentric flow path similar to that of the second modification.

1, 11, 21, 31, 41 High temperature exhaust pipe unit (high temperature exhaust pipe)
2, 12, 22, 32, 42 Cylinder body 2A, 12A, 22A, 32A, 42A 1st cylinder member (cylinder member, base end side cylinder member)
2B, 12B, 22B, 32B, 42B Second cylinder member (cylinder member, distal end side cylinder member, proximal end side cylinder member)
2C, 12C, 22C, 32C, 42C Third cylinder member (cylinder member, front end side cylinder member)
3a, 4a, 4d, 5a, 34d, 35a Opening 3b, 4b, 5b, 35b, 43b Inner surface (cylinder inner surface)
3A, 3B, 3C, 43A, 43B, 43C Second cylindrical part 3c, 4c, 5c, 34c Outer surface 4A, 4B, 4C, 34A, 34B, 34C, 44A, 44B, 44C Third cylindrical part 5A, 5B, 5C, 35A, 35B, 35C, 45A, 45B, 45C First cylindrical portions 7a, 17a, 27a Plate portion (rectifying plate)
7A, 7B, 7C, 17A, 17B, 17C, 27A, 27B, 27C, 47A, 47B, 47C Rectifiers 7b, 7c, 17b, 17c, 27b Openings 8, 48 Exhaust outlets 9a, 9b, 10, 39a, 39b, 40, 49a, 49b, 50 Gap 17b, 17c Opening 27d Connecting plate (rectifying plate)
35d Cylindrical part G Exhaust gas (high temperature exhaust gas)
K1, K2, K3 Outside air

Claims (3)

A first cylindrical portion, a second cylindrical portion having a cylindrical inner surface that is reduced in diameter relative to a cylindrical inner surface of the first cylindrical portion, and a cylindrical inner surface that is reduced in diameter below the cylindrical inner surface of the second cylindrical portion. A cylindrical body having a third cylindrical portion formed in this order, arranged in a plurality in the axial direction, and a cylindrical main body for circulating high-temperature exhaust gas inside the cylindrical member;
A rectifier that is installed in each of the cylindrical members and circulates a gas flowing through the cylindrical member as a laminar flow;
With
Of the cylindrical members adjacent to each other in the axial direction, a cylindrical member positioned on the proximal end side of the cylindrical main body is referred to as a proximal end side cylindrical member, and a cylindrical member positioned on the distal end side of the cylindrical main body is referred to as a distal end side cylindrical member. ,
The third cylindrical portion of the proximal end side cylindrical member has a gap through which outside air flows between the first cylindrical portion of the distal end side cylindrical member and the first cylindrical portion of the distal end side cylindrical member. Arranged,
At least one of the second cylindrical portions has a cylindrical inner surface that gradually decreases in diameter from the proximal end side toward the distal end side,
A high-temperature exhaust pipe in which the outside air flows in through the gap and the outside air flows as a laminar flow along the inner surface of each cylinder member inside each cylinder member.   2. The high-temperature exhaust pipe according to claim 1, wherein the first cylindrical portion and the third cylindrical portion are tapered portions that reduce in diameter from a proximal end side toward a distal end side.   3. The high-temperature exhaust pipe according to claim 1, wherein the rectifier includes a rectifying plate that is arranged in a lattice shape or a concentric shape in a cross section perpendicular to the axial direction of the cylindrical member and extends in the axial direction. .

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