JP2021113655A - Passage structure of heat exchanger and heat exchanger - Google Patents

Abstract

To provide a passage structure of a heat exchanger which achieves excellent heat recovery performance and heat shielding performance.SOLUTION: A passage structure of a heat exchanger 100 includes: an inner cylinder 10 in which a first fluid can circulate and which can house a heat recovery member 40; an outer cylinder 20 which is disposed forming a space at the radial outer side of the inner cylinder 10 so that a second fluid can circulate between itself and the inner cylinder 10; a middle cylinder 30 disposed between the inner cylinder 10 and the outer cylinder 20 and forming a first passage 31a for enabling the second fluid to circulate between itself and the outer cylinder 20 and a second passage 31b for enabling the second fluid to circulate between itself and the inner cylinder 10; and a flow rate control mechanism 50 which is disposed in at least one of the first passage 31a and the second passage 31b and controls a flow rate of the second fluid circulating in at least one of the first passage 31a and the second passage 31b. The middle cylinder 30 has a communication hole 32 which enables the second fluid to circulate between the first passage 31a and the second passage 31b.SELECTED DRAWING: Figure 1

Description

The present invention relates to a flow path structure of a heat exchanger and a heat exchanger.

In recent years, improvement in fuel efficiency of automobiles has been required. In particular, in order to prevent deterioration of fuel efficiency when the engine is cold, such as when the engine is started, cooling water, engine oil, automatic transmission fluid (ATF), etc. are warmed at an early stage to reduce friction loss. The system to do is expected. In addition, a system for heating the catalyst for activating the exhaust gas purification catalyst at an early stage is expected.

As a system as described above, for example, there is a heat exchanger. The heat exchanger is a device that exchanges heat between the first fluid and the second fluid by circulating the first fluid inside and the second fluid outside. In such a heat exchanger, heat can be effectively utilized by exchanging heat from a high-temperature fluid (for example, exhaust gas) to a low-temperature fluid (for example, cooling water).

In Patent Document 1, a heat collecting portion formed as a honeycomb structure having a plurality of cells through which a first fluid (for example, exhaust gas) can flow and a heat collecting portion are arranged so as to cover the outer peripheral surface of the heat collecting portion to collect heat. A heat exchanger having a casing through which a second fluid (for example, cooling water) can flow is proposed.
However, since the heat exchanger of Patent Document 1 has a structure that constantly recovers the exhaust heat from the first fluid to the second fluid, the exhaust heat is recovered even when it is not necessary to recover the exhaust heat. There was something. Therefore, when it is not necessary to recover the exhaust heat, it is necessary to increase the capacity of the radiator for releasing the recovered exhaust heat.

Therefore, in Patent Document 2, the casing arranged so as to cover the outer peripheral surface of the honeycomb structure is arranged so as to cover the inner cylinder arranged so as to fit the outer peripheral surface of the honeycomb structure and the inner cylinder. It is composed of an inner cylinder and an outer cylinder arranged so as to cover the inner cylinder, and an inner outer peripheral flow path is provided between the inner cylinder and the inner cylinder, and an outer outer peripheral flow path is provided between the inner cylinder and the outer cylinder. A formed heat exchanger has been proposed. According to this heat exchanger, when the temperature of the inner cylinder is lower than the boiling point of the refrigerant (second fluid) (when it is necessary to recover the exhaust heat), the inner outer peripheral flow path and the outer outer peripheral flow path are liquid. Since it is filled with the state refrigerant, heat exchange can be promoted. Further, when the temperature of the inner cylinder is higher than the boiling point of the refrigerant (when it is not necessary to recover the exhaust heat), the refrigerant in a gaseous state generated by boiling vaporization will be present in the inner outer peripheral flow path. , Heat exchange can be suppressed. Therefore, this heat exchanger can switch between promoting and suppressing heat exchange between two types of fluids.

Japanese Unexamined Patent Publication No. 2012-307165 International Publication No. 2016/185963

However, the heat exchanger described in Patent Document 2 does not have sufficient heat exchange promoting effect (hereinafter referred to as "heat recovery performance") and suppressing effect (hereinafter referred to as "heat blocking performance"), and these performances are exhibited. It is hoped that it will be improved.
The present invention has been made to solve the above problems, and an object of the present invention is to provide a flow path structure of a heat exchanger and a heat exchanger having excellent heat recovery performance and heat cutoff performance.

As a result of diligent research on the flow path structure of the heat exchanger, the present inventors have determined that the flow rate of the second fluid flowing through the two flow paths formed between the inner cylinder and the outer cylinder is the heat recovery performance. And it was found that it affects the heat insulation performance. Then, the present inventors have found that both the heat recovery performance and the heat blocking performance can be improved by providing a flow rate control mechanism for controlling the flow rate of the second fluid flowing through at least one of the two flow paths. , The present invention has been completed.

That is, the present invention includes an inner cylinder through which the first fluid can flow and can accommodate a heat recovery member.
An outer cylinder arranged at intervals on the radial outer side of the inner cylinder so that a second fluid can flow between the inner cylinder and the inner cylinder.
A first flow path that is arranged between the inner cylinder and the outer cylinder and allows the second fluid to flow between the outer cylinder and the second fluid that can flow between the inner cylinder. The inner cylinder that forms the two flow paths and
A flow rate control mechanism that is arranged in at least one of the first flow path and the second flow path and controls the flow rate of the second fluid that flows through at least one of the first flow path and the second flow path. With
The middle cylinder has a flow path structure of a heat exchanger having a communication hole through which a second fluid can flow between the first flow path and the second flow path.

Further, in the present invention, an inner cylinder capable of circulating the first fluid and accommodating a heat recovery member and an inner cylinder
An outer cylinder arranged at intervals on the radial outer side of the inner cylinder so that a second fluid can flow between the inner cylinder and the inner cylinder.
A first flow path that is arranged between the inner cylinder and the outer cylinder and allows the second fluid to flow between the outer cylinder and the second fluid that can flow between the inner cylinder. The inner cylinder that forms the two flow paths and
A flow rate control mechanism for controlling the flow rate of the second fluid flowing through at least one of the first flow path and the second flow path according to the temperature of the second fluid is provided.
The middle cylinder has a flow path structure of a heat exchanger having a communication hole through which a second fluid can flow between the first flow path and the second flow path.

Further, the present invention is a heat exchanger having the above-mentioned flow path structure of the heat exchanger.

According to the present invention, it is possible to provide a flow path structure of a heat exchanger and a heat exchanger having excellent heat recovery performance and heat cutoff performance.

It is sectional drawing parallel to the flow direction of the 1st fluid of the heat exchanger which concerns on Embodiment 1 of this invention. It is sectional drawing of the aa'line in the heat exchanger of FIG. It is sectional drawing of the bb'line in the heat exchanger of FIG. It is sectional drawing of the composite metal material (bimetal) composed of two kinds of metal plates. It is a partially enlarged view of the flow path structure of the 2nd fluid in FIG. It is a partially enlarged view of the flow path structure of the 2nd fluid in the heat exchanger which concerns on Embodiment 2 of this invention. It is a partially enlarged view of the flow path structure of the 2nd fluid in the heat exchanger which concerns on Embodiment 3 of this invention. FIG. 5 is a cross-sectional view perpendicular to the flow direction of the first fluid in the heat exchanger according to the third embodiment of the present invention.

In the flow path structure of the heat exchanger according to the embodiment of the present invention, the first fluid can flow, and the second fluid can flow between the inner cylinder capable of accommodating the heat recovery member and the inner cylinder. The second fluid is arranged between the inner cylinder and the outer cylinder, and the second fluid flows between the outer cylinder and the outer cylinder arranged at intervals on the radial outer side of the inner cylinder. An inner cylinder forming a second flow path through which the second fluid can flow between a possible first flow path and the inner cylinder, and at least one of the first flow path and the second flow path. The middle cylinder is provided with a flow rate control mechanism that is arranged and controls the flow rate of the second fluid that flows through at least one of the first flow path and the second flow path, and the middle cylinder is the first flow path and the second flow path. It has a communication hole through which a second fluid can flow between the flow path and the flow path.
Further, in the flow path structure of the heat exchanger according to the embodiment of the present invention, the first fluid can flow, and the second fluid flows between the inner cylinder capable of accommodating the heat recovery member and the inner cylinder. The second fluid is arranged between the inner cylinder and the outer cylinder, and is arranged between the outer cylinder and the outer cylinder so as to be possible. A middle cylinder that forms a second flow path through which the second fluid can flow between the first flow path through which the fluid can flow and the inner cylinder, and the first flow path according to the temperature of the second fluid. And a flow rate control mechanism for controlling the flow rate of the second fluid flowing through at least one of the second flow paths, the middle cylinder has a second flow rate between the first flow path and the second flow path. It has a communication hole through which fluid can flow.
Further, the heat exchanger according to the embodiment of the present invention is a heat exchanger having the flow path structure of the above heat exchanger.
Hereinafter, specific embodiments of the present invention will be described in detail with reference to the drawings. The present invention is not limited to the following embodiments, and changes, improvements, etc. have been appropriately added to the following embodiments based on the ordinary knowledge of those skilled in the art without departing from the spirit of the present invention. It should be understood that things also fall within the scope of the present invention.

(Embodiment 1)
FIG. 1 is a cross-sectional view parallel to the flow direction of the first fluid of the heat exchanger according to the first embodiment of the present invention. 2 is a cross-sectional view taken along the line aa'in the heat exchanger of FIG. 1, and FIG. 3 is a cross-sectional view taken along the line bb'in the heat exchanger of FIG.
As shown in FIGS. 1 to 3, the heat exchanger 100 according to the first embodiment of the present invention includes an inner cylinder 10 capable of flowing a first fluid and accommodating a heat recovery member 40, and an inner cylinder 10. The outer cylinder 20 is arranged between the inner cylinder 10 and the outer cylinder 20 at intervals in the radial direction of the inner cylinder 10 so that the second fluid can flow between the two. The middle cylinder 30 forming the first flow path 31a through which the second fluid can flow between the 20 and the second flow path 31b through which the second fluid can flow between the inner cylinder 10 and the first flow path 31a. It is provided inside with a flow rate control mechanism 50 that controls the flow rate of the second fluid flowing through the first flow path 31a. Further, the middle cylinder 30 has a communication hole 32 through which a second fluid can flow between the first flow path 31a and the second flow path 31b.

Here, various liquids and gases can be used as the first fluid and the second fluid. For example, when the heat exchanger 100 is mounted on an automobile, exhaust gas can be used as the first fluid, and water or antifreeze (LLC specified in JIS K2234: 2006) can be used as the second fluid. Further, the first fluid can be a fluid having a higher temperature than the second fluid.

In the heat exchanger 100 having the above structure, the flow rate control mechanism 50 has a function of controlling the flow rate of the second fluid flowing through the first flow path 31a. When heat exchange is performed (during heat recovery), the flow rate control mechanism 50 is controlled so as to reduce the flow rate of the second fluid flowing through the first flow path 31a (the pressure loss of the first flow path 31a increases). Therefore, the flow rate of the second fluid flowing through the second flow path 31b can be increased. As a result, heat exchange between the first fluid flowing through the inner cylinder 10 and the second fluid flowing through the second flow path 31b is promoted, and the heat recovery performance is improved. On the other hand, when suppressing heat exchange (when heat is cut off), the flow rate control mechanism 50 is set so as to increase the flow rate of the second fluid flowing through the first flow path 31a (reduce the pressure loss of the first flow path 31a). By controlling, the flow rate of the second fluid flowing through the second flow path 31b can be reduced. As a result, the second fluid in a gaseous state is easily held in the second flow path 31b, so that the heat blocking performance is improved.

The flow rate control mechanism 50 is not particularly limited as long as it has the above-mentioned functions, but as shown in FIG. 1, a flow rate that controls the flow path area of the first flow path 31a through which the second fluid flows. It can be a road area control mechanism. By using such a control mechanism, the flow rate of the second fluid flowing through the first flow path 31a can be easily controlled.

The flow rate control mechanism 50 (flow path area control mechanism) is provided inside the outer cylinder 20 in the radial direction and has a donut-shaped plate 52 having an opening 53, and the opening 53 can be opened and closed according to the temperature of the second fluid. The thermal deformation member 51 provided in the above manner can be provided. The heat-deformable member 51 is deformable according to the temperature of the second fluid, and a part of the heat-deformable member 51 is joined to the outer cylinder 20. A part of the donut-shaped plate 52 is joined to the outer cylinder 20. Although FIG. 1 shows an example in which the flow rate control mechanism 50 including the heat deformation member 51 and the plate 52 is provided inside the outer cylinder 20 in the radial direction, it may be provided outside the inner cylinder 30 in the radial direction. good.

The shape of the opening 53 is not particularly limited as long as it allows the second fluid to pass through, and may be various shapes such as a circular shape, an elliptical shape, and a polygonal shape.
The number of openings 53 is not particularly limited and may be appropriately adjusted according to the flow rate to be controlled.

The shape of the heat deforming member 51 is not particularly limited as long as the opening 53 can be opened and closed according to the temperature of the second fluid. The shape of the heat deforming member 51 is preferably plate-shaped.
One thermal deformation member 51 may be provided for one opening 53, or one may be provided for two or more openings 53.

The heat deforming member 51 is not particularly limited, but a bimetal, a shape memory alloy, or the like can be used. Among them, the heat deformation member 51 is preferably bimetal.
Here, the term "bimetal" as used herein means a composite metal material obtained by joining two or more types of metal plates having different coefficients of thermal expansion. As an example of bimetal, FIG. 4 shows a cross-sectional view of a composite metal material composed of two types of metal plates. In FIG. 4, the composite metal material is composed of a metal plate A having a small coefficient of thermal expansion and a metal plate B having a large coefficient of thermal expansion. A composite metal material having such a structure has a property of bending (deforming) to a side having a small coefficient of thermal expansion when the temperature rises.
The deformation temperature and the magnitude of deformation can be controlled by selecting the type of metal plate constituting the composite metal material.

The operation of the flow rate control mechanism 50 having the above structure will be described with reference to FIG. FIG. 5 is a partially enlarged view of the flow path structure of the second fluid in FIG.
When heat exchange is performed, since the temperature of the second fluid is low, the heat deformable member 51 is configured to be deformable so as to close the opening 53. Therefore, as shown in FIG. 5A, the thermal deformation member 51 is deformed so as to close the opening 53. As a result, the flow of the second fluid flowing through the second flow path 31b (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a decreases (pressure loss of the first flow path 31a). Increases), and the flow rate of the second fluid flowing through the second flow path 31b increases.
On the other hand, when heat exchange is suppressed, since the temperature of the second fluid is high, the heat deformable member 51 is configured to be deformable so as to open the opening 53. Therefore, as shown in FIG. 5B, the thermal deformation member 51 is deformed so as to open the opening 53. As a result, the flow of the second fluid flowing through the first flow path 31a (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a increases (pressure loss of the first flow path 31a). Is reduced), and the flow rate of the second fluid flowing through the second flow path 31b is reduced.

Hereinafter, each component of the heat exchanger 100 will be described in detail for each component.
<About inner cylinder 10>
The inner cylinder 10 is a tubular member arranged on the outer peripheral surface of the heat recovery member 40 in the axial direction (flow direction of the first fluid).
The inner peripheral surface of the inner cylinder 10 may be in direct contact with or indirectly in contact with the axial outer peripheral surface of the heat recovery member 40, but from the viewpoint of thermal conductivity, the axial direction of the heat recovery member 40 It is preferable that it is in direct contact with the outer peripheral surface. In this case, the cross-sectional shape of the inner peripheral surface of the inner cylinder 10 matches the cross-sectional shape of the outer peripheral surface of the heat recovery member 40. Further, it is preferable that the axial direction of the inner cylinder 10 coincides with the axial direction of the heat recovery member 40, and the central axis of the inner cylinder 10 coincides with the central axis of the heat recovery member 40.
The axial length of the inner cylinder 10 is preferably set longer than the axial length of the heat recovery member 40. Further, it is preferable that the central position of the inner cylinder 10 coincides with the central position of the heat recovery member 40 in the axial direction of the inner cylinder 10.

The diameter (outer diameter and inner diameter) of the inner cylinder 10 is not particularly limited, but it is preferable that both ends in the axial direction are enlarged. With such a configuration, the middle cylinder 30 can be directly provided on the outer peripheral surface of the inner cylinder 10 having an expanded diameter in the axial direction, so that the second flow path 31b can be easily provided between the inner cylinder 10 and the middle cylinder 30. Can be formed into.
The diameter (outer diameter and inner diameter) of the inner cylinder 10 may be uniform over the entire axial direction, or both ends in the axial direction may be reduced in diameter. In this case, the second flow path 31b can be easily formed between the inner cylinder 10 and the inner cylinder 30 by providing spacers at both ends of the inner cylinder 30 in the axial direction and holding the inner cylinder 30.

Since the heat of the first fluid passing through the heat recovery member 40 is transferred to the inner cylinder 10 via the heat recovery member 40, the inner cylinder 10 is preferably formed of a material having excellent thermal conductivity. As the material used for the inner cylinder 10, for example, metal, ceramics, or the like can be used. Examples of the metal include stainless steel, titanium alloy, copper alloy, aluminum alloy, brass and the like. The material of the inner cylinder 10 is preferably stainless steel because of its high durability and reliability.

<About the outer cylinder 20>
The outer cylinder 20 is a tubular member arranged at intervals on the outer side in the radial direction of the inner cylinder 10.
It is preferable that the axial direction of the outer cylinder 20 coincides with the axial direction of the heat recovery member 40 and the inner cylinder 10, and the central axis of the outer cylinder 20 coincides with the central axis of the heat recovery member 40 and the inner cylinder 10.
The axial length of the outer cylinder 20 is preferably set longer than the axial length of the heat recovery member 40. Further, it is preferable that the central position of the outer cylinder 20 coincides with the central position of the heat recovery member 40 and the inner cylinder 10 in the axial direction of the outer cylinder 20.

The outer cylinder 20 discharges the supply pipe 21 for supplying the second fluid to the region between the outer cylinder 20 and the inner cylinder 10 and the second fluid from the region between the outer cylinder 20 and the inner cylinder 10. It is connected to the discharge pipe 22 for the purpose. The supply pipe 21 and the discharge pipe 22 are preferably provided at positions corresponding to both ends in the axial direction of the heat recovery member 40.
Further, the supply pipe 21 and the discharge pipe 22 may be extended in the same direction as shown in FIG. 1 or may be extended in different directions.

The diameter (outer diameter and inner diameter) of the outer cylinder 20 may be uniform over the axial direction, but at least a part (for example, the central portion in the axial direction, both ends in the axial direction, etc.) is reduced or expanded in diameter. May be good. For example, by reducing the diameter of both ends of the outer cylinder 20 in the axial direction, the inner cylinder 10 can be directly joined and the second flow path 31b can be easily formed between the outer cylinder 20 and the inner cylinder 30. .. Further, by reducing the diameter of the central portion of the outer cylinder 20 in the axial direction, the second fluid can be distributed in the entire outer cylinder 10 in the outer peripheral direction. Therefore, the amount of the second fluid that does not contribute to heat exchange is reduced in the central portion in the axial direction, so that the heat recovery performance can be improved.

As the material used for the outer cylinder 20, for example, metal, ceramics, or the like can be used. Examples of the metal include stainless steel, titanium alloy, copper alloy, aluminum alloy, brass and the like. The material of the outer cylinder 20 is preferably stainless steel because of its high durability and reliability.

<About the middle cylinder 30>
The middle cylinder 30 is a tubular member. It is preferable that the axial direction of the middle cylinder 30 coincides with the axial direction of the heat recovery member 40, and the central axis of the middle cylinder 30 coincides with the central axis of the heat recovery member 40.
The axial length of the middle cylinder 30 is preferably set longer than the axial length of the heat recovery member 40. Further, in the axial direction of the middle cylinder 30, the central position of the middle cylinder 30 preferably coincides with the central position of the heat recovery member 40, the inner cylinder 10 and the outer cylinder 20.

The middle cylinder 30 is arranged between the inner cylinder 10 and the outer cylinder 20, and has a first flow path 31a through which a second fluid can flow between the outer cylinder 20 and the middle cylinder 30, and the inner cylinder 10 and the middle cylinder 30. A second flow path 31b through which the second fluid can flow is formed with 30.
The middle cylinder 30 has a communication hole 32 through which a second fluid can flow between the first flow path 31a and the second flow path 31b. With such a configuration, the second fluid can be circulated in the second flow path 31b.
The shape of the communication hole 32 is not particularly limited as long as it allows the second fluid to pass through, and may be various shapes such as a circular shape, an elliptical shape, and a polygonal shape. Further, a slit may be provided as a communication hole 32 along the axial direction or the circumferential direction of the inner cylinder 30.
The number of the communication holes 32 may be appropriately set according to the shape of the communication holes 32 and is not particularly limited, but is preferably one or more, and more preferably a plurality (two or more).
The position of the communication holes 32 may be appropriately set according to the shape and number of the communication holes 32, and is not particularly limited. For example, when the communication holes 32 have a circular shape or the like, a plurality of communication holes 32 may be provided on both ends in the axial direction of the middle cylinder 30.

When the second flow path 31b is filled with the second fluid of liquid, the heat of the first fluid transferred from the heat recovery member 40 to the inner cylinder 10 is transferred to the inner cylinder 10 via the second fluid of the second flow path 31b. It is transmitted to the second fluid of one flow path 31a. On the other hand, when the temperature of the inner cylinder 10 is high and a second fluid in a gaseous state (steam (air bubbles) of the second fluid) is generated in the second flow path 31b, the second fluid of the second flow path 31b is passed through. Heat conduction of one flow path 31a to the second fluid is suppressed. This is because the thermal conductivity of a gaseous fluid is lower than that of a liquid fluid. That is, it is possible to switch between a state in which heat exchange is promoted and a state in which heat exchange is suppressed, depending on whether or not a second fluid in a gaseous state is generated in the second flow path 31b. This heat exchange state does not require external control. Therefore, by providing the middle cylinder 30, it is possible to easily switch between promoting and suppressing heat exchange between the first fluid and the second fluid without external control.
As the second fluid, a fluid having a boiling point in a temperature range in which heat exchange is desired to be suppressed may be used. For example, examples of the second fluid used in heat exchangers for automobiles include water containing LLC (long life coolant).

<About heat recovery member 40>
The heat recovery member 40 is not particularly limited as long as it can recover heat. For example, a honeycomb structure can be used as the heat recovery member 40.
The honeycomb structure is generally a columnar structure. The cross-sectional shape perpendicular to the axial direction of the honeycomb structure is not particularly limited, and may be a circle, an ellipse, a square, or another polygon.

The honeycomb structure has a plurality of cells partitioned from each other by a partition wall containing ceramics as a main component and an outer peripheral wall. Each cell penetrates the inside of the honeycomb structure from the first end face to the second end face of the honeycomb structure. The first end face and the second end face are end faces on both sides in the axial direction (direction in which the cell extends) of the honeycomb structure.
The cross-sectional shape of each cell (the shape of the cross section perpendicular to the direction in which the cell extends) is not particularly limited, and may be any shape such as a circle, an ellipse, a fan, a triangle, a quadrangle, and a polygon of pentagon or more. can.
Further, each cell may be formed radially in a cross section perpendicular to the axial direction of the honeycomb structure. With such a configuration, the heat of the first fluid flowing through the cell can be efficiently transferred toward the outer side in the radial direction of the honeycomb structure.

The outer peripheral wall of the honeycomb structure is preferably thicker than the partition wall. With such a configuration, the strength of the outer peripheral wall that is easily broken (for example, cracks, cracks, etc.) due to an external impact, thermal stress due to a temperature difference between the first fluid and the second fluid, etc. is increased. Can be done.

The thickness of the partition wall is not particularly limited and may be appropriately adjusted according to the intended use. For example, the thickness of the partition wall is preferably 0.1 to 1 mm, more preferably 0.2 to 0.6 mm. By setting the thickness of the partition wall to 0.1 mm or more, the mechanical strength of the honeycomb structure can be made sufficient. Further, by setting the thickness of the partition wall to 1 mm or less, it is possible to suppress the problems that the pressure loss increases due to the decrease in the opening area and the heat recovery efficiency decreases due to the decrease in the contact area with the first fluid. can.

Next, a method of manufacturing the heat exchanger 100 will be described.
As a method for manufacturing the heat exchanger 100, it can be manufactured according to a method known in the art. For example, when a honeycomb structure is used as the heat recovery member 40, the heat exchanger 100 can be manufactured as follows.
First, the clay containing the ceramic powder is extruded into a desired shape to prepare a honeycomb molded body. The material of the honeycomb structure is not particularly limited, and known materials can be used. For example, in the case of producing a honeycomb structure containing a Si-impregnated SiC composite material as a main component, a binder and water or an organic solvent are added to a predetermined amount of SiC powder, and the obtained mixture is kneaded to form a clay. Therefore, a honeycomb molded body having a desired shape can be obtained. Then, the obtained honeycomb molded body is dried, and the honeycomb molded body is impregnated with metal Si and fired in an inert gas under reduced pressure or in a vacuum. A partitioned honeycomb structure can be obtained.

Next, the honeycomb structure is inserted into the inner cylinder 10, and the inner cylinder 10 is arranged so as to fit into the honeycomb structure by shrink fitting. In addition to shrink fitting, press fitting, brazing, diffusion joining, or the like may be used to fit the honeycomb structure to the inner cylinder 10.
Next, the middle cylinder 30 is arranged on the inner cylinder 10. The inner cylinder 10 and the middle cylinder 30 may be fixed by welding or the like.
Next, the structure produced above is placed inside the outer cylinder 20 provided with the second fluid supply pipe 21, the discharge pipe 22, and the flow rate control mechanism 50, and fixed by welding or the like.

According to the heat exchanger 100 according to the first embodiment of the present invention, the flow rate of the second fluid flowing through the first flow path 31a can be controlled by the flow rate control mechanism 50 including the heat deformation member 51 and the plate 52. Therefore, both the heat recovery performance and the heat cutoff performance can be improved.

(Embodiment 2)
FIG. 6 is a partially enlarged view (cross-sectional view parallel to the flow direction of the first fluid) of the flow path structure of the second fluid in the heat exchanger according to the second embodiment of the present invention. The components having the same reference numerals as those appearing in the description of the heat exchanger 100 according to the first embodiment of the present invention are the same as the components of the heat exchanger 200 according to the second embodiment of the present invention. Since there is, the description thereof will be omitted. Further, the structure other than the flow path structure in the heat exchanger 200 according to the second embodiment of the present invention is the same as the heat exchanger 100 according to the first embodiment of the present invention.

In the heat exchanger 200 according to the second embodiment of the present invention, the flow rate control mechanism 50 (flow path area control mechanism) is one or more plates 54 provided inside the outer cylinder 20 in the radial direction. It is different from the heat exchanger 100 according to the second embodiment of the present invention. The plate 54 is formed of a heat deforming member 51 whose flow path area of the first flow path 31a can be controlled according to the temperature of the second fluid.
In FIG. 6, a part of the plate 54 is joined to the inclined portion of the outer cylinder 20 whose diameter is reduced in the central portion in the axial direction, but it may be joined to a portion other than the inclined portion. Further, although the plate 54 is joined to the inner side in the radial direction of the outer cylinder 20, it may be joined to the outer side in the radial direction of the inner cylinder 30.

The shape of the plate 54 is not particularly limited and can be appropriately set according to the position where the plate 54 is provided. For example, the plate 54 can be donut-shaped. The donut-shaped plate 54 may be formed from one heat-deformable member 51, or may be formed by combining a plurality of heat-deformable members 51.

In the heat exchanger 200 having the above structure, when heat exchange is performed, the temperature of the second fluid is low, so that the plate 54 can be deformed so as to reduce the flow path area of the first flow path 31a. It is configured. Therefore, as shown in FIG. 6A, the plate 54 is deformed so as to reduce the flow path area of the first flow path 31a. As a result, the flow of the second fluid flowing through the second flow path 31b (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a decreases (pressure loss of the first flow path 31a). Increases), and the flow rate of the second fluid flowing through the second flow path 31b increases. As a result, heat exchange between the first fluid flowing through the inner cylinder 10 and the second fluid flowing through the second flow path 31b is promoted, and the heat recovery performance is improved.
On the other hand, when heat exchange is suppressed, since the temperature of the second fluid is high, the plate 54 is configured to be deformable so as to increase the flow path area of the first flow path 31a. Therefore, as shown in FIG. 6B, the plate 54 is deformed so as to increase the flow path area of the first flow path 31a. As a result, the flow of the second fluid flowing through the first flow path 31a (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a increases (pressure loss of the first flow path 31a). Is reduced), and the flow rate of the second fluid flowing through the second flow path 31b is reduced. As a result, the second fluid in a gaseous state is easily held in the second flow path 31b, so that the heat blocking performance is improved.

The heat exchanger 200 having the above-mentioned flow path structure can be manufactured according to a method known in the art, similarly to the heat exchanger 100 according to the first embodiment of the present invention.

According to the heat exchanger 200 according to the second embodiment of the present invention, the flow rate of the second fluid flowing through the first flow path 31a can be controlled by the plate 54 (heat deformation member 51), so that the heat recovery performance and the heat recovery performance can be controlled. Both heat insulation performance can be improved.
In the heat exchanger 200 of the second embodiment of the present invention, the plate 54 (heat deformation member 51) is used as the flow rate control mechanism 50 (flow path area control mechanism), but the flow rate control of the first embodiment of the present invention. By combining with the mechanism 50, both the heat recovery performance and the heat blocking performance can be further improved.

(Embodiment 3)
FIG. 7 is a partially enlarged view (cross-sectional view parallel to the flow direction of the first fluid) of the flow path structure of the second fluid in the heat exchanger according to the third embodiment of the present invention. The components having the same reference numerals as those appearing in the description of the heat exchanger 100 according to the first embodiment of the present invention are the same as the components of the heat exchanger 300 according to the third embodiment of the present invention. Since there is, the description thereof will be omitted. Further, the structure other than the flow path structure in the heat exchanger 300 according to the third embodiment of the present invention is the same as the heat exchanger 100 according to the first embodiment of the present invention.

The heat exchanger 300 according to the third embodiment of the present invention is a heat exchange according to the first and second embodiments of the present invention in that the flow control mechanism 50 is an opening area control mechanism for controlling the opening area of the communication hole 32. It is different from the vessels 100 and 200.
The opening area control mechanism is not particularly limited, but may be one or more plates 60 provided on the radial outer side (inside the first flow path 31a) of the inner cylinder 30 as shown in FIG. .. The plate 60 may be provided inside the inner cylinder 30 in the radial direction (inside the second flow path 31b) or inside the outer cylinder 20 in the radial direction (inside the first flow path 31a). Further, the plate 60 may be provided at a plurality of of these positions.
The plate 60 can be formed from the heat deforming member 51. The thermal deformation member 51 can open and close the communication hole 32 according to the temperature of the second fluid, and a part of the thermal deformation member 51 is joined to the inner cylinder 30.

The shape of the heat deforming member 51 is not particularly limited as long as the communication hole 32 can be opened and closed according to the temperature of the second fluid. The shape of the heat deforming member 51 is preferably plate-shaped.
One thermal deformation member 51 may be provided for one communication hole 32, or one may be provided for two or more communication holes 32. For example, when one heat deforming member 51 is provided for two communication holes 32, one heat deformation member 51 may be provided for two communication holes 32 in the axial direction as shown in FIG. 7. , One thermal deformation member 51 may be provided for two communication holes 32 in the circumferential direction as shown in FIG. Note that FIG. 8 is a cross-sectional view of the heat exchanger 300 corresponding to the bb'line in the heat exchanger 100 of FIG.

In the heat exchanger 300 having the above structure, the plate 60 is configured to be deformable so as to open the communication hole 32 because the temperature of the second fluid is low when heat exchange is performed. Therefore, as shown in FIG. 7A, the plate 60 is deformed so as to open the communication hole 32. As a result, the flow of the second fluid flowing through the second flow path 31b (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a decreases (pressure loss of the first flow path 31a). Increases), and the flow rate of the second fluid flowing through the second flow path 31b increases. As a result, heat exchange between the first fluid flowing through the inner cylinder 10 and the second fluid flowing through the second flow path 31b is promoted, and the heat recovery performance is improved.
On the other hand, when heat exchange is suppressed, since the temperature of the second fluid is high, the plate 60 is configured to be deformable so as to close the communication hole 32. Therefore, as shown in FIG. 7B, the plate 60 is deformed so as to close the communication hole 32. As a result, the flow of the second fluid flowing through the first flow path 31a (dotted flow) becomes stronger, and the flow rate of the second fluid flowing through the first flow path 31a increases (pressure loss of the first flow path 31a). Is reduced), and the flow rate of the second fluid flowing through the second flow path 31b is reduced. As a result, the second fluid in a gaseous state is easily held in the second flow path 31b, so that the heat blocking performance is improved.

The heat exchanger 300 having the above-mentioned flow path structure can be manufactured according to a known method except that a part of the plate 60 is fixed to the middle cylinder 30 by welding or the like.

According to the heat exchanger 300 according to the third embodiment of the present invention, the flow rate of the second fluid flowing through the second flow path 31b can be controlled by the opening area control mechanism, so that the heat recovery performance and the heat blocking performance can be improved. Both can be improved.
In the heat exchanger 300 of the third embodiment of the present invention, the plate 60 (heat deformation member 51) is used as the flow rate control mechanism 50 (opening area control mechanism), but the first and / or embodiment of the present invention By combining with the flow rate control mechanism 50 of the second embodiment, both the heat recovery performance and the heat blocking performance can be further improved.

10 Inner cylinder 20 Outer cylinder 21 Supply pipe 22 Discharge pipe 30 Middle cylinder 31a 1st flow path 31b 2nd flow path 32 Communication hole 40 Heat recovery member 50 Flow control mechanism 51 Thermal deformation member 52 Plate 53 Opening 54 Plate 60 Plate 100 , 200, 300 Heat exchanger A Metal plate with small coefficient of thermal expansion B Metal plate with large coefficient of thermal expansion

Claims (12)

An inner cylinder that allows the first fluid to flow and can accommodate heat recovery members,
An outer cylinder arranged at intervals on the radial outer side of the inner cylinder so that a second fluid can flow between the inner cylinder and the inner cylinder.
A first flow path that is arranged between the inner cylinder and the outer cylinder and allows the second fluid to flow between the outer cylinder and the second fluid that can flow between the inner cylinder. The inner cylinder that forms the two flow paths and
A flow rate control mechanism that is arranged in at least one of the first flow path and the second flow path and controls the flow rate of the second fluid that flows through at least one of the first flow path and the second flow path. With
The middle cylinder has a flow path structure of a heat exchanger having a communication hole through which a second fluid can flow between the first flow path and the second flow path. The flow rate control mechanism is a flow path area control mechanism that controls the flow path area of the first flow path through which the second fluid flows, an opening area control mechanism that controls the opening area of the communication hole, or a combination thereof. The flow path structure of the heat exchanger according to claim 1. The flow path structure of the heat exchanger according to claim 1 or 2, wherein the flow rate control mechanism includes a heat deformable member that can be deformed according to the temperature of the second fluid. The flow path structure of the heat exchanger according to claim 3, wherein a part of the heat deforming member is joined to the outer cylinder or the inner cylinder. The flow path area control mechanism includes a donut-shaped plate provided inside the outer cylinder in the radial direction and having an opening, and heat provided so that the opening can be opened and closed according to the temperature of the second fluid. The flow path structure of the heat exchanger according to any one of claims 2 to 4, further comprising a deformable member. The flow path area control mechanism is one or more plates provided inside the outer cylinder in the radial direction, and the plate adjusts the flow path area of the first flow path according to the temperature of the second fluid. The flow path structure of the heat exchanger according to any one of claims 2 to 4, which is formed of a controllable thermal deformation member. The opening area control mechanism is one or more plates provided at one or more positions selected from the radial outside of the middle cylinder, the radial inside of the middle cylinder, and the radial inside of the outer cylinder. The flow path structure of the heat exchanger according to any one of claims 2 to 6, wherein the plate is formed of a heat deforming member capable of opening and closing the communication hole according to the temperature of the second fluid. .. The flow path structure of the heat exchanger according to any one of claims 3 to 7, wherein the heat deforming member is a bimetal. Any of claims 1 to 8, wherein the flow rate control mechanism is configured to increase the pressure loss of the first flow path during heat recovery and reduce the pressure loss of the first flow path during heat cutoff. The flow path structure of the heat exchanger according to item 1. A heat exchanger having a flow path structure of the heat exchanger according to any one of claims 1 to 9. The heat exchanger further comprises the heat recovery member.
The heat exchanger according to claim 10, wherein the heat recovery member is a honeycomb structure having a partition wall forming a plurality of cells extending from the first end surface to the second end surface. An inner cylinder that allows the first fluid to flow and can accommodate heat recovery members,
An outer cylinder arranged at intervals on the radial outer side of the inner cylinder so that a second fluid can flow between the inner cylinder and the inner cylinder.
A first flow path that is arranged between the inner cylinder and the outer cylinder and allows the second fluid to flow between the outer cylinder and the second fluid that can flow between the inner cylinder. The inner cylinder that forms the two flow paths and
A flow rate control mechanism for controlling the flow rate of the second fluid flowing through at least one of the first flow path and the second flow path according to the temperature of the second fluid is provided.
The middle cylinder has a flow path structure of a heat exchanger having a communication hole through which a second fluid can flow between the first flow path and the second flow path.

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