WO2021029022A1

WO2021029022A1 - Heat exchanger

Info

Publication number: WO2021029022A1
Application number: PCT/JP2019/031913
Authority: WO
Inventors: 正己野村; 野村　隆; 政明野村
Original assignee: 正己野村; 野村　隆; 政明野村
Priority date: 2019-08-14
Filing date: 2019-08-14
Publication date: 2021-02-18
Also published as: JP7221502B2; JPWO2021029022A1

Abstract

In this heat exchanger (1), a wall of a partition chamber (14) in a heating tank (30) is formed from two adjacent metal members (10, 10) and an inner surface (30a) of the heating tank (30). Inlets and outlets of discharge holes (10e) of each metal member (10) are formed concentrically about the center of the metal member (10) such that concyclic inlets and outlets are at equal intervals. A straight line connecting the inlet and outlet of each discharge hole (10e) and a shaft (13) are skew, yet all the straight lines connecting the inlets and outlets of the discharge holes (10e) are at equal angles to the shaft (13). Accordingly, an adequately high heating efficiency can be achieved.

Description

Heat exchanger

The present invention relates to a heat exchanger that heats a fluid by passing it through a heating tank.

Conventionally, a heat exchanger that heats the above-mentioned fluid by heating the heating tank from the outside and passing the fluid through the heating tank has been known.

Specifically, as the electromagnetic induction heating type heat exchanger (heating device), for example, the device disclosed in Patent Document 1 can be mentioned.

In the configuration disclosed in Patent Document 1, the tank is filled with a heating element made of a magnetic material, and a high-frequency voltage is applied from the outside of the tank to heat the heating element. Then, the fluid is heated by passing the fluid through the tank.

However, the method disclosed in Patent Document 1 has a problem that the heating efficiency is poor. Specifically, for example, when one 10 mm iron plate is heated, heat is uniformly transferred, but when two 5 mm iron plates are stacked and one iron plate is heated, the other iron plate is heated by radiant heat. become. That is, heat is only indirectly transferred to the other iron plate. Therefore, for example, when the inside of the tank is filled with a heating element, since the tank and the heating element are separately provided, only the heating element is heated, and the tank is provided with an outer wall that holds a solution or steam. Since there is only one, the thermal efficiency is poor.

Further, Patent Document 1 has a problem that it is difficult to control the temperature of the fluid because the fluid is heated by the heating element filled in the tank.

In order to solve such a problem, the inventors of the present application have proposed the technique disclosed in Patent Document 2.

Specifically, in the configuration disclosed in Patent Document 2, the tank and the magnetic material member are integrated, and the tank is heated by an electromagnetic induction heating method. With the configuration of Patent Document 2, the heating efficiency can be significantly increased as compared with Patent Document 1.

Japanese Patent Publication "Japanese Patent Laid-Open No. 2000-65312 (published on March 3, 2000)" International Patent Gazette "WO2007 / 007763 (published January 18, 2007)

However, there is still room for improvement in improving the heating efficiency by the technique disclosed in Patent Document 2.

The present invention has been made in view of the above problems, and an object of the present invention is to realize a heat exchanger capable of further improving heating efficiency.

In order to solve the above problems, the heat exchanger according to the present invention is provided with a heating tank having a compartment inside for retaining the inflowing fluid, and by heating from the outside of the heating tank, the compartment chamber is described. It is a heat exchanger that heats the fluid in which the fluid stays, and has a plurality of substantially disk-shaped metal members having a plurality of discharge holes that are fluid passages, and each of the metal members is in the heating tank. The plate surfaces are arranged so as to face each other, and the axis connecting the center points of the plate surfaces is arranged along the inflow direction of the fluid, and the wall of the partition chamber is formed by at least two adjacent metal members. The straight line connecting the inlet and the outlet of the discharge hole is oblique to the facing surface of the metal member on the outlet side for each of the plurality of discharge holes of the metal member. It is said.

According to the heat exchanger according to the present invention, there is an effect that the heating efficiency can be further improved.

It is a schematic structural sectional view of the heat exchanger which concerns on one Embodiment of this invention. It is a schematic block diagram of the heat exchanger according to another embodiment of this invention. An example of a metal member constituting the heat exchanger shown in FIG. 2 is shown, where FIG. 2A is a front view and FIG. 2B is an end view taken along the line AA. The metal member shown in FIG. 3 is shown, (a) is a front view, and (b) is an end view taken along the line BB. Another example of the metal member constituting the heat exchanger shown in FIG. 2 is shown, (a) is a front view, and (b) is a CC line arrow viewing end view. The metal member shown in FIG. 5 is shown, FIG. 5A is a front view, and FIG. 5B is an end view taken along the line of the arrow. A state in which the fluid discharged from the metal member collides with the opposing metal member is shown, FIG. 3A shows an example of the metal member shown in FIG. 3, and FIG. 5B shows an example of the metal member shown in FIG. is there. It is a graph which shows the result of the performance test of the heat exchanger shown in FIG. It is a graph which shows the result of the performance test of the heat exchanger of the comparative example.

Hereinafter, an embodiment of the present invention will be described.

First, before explaining the heat exchanger according to the present embodiment, the basic heat exchange principle of the heat exchanger of the present invention will be described below with reference to FIG. In the present embodiment, the fluid may be a gas or a liquid.

(Outline configuration of heat exchanger)
FIG. 1 is a schematic configuration sectional view of a heat exchanger 101 for explaining the basic heat exchange principle of the heat exchanger of the present invention.

As shown in FIG. 1, the heat exchanger 101 includes a heating tank 130 including a plurality of metal members 110 inside, and a supply port serving as an inlet for a fluid (arrow in the figure) for supplying the fluid to the heating tank 130. It includes 111 and a discharge port 112 which is an outlet for the fluid discharged from the heating tank 130.

The metal member 110 is made of a substantially disk-shaped metal plate, and is arranged in the heating tank 130 at predetermined intervals in the traveling direction of the fluid so that the plate surfaces face each other. The positioning of the metal member 110 is performed by passing the positioning shaft 113 through the through hole 110c formed in the center of the metal member 110.

Further, as shown in FIG. 1, the metal member 110 is formed with a plurality of discharge holes 110e penetrating in the thickness direction. The discharge hole 110e is located at a position (periphery) closer to the peripheral end surface 110d than the central portion on the surface corresponding to the partition wall of the partition chamber 114 (details will be described later) formed when the peripheral end surfaces 110d of the metal member 110 are welded to each other. It is preferably formed at a position (a portion from the end face 110d to a position from a distance d5), and particularly preferably at a position close to the peripheral end face 110d where the temperature becomes high. Further, it is preferable that the discharge holes 110e formed in each of the adjacent metal members 110 are formed so as not to overlap in the traveling direction of the fluid passing through the heating tank 130. In other words, since the discharge hole 110e is formed at a position closer to the peripheral end surface 110d than the central portion of the metal member 110, the fluid discharged from the discharge hole 110e is the fluid in the metal member 110 adjacent to the downstream side. It hits the second surface 110b, which is the surface on the inflow side, and stays in the vicinity of the peripheral end surface 110d of the metal member 110 while forming a high-speed rotating vortex, and is extremely high due to the increase in the effective heat transfer area and the forced convection heat transfer by the vortex. Efficient fluid heating can be performed. The position of the discharge hole 110e is not limited to the above position.

The number of discharge holes 110e in each metal member 110, the size (caliber) of each discharge hole 110e, the shape, and the like are not particularly limited, and are appropriately adjusted according to the amount of fluid supplied to the heat exchanger 101. You can set it.

The heating tank 130 is made of a substantially cylindrical metal cylinder whose inner diameter is substantially the same as the outer diameter of the metal member 110. As a result, the peripheral end surface 110d of the metal member 110 arranged in the heating tank 130 comes into close contact with the inner surface 130a of the heating tank 130. In order to eliminate the gap between the peripheral end surface 110d of the metal member 110 and the inner surface 130a of the heating tank 130, the contact portion is metal welded. If the degree of adhesion between the peripheral end surface 110d of the metal member 110 and the inner surface 130a of the heating tank 130 is high, metal welding does not have to be performed.

Further, when the heating tank 130 and the metal member 110 are made of the same metal, the heating tank 130 and the metal member 110 may be integrally formed. In this case, it is formed by pouring the melted metal into a desired mold. If the heating tank 130 and the metal member 110 are integrally formed in this way, the inner surface 130a of the heating tank 130 and the metal member are as in the case where the heating tank 130 and the metal member 110 are provided as separate members. It is not necessary to consider the degree of adhesion of the contact portion of the peripheral end surface 110d of 110.

In the heating tank 130, among the adjacent metal members 110, the first surface 110a, which is the surface on the upstream side metal member 110 on the fluid outflow side, and the surface on the downstream side metal member 110 on the fluid inflow side. The space surrounded by the second surface 110b and the inner surface 130a of the heating tank 130 is referred to as a partition chamber 114. That is, a plurality of compartments 114 are formed in the heating tank 130.

In the partition chamber 114, of the two metal members 110, the fluid discharged from the discharge hole 110e formed in the metal member 110 on the upstream side of the fluid hits the second surface 110b of the metal member 110 on the downstream side and is disturbed. It becomes a flow and stays. In the partition chamber 114, the fluid discharged from the discharge hole 110e hits the second surface 110b of the metal member 110 at high speed, so that the fluid changes from turbulent flow to high-speed rotating vortex flow. Then, the fluid staying in the compartment 114 is sent to the adjacent compartment 114 arranged in the traveling direction of the fluid. In this way, the fluid is sequentially sent to the compartment 114 on the downstream side and discharged from the discharge port 112 of the heating tank 130.

The heat exchanger 101 heats the heating tank 130 by heating the heating tank 130 from the outside. As a result, the fluid that sequentially passes through the adjacent downstream partition chamber 114 while staying in the compartment 114 formed in the heating tank 130 will continue to be heated.

(Heating principle)
The heat exchanger 101 is heated from the outside by a heating means. Any heating means may be used to heat the heat exchanger 101 from the outside of the heat exchanger 101. For example, the heat exchanger 101 may be directly heated by using a burner, a nichrome wire, or the like. When the metal member 110 constituting the exchanger 101 is a material compatible with IH (induction heating) such as a magnetic material, it may be heated by electromagnetic induction.

Here, a case where the heat exchanger 101 is heated by using an electromagnetic induction heating method, that is, a case where the heat exchanger 101 is heated by using a high frequency AC power supply will be described. Here, the high frequency of the high-frequency AC power supply means a frequency higher than the frequency of the household power supply of 50 to 60 Hz, and is, for example, 250 Hz to 60,000 Hz while considering the influence on the radio wave interference in the vicinity. It can be applied in a wide range.

In order to adopt the electromagnetic induction heating method, it is necessary to use a material that generates an eddy current when a high frequency AC voltage is applied from the outside as a material constituting the metal member 110. Examples of such a material include a magnetic material. Specific examples of the metal member 110 that is the magnetic material include a strong magnetic metal such as iron and stainless steel (SUS) 430. This is because the Curie temperature needs to be as high as possible. Therefore, it is necessary to efficiently heat the entire metal member 110 until it exceeds the Curie temperature. Therefore, the metal member 110 shown in FIG. 1 has the following shape.

That is, as shown in FIG. 1, the metal member 110 has a plate shape, and its thickness in the cross-sectional direction is formed so that the through hole 110c side is thinner than the peripheral end surface 110d side. Specifically, the metal member 110 is formed so that the thickness is the same from the peripheral end surface 110d toward the through hole 110c up to the distance d5, and after the distance d5 is passed, the thickness gradually decreases toward the through hole 110c. There is. In other words, the metal member 110 has a thinner wall thickness on the through hole 110c side than a wall thickness on the peripheral end surface 110d side on the heat supply side from the outside, and the wall thickness in the vicinity of the through hole 110c is the thinnest. ing.

As described above, the metal member 110 is composed of a first portion having a constant thickness from the peripheral end surface 110d to the distance d5 and a second portion having a gradually thinning thickness from the distance d5 to the through hole 110c.

Therefore, in the metal member 110, the second portion whose thickness gradually decreases is easier to dissipate heat than the first portion having a constant thickness, and therefore is supplied from the thick peripheral end surface 110d side of the metal member 110. The heat is easily dissipated in the thin second portion. As a result, even if the metal member 110 is heated from the first portion near the heat source, the heat is dissipated at the second portion far from the heat source, so that the heat from the heat source is easily transferred to the entire metal member 110. As a result, the entire metal member 110 can be heated to a very high temperature. Therefore, it is possible to substantially uniformly heat the metal member 110 from the peripheral end surface 110d to the through hole 110c to a temperature close to the Curie temperature.

For example, assuming that the Curie temperature of stainless steel is about 700 ° C., the fluid in the compartment 114 surrounded by the metal member 110 heated to near the Curie temperature (about 700 ° C.) stays in the compartment 114. Therefore, the metal member 110 heats the metal member 110 to a very high temperature (near 700 ° C.). The fluid heated to a very high temperature in this way sequentially moves to the adjacent compartment 114 and is discharged from the discharge port 112 while continuing to be heated. Here, if the fluid flowing into the supply port 111 of the heat exchanger 101 is water vapor, the metal member continues to be heated to near the Curie temperature of the metal member 110 in each compartment 114 in the heat exchanger 101. It is discharged from the discharge port 112 as superheated steam heated near the Curie temperature of 110.

As described above, the metal member 110 has the same thickness from the peripheral end surface 110d toward the through hole 110c up to the distance d5, and is formed so as to gradually become thinner toward the through hole 110c after the distance d5 is passed. There is. Therefore, in the partition chamber 114 formed by the adjacent metal members 110, the central portion of the heating tank 130 is wider than the peripheral portion. As described above, since the internal pressure of the central portion is lower than that of the peripheral portion in the compartment 114 because it is wider than the peripheral portion of the central portion of the compartment 114, fluids are collected and collected in the central portion of the compartment 114. The fluid forms a vortex in the center. Forced convection heat transfer and turbulent heat transfer by this vortex flow promote heat exchange in the compartment 114, and the heating efficiency can be improved. Further, as the fluid flows in the compartment 114 for a long time, the fluid circulates in the compartment 114 and repeatedly contacts the high temperature wall surface, and as a result, the effect of increasing the effective heat transfer area is obtained, and the heating efficiency is improved. It can be further enhanced.

Further, due to the expansion of the fluid due to heating, the fluid is further accelerated from the upstream compartment 114 to the downstream compartment 114. As a result, the heat transfer characteristics improve as the fluid velocity increases. Therefore, the heat transfer characteristics are synergistically improved as the fluid moves to the downstream partition chamber 114, and the heating efficiency of the heat exchanger 101 as a whole is dramatically improved. To do. Further, the fluid is accelerated toward the downstream compartment 114 from the upstream compartment 114, so that the flow rate of the fluid passing through the heat exchanger 101 can be increased.

(Effect: Superheated steam temperature)
The heat exchanger 101 having the above configuration can realize a heat exchange rate significantly superior to that of the conventional heat exchanger. For example, the performance of the heat exchanger 101 can be confirmed under the following conditions.

Supply saturated steam pressure: 0.15 MPa
Supply saturated steam flow rate: 100 kg / h
Here, the heat exchanger 101 shown in FIG. 1 has an outer diameter d1 = 110 mm of the heating tank 130, a thickness d2 = 10 mm of the inner surface 130a of the heating tank 130, an inner diameter d3 = 90 mm of the heating tank 130, and a peripheral end surface of the metal member 110. The thickness d4 = 10 mm of the metal member 110, the uniform distance d5 = 15 mm between the peripheral end surface 110d of the metal member 110 and the through hole 110c, the thickness d6 = 3 mm of the through hole 110c of the metal member 110, and the shaft 13. The outer diameter is d7 = 12 mm. The number of metal members 10 is 16. The number of the metal members 110 is preferably 16 to 18, and is appropriately selected depending on the thickness of the metal members 110, the structure such as the inner diameter of the discharge hole 110e, the heating conditions of the heating tank 130, and the like.

Here, the temperature of the superheated steam obtained by the heat exchanger 101 is the temperature of the fluid discharged from the discharge port 112 of the heat exchanger 101.

When the heat generating main body temperature (temperature of the metal member 110) is about 530 ° C., the superheated steam temperature in the heat exchanger 101 shown in FIG. 1 is about 500 ° C.

Further, the surface area of the fluid in the heat exchanger 101 in contact with the fluid in the heat exchanger 101 before the fluid flowing in from the supply port 111 is discharged from the discharge port 112 is about 10000 mm ² . That is, in the heat exchanger 101 shown in FIG. 1, when the supply saturated steam pressure is 0.15 MPa and the supply saturated steam flow rate is 100 kg / h, the heat for adjusting the temperature of the discharged superheated steam to about 500 ° C. The contact surface of the fluid in the exchanger 101 is about 0.3 m ² .

Further, in the heat exchanger 101, when the surface area in contact with the fluid is about 0.3 m ² , when the supply saturated steam flow rate in the heat exchanger 101 is 100 kg / h, the volume becomes large when heated to 500 ° C. When heated to 550 ° C, the volume becomes about 3500 times the volume at the time of inflow and about 3700 times the volume at the time of inflow. As described above, if the heat exchanger 101 is used, a very large volume of superheated steam can be obtained.

Therefore, according to the heat exchanger 101 having the above configuration, when the heat exchange rates are the same, the surface area in contact with the fluid can be significantly reduced as compared with the conventional heat exchanger having a honeycomb structure. Therefore, if the heat exchange rate is the same, it is possible to realize a heat exchanger in which the size of the entire device is much smaller than that of a heat exchanger in which the contact area of a honeycomb structure or the like is physically increased.

In the present invention, the heat exchanger shown in FIG. 1 has been further improved to realize a heat exchanger that is compact and capable of further improving the heat exchange rate. This heat exchanger will be described in the first embodiment below.

[Embodiment 1]
Embodiments of the present invention will be described below.

(Overview of heat exchanger)
FIG. 2 is a schematic configuration diagram of the heat exchanger 1 according to the present embodiment. The heat exchanger 1 shown in FIG. 2 has substantially the same configuration as the heat exchanger 101 shown in FIG. 1, but the structure of the metal member 10 is different.

That is, as shown in FIG. 2, the heat exchanger 1 serves as an inlet for a heating tank 30 including a plurality of metal members 10 inside and a fluid (arrow in the figure) for supplying the fluid to the heating tank 30. It includes a supply port 11 and a discharge port 12 that serves as an outlet for the fluid discharged from the heating tank 30. The heat exchanger 1 has substantially the same configuration as the heat exchanger 101 shown in FIG. 1, but the configuration of the metal member 10 is different. That is, the metal member 10 has the same function as the metal member 110 shown in FIG. 1, and further, the fluid circulates in the partition chamber 14 and repeatedly contacts the high temperature wall surface to obtain a more effective heat transfer area. The configuration is such that an increasing effect can be obtained.

The metal member 10 is made of a substantially disk-shaped metal plate, and is arranged in the heating tank 30 at predetermined intervals in the traveling direction of the fluid so that the plate surfaces face each other. The positioning of the metal member 10 is performed by passing the positioning shaft 13 through the through hole 10c formed in the center of the metal member 10. Each metal member 10 is fixed at a predetermined position on the shaft 13 by metal welding. That is, each of the metal members 10 is arranged so that the plate surfaces face each other in the heating tank 30, and the shaft connecting the center points of the plate surfaces is arranged along the inflow direction of the fluid.

Further, the metal member 10 arranged in the heating tank 30 is located at least on the most upstream side (supply port 11) from the upstream side to the downstream side (hereinafter, simply referred to as the upstream side and the downstream side) of the fluid flow. The thickness D1 of the metal member 10 arranged at the position closest to the side) is formed to be thicker than the thickness D2 of the metal member 10 arranged on the adjacent downstream side. Further, the thickness D3 of the metal member 10 arranged on the downstream side adjacent to the metal member 10 having the thickness D2 is formed to be thinner than the thickness D2. That is, the thicknesses of the two metal members 10 arranged adjacent to each other have a relationship of D1> D2> D3. The relationship may be D1> D2 = D3. Further, the thickness of the fourth and subsequent metal members 10 may be thinner than the thickness of the metal member 10 on the upstream side thereof, or may be the same thickness. Further, the thickness of all the metal members 10 may be the same. The details of the metal member 10 will be described later.

The heating tank 30 is made of a substantially cylindrical metal cylinder whose inner diameter is substantially the same as the outer diameter of the metal member 10. As a result, the peripheral end surface 10d of the metal member 10 arranged in the heating tank 30 comes into close contact with the inner surface 30a of the heating tank 30. In order to eliminate the gap between the peripheral end surface 10d of the metal member 10 and the inner surface 30a of the heating tank 30, the contact portion is metal welded. If the degree of adhesion between the peripheral end surface 10d of the metal member 10 and the inner surface 30a of the heating tank 30 is high, metal welding does not have to be performed.

In the heating tank 30, among the adjacent metal members 10, the first surface 10a, which is the surface on the upstream side metal member 10 on the fluid outflow side, and the surface on the downstream side metal member 10 on the fluid inflow side. The space surrounded by the second surface 10b and the inner surface 30a of the heating tank 30 is referred to as a partition chamber 14. That is, a plurality of compartments 14 are formed in the heating tank 30. In the partition chamber 14, the fluid flowing in from the second surface 10b of the metal member 10 on the upstream side is discharged from the first surface 10a of the metal member 10 toward the first surface 10a of the metal member 10 on the downstream side.

In the partition chamber 14, the fluid discharged from the discharge hole 10e formed in the metal member 10 on the upstream side of the fluid among the adjacent metal members 10 hits the second surface 10b of the metal member 10 on the downstream side and is disturbed. It becomes a flow and stays. In the partition chamber 14, the fluid discharged from the discharge hole 10e hits the second surface 10b of the metal member 10 at high speed, so that the fluid changes from turbulent flow to high-speed rotating vortex flow. Then, the fluid staying in the compartment 14 is discharged from the discharge hole 10e formed in the metal member 10 and sent to the adjacent compartment 14 arranged in the traveling direction of the fluid. In this way, the fluid is sequentially sent to the partition chamber 14 on the downstream side and discharged from the discharge port 12 of the heating tank 30.

The heat exchanger 1 heats the heating tank 30 by heating the heating tank 30 from the outside. As a result, the fluid that sequentially passes through the adjacent downstream partition chamber 14 while staying in the compartment 14 formed in the heating tank 30 is continuously heated.

Also in the heat exchanger 1 shown in FIG. 2, the heating means heats using the electromagnetic induction heating method in the same manner as in the heat exchanger 101 of FIG.

(Metal member)
The metal member 10 arranged in the heating tank 30 will be described below with reference to FIGS. 3 and 4. FIG. 3A is a front view of the metal member 10 as viewed from the fluid input surface side, and FIG. 3B is the end surface of the metal member 10 shown in FIG. 3A on the AA line. It is a figure. FIG. 4A is a front view of the metal member 10 as viewed from the fluid input surface side, and FIG. 4B is a cross section taken along the line BB of the metal member 10 shown in FIG. 4A. It is a figure.

As shown in (b) of FIG. 3 and (b) of FIG. 4, the metal member 10 has a plate shape, and the thickness in the cross-sectional direction is thinner on the through hole 10c side than on the peripheral end surface 10d side. It is formed like this. Specifically, similarly to the metal member 110 shown in FIG. 1, the thickness is the same from the peripheral end surface 10d toward the through hole 10c to a predetermined distance, and after the predetermined distance is passed, gradually toward the through hole 10c. The metal member 10 is formed so as to be thin. In other words, the wall thickness of the metal member 10 on the through hole 10c side is thinner than that on the peripheral end surface 10d side, and the wall thickness in the vicinity of the through hole 10c is the thinnest.

As described above, also in the metal member 10 of the heat exchanger 1, similarly to the metal member 110 of the heat exchanger 101 shown in FIG. 1, from the peripheral end surface 10d side of the metal member 10 to a predetermined distance toward the through hole 10c. The thickness of the metal is constant, and the thickness from that point onward gradually decreases to the through hole 10c. That is, the metal member 10 includes a first portion having a constant thickness from the peripheral end surface 10d to a predetermined distance, and a second portion having a gradually thinning thickness from the predetermined distance to the through hole 10c. .. Therefore, the metal member 10 is subjected to heat conduction in the same manner as the metal member 110. The metal member 10 is different from the metal member 110 in that the structure of the discharge hole 10e, the protrusion 10f formed by continuous spiral protrusions, and the position where the fluid discharged from the discharge hole 10e hits the second surface 10b. It is a point where a substantially conical protrusion 10g formed in the above is formed.

First, the discharge hole 10e formed in the metal member 10 will be described.

As shown in FIGS. 3 and 4, the metal member 10 has a plurality of discharge holes 10e which are fluid passages.

The discharge hole 10e has a fluid inlet 10eIN formed on the second surface 10b side, which is the inflow side of the fluid, and a fluid outlet 10eOUT formed on the first surface 10a side, which is the fluid discharge side. There is. The inlet 10eIN of the discharge hole 10e is located on a concentric circle centered on the center point of the metal member 10, and similarly, the outlet 10eOUT is located on a concentric circle centered on the center point of the metal member 10. As shown in FIGS. 3 and 4, the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e are obliquely displaced from the extending direction of the through hole 10c through which the shaft 13 penetrates. Each discharge hole 10e is formed so that the penetration direction of the through hole connecting the inlet 10eIN and the outlet 10eOUT has the same inclination angle with respect to the extension direction of the shaft 13. As a result, the fluid discharged from each discharge hole 10e is discharged diagonally and in the same direction with respect to the first surface 10a of the adjacent metal members 10 arranged to face each other. As a result, the discharged fluid forms a vortex flow centered on the through hole 10c in the compartment formed between the two metal members 10. In order to properly form the vortex, it is preferable that the direction and the distance at which the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e are shifted are common to each of the discharge holes 10e. In other words, each discharge hole 10e has the same inclination angle with respect to the extension direction of the shaft 13 so that the fluid discharged from the outlet of the discharge hole 10e can form a vortex. It is formed.

From the above, for each of the plurality of discharge holes 10e included in the metal member 10, the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e are formed on concentric circles centered on the center point of the metal member 10. It is formed at equal intervals on the same circumference, and the straight line connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e and the extension direction of the shaft 13 are at twisted positions, and the inlet 10eIN and the outlet of the discharge hole 10e The angle formed by the extending direction of the shaft 13 may be the same for each of the straight lines connecting the 10eOUT.

Further, as shown in FIGS. 3 and 4 (a), the discharge holes 10e may be formed on concentric circles having different distances (radii) from the through holes 10c. In this case, it is preferable that the through holes 10c are not arranged on the same straight line extending in the radial direction from the through holes 10c.

As a result, the fluid passing through each of the discharge holes 10e is obliquely inclined to the second surface 10b of the lower metal member 10 after the traveling direction is deviated by the same angle in the same rotation direction with respect to the stretching direction of the shaft 13. Hit from the direction. Therefore, every time the fluid passes through the metal member 10, a vortex is formed. That is, the fluid stays for a long time while forming a high-speed rotating vortex in the partition chamber 14 formed from the peripheral end surface 10d of the metal member 10 to the through hole 10c, increasing the effective heat transfer area and forcibly convective heat transfer by the vortex. It is possible to heat a fluid with very high efficiency.

Further, the number of discharge holes 10e in each metal member 10, the size (diameter), shape, etc. of each discharge hole 10e are not particularly limited, and are appropriately set according to the amount of fluid supplied to the heat exchanger 1. do it. For example, the shape of the discharge hole 10e may be circular or rectangular.

In the metal member 10, the distance from the center of the inlet of the discharge hole 10e to the center of the metal member 10 and the distance from the center of the outlet of the discharge hole 10e to the center of the metal member 10 are the same. It may be different or it may be different.

Further, in order to properly form a vortex, it is preferable to satisfy the following three conditions for each of the discharge holes 10e as described above. (1) The inlet 10eIN and the outlet 10eOUT of the discharge hole 10e are formed on concentric circles centered on the center point of the metal member 10, and are formed at equal intervals on the same circumference. (2) The straight line connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e and the extending direction of the shaft 13 are in twisted positions. (3) The angle formed by the extending direction of the shaft 13 is the same for each of the straight lines connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e.

However, in order to form a vortex in the compartment 14, the positional relationship between the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e does not necessarily have to be as described above. That is, the straight line connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e and the extending direction of the shaft 13 are indispensable to be in a twisted position, but the straight line connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e. The angles formed by the shaft 13 with respect to the stretching direction need not be the same for each of the above. That is, each discharge hole 10e of the metal member 10 does not have to be formed so as to discharge the fluid in the same direction as long as it can be discharged in an oblique direction rather than perpendicular to the second surface 10b of the metal member 10 facing each other.

Next, the protrusion 10f formed on the second surface 10b of the metal member 10 will be described.

As shown in (a) of FIG. 3 and (a) of FIG. 4, the second surface 10b of the metal member 10 is continuously formed in a spiral shape centered on the center (through hole 10c) of the metal member 10. The formed protrusion 10f is arranged. The protrusion 10f is made of a ridge-shaped member formed in a spiral shape, and is formed along a desired vortex flow direction in the partition chamber 14. However, the protrusion 10f is formed so that the fluid discharged from the discharge hole 10e of the opposing metal member 10 does not directly hit the protrusion 10f. The protrusion 10f functions to guide the fluid in the compartment 14 in the direction in which the fluid flows. As a result, the fluid in the partition chamber 14 travels along the protrusion 10f, so that a higher speed vortex can be formed. In this way, the fluid discharged from the discharge hole 10e becomes a high-speed vortex in the partition chamber 14 due to the spiral protrusion 10f, so that the fluid can be in contact with the metal member 10 heated to a high temperature for a longer time. .. As a result, it is possible to heat the fluid with extremely high efficiency by further increasing the effective heat transfer area and forcibly convective heat transfer by the vortex.

As described above, the protrusion 10f is not formed at a position where the fluid discharged from the discharge hole 10e directly hits. As shown in FIGS. 3 (b) and 4 (b), a protrusion 10 g is formed at a position where the fluid discharged from the discharge hole 10e directly hits.

Next, the protrusion 10g formed on the second surface 10b of the metal member 10 will be described.

As shown in (b) of FIG. 3 and (b) of FIG. 4, the protruding portion 10g is the metal member on the second surface 10b, which is the surface on the inflow side of the fluid among the plate surfaces of each of the metal members 10. It is formed at a position on a straight line connecting the inlet 10eIN and the outlet 10eOUT of the discharge hole 10e of the metal member 10 arranged adjacent to the upstream side of the 10. As a result, the fluid discharged from the discharge hole 10e hits the protrusion 10g and diffuses as shown in FIG. 7A. That is, the protrusion 10g functions as a diffusion member that diffuses the fluid discharged from the discharge hole 10e in the partition chamber 14. The protrusion 10g is, for example, conical, and the size of the bottom surface is preferably about the same as or slightly smaller than the inner diameter of the discharge hole 10e, but may be larger than that.

Here, as described above, the discharge hole 10e of the metal member 10 is inclined with respect to the second surface 10b of the opposing metal member 10. Therefore, as shown in FIG. 7A, the fluid discharged from the discharge hole 10e diagonally hits the protrusion 10g of the second surface 10b. If the direction of inclination of each discharge hole 10e is along the rotation direction of the vortex, the fluid discharged from each discharge hole 10e diagonally hits the protrusion 10g, is more likely to be diffused, and is more likely to generate turbulence. In this case, by aligning the inclination direction of each discharge hole 10e with the spiral direction of the spiral protrusion 10f, the fluid becomes a vortex at a higher speed in the compartment 14, and the fluid in the compartment 14 becomes hot. The time of contact with the metal member 10 (residence time) becomes longer.

Note that the protrusion 10g is not limited to a conical shape, and is not particularly limited as long as it has a shape that allows the discharged fluid to diffuse by hitting it. The protruding portion 10g may be any one as long as it protrudes from the surface of the second surface 10b, for example. However, the protrusions 10g are not formed in a continuous manner like the protrusions 10f, but are formed in fragments at positions where the fluid discharged from the discharge holes 10e directly hits.

The

protrusions

10f and 10g of the metal member 10 shown in FIGS. 3 and 4 may be replaced with continuous recesses and non-continuous recesses, respectively. For example, instead of the metal member 10, as shown in FIGS. 5 and 6, a recess 10i formed of a continuous spiral recess instead of the protrusion 10f and a recess of a non-continuous recess instead of the protrusion 10g. Even if the metal member 10A having 10h formed on the second surface 10b is used, the same effect as that of the metal member 10 can be obtained. As in the case of the protrusion 10g, as shown in FIG. 7B, if the fluid discharged from the discharge hole 10e hits the recess 10h, it diffuses.

An example in which only the protrusion 10g is formed on the second surface 10b as shown in FIG. 3B, and only the recess 10h is formed on the second surface 10b as shown in FIG. 5B. Although the example described above has been described, the protrusion 10g and the recess 10h may be mixed for the purpose of forming a turbulent flow. However, even if the protrusions 10g and the recesses 10h are mixed, they are formed at positions where the fluid discharged from the discharge holes 10e hits.

The shape of the metal member 10 (10A) is not particularly limited, but may be any shape as long as the peripheral end surface 10d can be brought into close contact with the inner surface 30a of the heating tank 30. That is, the shape of the metal member 10 (10A) may be determined according to the internal shape of the heating tank 30. For example, the shape of the metal member 10 (10A) is circular if the internal shape of the heating tank 30 is circular, elliptical if elliptical, rectangular if it is rectangular, and many with the same number of angles if it is polygonal. It may be rectangular.

The material of the metal member 10 (10A) may be appropriately set according to the application of the heat exchanger 1 to be used. For example, when the heated fluid discharged from the heat exchanger 1 is used for food purposes, it is preferable to use a non-rusting material such as stainless steel. The material of the metal member 10 (10A) is preferably a metal having a high thermal conductivity. Specifically, as the material constituting the metal member 10 (10A), for example, iron, aluminum, copper or the like may be used, or an alloy may be used.

In this embodiment, an electromagnetic induction heating method is adopted as a method for heating the heat exchanger 1. Therefore, as a material constituting the metal member 10 (10A), it is necessary to use a material that generates an eddy current when a high frequency AC voltage is applied from the outside. Examples of such a material include a magnetic material. Specific examples of the metal member 10 which is the magnetic material include a strong magnetic metal such as iron and stainless steel (SUS) 430.

(Manufacturing method of heat exchanger)
Here, a method of manufacturing the heat exchanger 1 will be described. In the following description, a case where the disk-shaped metal member 10 is used will be described with reference to the heat exchanger 1 shown in FIG.

First, prepare a disk-shaped metal member 10. Here, SUS430 is used as the disk-shaped metal member 10.

Next, one side of the disk-shaped metal member 10 is ground so that the wall thickness becomes thinner from the peripheral portion to the central portion. Specifically, the metal member 10 is ground using a lathe.

Next, a through hole 10c is formed in the center of the metal member 10 in order to adjust the position between the plurality of metal members 10. The through hole 10c is formed for easy positioning and is not always necessary.

After that, a discharge hole 10e is formed in the metal member 10.

Next, the positioning shaft 13 is passed through the through hole 10c formed in the center of the metal member 10, and a plurality of metal members 10 are passed through the shaft 13.

After that, the peripheral end surface 10d of the metal member 10 is metal-welded to the inner surface 30a of the heating tank 30, and each metal member 10 is fixed at a predetermined position in the heating tank 30. When positioning is performed using the shaft 13, the shaft 13 and the metal member 10 may or may not be welded.

Finally, the fluid supply ports 11 and discharge ports 12 are attached to both ends of the heating tank 30. The heat exchanger 1 is manufactured as described above.

In the above description, the flat metal member 10 is ground to make a metal member 10 whose inner side portion is thinner than the peripheral portion, but the inner side portion thereof is thinner than the peripheral portion from the beginning. When the thin metal member 10 is used, the step of performing the above grinding is not necessary.

Further, in the above description, welding is performed after positioning all of the plurality of metal members 10 to be welded to the inner surface of the heating tank 30, but for example, the peripheral edges of the two metal members 10 are first welded to each other. After that, another metal member 10 may be further superposed on this and welded.

Further, the above welding includes, for example, cold welding in addition to at least one normal welding such as electric welding, laser welding, argon welding and gas welding. Moreover, you may combine the above-exemplified welding as appropriate.

(Performance comparison)
FIG. 8 is a graph showing the results of the performance test of the heat exchanger 1 shown in FIG.

FIG. 9 is a graph showing the results of the performance test of the heat exchanger of the comparative example. Here, in the heat exchanger of the comparative example, the thickness of the metal member 10 in the heat exchanger 1 shown in FIG. 2 is the same from the peripheral end surface 10d to the through hole 10c. The number of metal members 10 is 16. Further, the heat exchanger of the comparative example is almost the same as the heat exchanger 1 shown in FIG. 2, but differs from the heat exchanger 101 in that the thickness of the metal member is the same 10 mm from the peripheral end surface to the through hole. ..

The performance test was conducted under the following conditions.

Supply saturated steam pressure: 0.15 MPa
Supply saturated steam flow rate: 100 kg / h
From the start of heating until the temperature of superheated steam stabilizes: Approximately 20 kW
After superheated steam temperature stabilizes: Approximately 14.8 kW
Here, the performance of the heat exchanger is compared by comparing the temperature of the superheated steam obtained by the heat exchanger (the temperature for 60 minutes after the rated temperature is stabilized). The temperature of the superheated steam is measured at the outlet temperature at which the fluid of the heat exchanger is discharged.

From the graph of FIG. 8, when the heat generating body temperature is about 630 ° C., the superheated steam temperature in the heat exchanger 1 shown in FIG. 2 is about 600 ° C., and from the graph of FIG. 9, when the heat generating body temperature is about 530 ° C. The superheated steam temperature in the heat exchanger of the comparative example was about 500 ° C. As described above, it can be seen that the superheated steam temperature of the heat exchanger 1 is about 100 ° C. higher than that of the conventional heat exchanger. Moreover, even though the power consumption values are the same, the graph shown in FIG. 8, that is, the heat exchanger 1 shown in FIG. 2 can obtain a superheated steam temperature as high as 100 ° C. In other words, it can be seen that a heat exchange rate that is significantly superior to that of the conventional heat exchanger can be realized. This is because the fluid stays in the partition chamber 14 for a long time while forming a high-speed rotating vortex by devising the penetrating direction of the discharge hole 10e formed in the metal member 10, and the effective heat transfer area is increased and the vortex is caused. This is because the fluid can be heated with very high efficiency by forced convection heat transfer.

On the other hand, in the heat exchanger of the comparative example, the discharge holes of the metal members are formed parallel to the traveling direction of the fluid passing through the heating tank, similarly to the heat exchanger 101 shown in FIG. , The residence time of the fluid in the compartment 114 is shorter than that of the heat exchanger 1 shown in FIG. As a result, the fluid cannot be sufficiently heated.

In addition, the difference in the above performance depends on the difference in the temperature of the heat generating body, that is, the temperature of the metal member. The metal member 10 in the heat exchanger 1 shown in FIG. 2 has a first portion having a constant thickness from the peripheral end surface 10d to a predetermined distance, and a first portion in which the thickness from the predetermined distance to the through hole 10c is gradually reduced. Since it is composed of two parts, the second part whose thickness is gradually reduced is easier to dissipate heat than the first part having a constant thickness. Therefore, from the peripheral end surface 10d of the metal member 10 to the through hole 10c. Can be heated almost uniformly to a temperature close to the Curie temperature. Therefore, the steam staying in the compartment 14 can be continuously heated at a higher temperature.

On the other hand, if the thickness of the metal member is the same from the peripheral end surface to the through hole, it is difficult to dissipate heat in any part of the metal member. Therefore, when raising the temperature on the through hole side of the metal member to near the Curie temperature. , It is necessary to heat the temperature of the peripheral end surface side of the metal member so as to be higher than the Curie temperature, which is not realistic. That is, unlike the metal member 10, it is not possible to heat from the peripheral end surface to the through hole substantially uniformly to a temperature close to the Curie temperature. Therefore, the steam staying in the compartment cannot be continuously heated at a higher temperature.

(effect)
According to the above configuration, the fluid that has passed through each of the discharge holes 10e is displaced by the same angle in the same direction as the stretching direction of the shaft 13, and then the second surface 10b of the lower metal member 10 Hits diagonally. Therefore, every time the fluid passes through the metal member 10, a vortex is formed. Further, of the two metal members 10 constituting the wall of the partition chamber 14, a spiral protrusion is provided on the surface (second surface 10b) of the metal member 10 arranged on the downstream side in the inflow direction of the fluid into which the fluid flows. Since the 10f is formed, the turbulence formed on the second surface 10b of the metal member 10 on the downstream side by the fluid discharged from the discharge hole 10e of the metal member 10 on the upstream side forming the wall in the partition chamber 14. The flow moves in a spiral along the protrusion 10f.

From these facts, since a high-speed rotating vortex of the fluid is formed in the compartment 14, the fluid circulates in the compartment 14 and repeatedly contacts the high-temperature wall surface at high speed, resulting in an effect of increasing the effective heat transfer area. It can be obtained and the heating efficiency can be increased.

Therefore, since the effective heat transfer area of the fluid is increased to increase the heating efficiency, a sufficiently high heating efficiency can be obtained without increasing the heat exchanger itself as in the conventional case. Moreover, the fluid can be retained in the partition chamber 14 for a long time only by devising the penetrating direction of the discharge hole 10e, and the fluid can be heated with extremely high efficiency, so that the power consumption is increased. Can be suppressed. In other words, in order to obtain the same heating efficiency, the heat exchanger 1 of the present embodiment is smaller in size and consumes less power than the conventional heat exchanger.

Further, since the metal member 10 is formed so that the inner side portion thereof is thinner than the peripheral edge portion, the heat supplied from the outside is efficiently transferred from the peripheral edge portion to the central portion of the metal member 10. It will be. Therefore, since the wall constituting the compartment 14 is sufficiently heated, the fluid guided to the compartment 14 can be sufficiently heated as compared with the conventional case.

Further, the wall thickness of the adjacent metal member 10 arranged in the heating tank 30 is larger in the metal member 10 arranged on the downstream side than in the metal member 10 arranged on the upstream side in the inflow direction of the fluid. By being thin, the heat on the upstream side is transferred to the downstream side at high speed and with high efficiency, so that the heat transfer characteristics can be further improved and the fluid can be heated more preferably. As a result, the sufficiently heated fluid on the upstream side in the inflow direction of the fluid is guided to the compartment 14 on the downstream side while maintaining the high temperature, so that it is possible to obtain a sufficiently heated fluid. Become.

Normally, in order to increase the heat exchange rate of the heat exchanger, it is necessary to increase the effective heat transfer area itself, the area of the part (fins, etc.) for heat exchange increases, and the heat exchanger itself becomes large.

On the other hand, in the heat exchanger 1 of the present embodiment, as described above, in order to increase the heat exchange rate of the heat exchanger 1, the fluid forms a high-speed rotating vortex in the partition chamber 14, and is effectively transferred. Since the effect of increasing the heat area is obtained, it is not necessary to increase the effective heat transfer area itself. Therefore, in order to obtain the same heat exchange rate, the size of the heat exchanger 1 according to the present embodiment can be made smaller than that of the conventional heat exchanger.

As described above, in order to be heated to near the Curie temperature and form a high-speed rotating vortex in the partition chamber 14, the metal member 10 having the above configuration is not limited to the above, and other metal members may be used. ..

[Aspect 1]
The heat exchanger of the present invention includes a heating tank having a partition chamber inside for retaining the inflowing fluid, and heats the retained fluid in the compartment by heating from the outside of the heating tank. It is a heat exchanger and has a plurality of substantially disk-shaped metal members having a plurality of discharge holes which are fluid passages, and each of the metal members is arranged so that the plate surfaces face each other in the heating tank. In addition, the axis connecting the center points of each plate surface is arranged along the inflow direction of the fluid, and the wall of the partition chamber is composed of at least two adjacent metal members, and the metal members have the same. For each of the plurality of discharge holes, the inlet and outlet of the discharge holes are formed on concentric circles centered on the center point of the metal member, and are formed at equal intervals on the same circumference. The heat exchanger is characterized in that the straight line connecting the inlet and the outlet of the discharge hole is oblique to the facing surface of the metal member on the outlet side.

According to the above configuration, the fluid passing through each of the discharge holes 10e is displaced by the same angle in the same direction as the stretching direction of the shaft 13, and then the second surface 10b of the lower metal member 10 Hits diagonally. Therefore, every time the fluid passes through the metal member 10, a vortex is formed. As a result, a high-speed rotating vortex of the fluid is formed in the compartment, so that the fluid circulates in the compartment and repeatedly contacts the high-temperature wall surface at high speed. As a result, the effect of increasing the effective heat transfer area is obtained, and the heating efficiency is improved. Can be enhanced.

Therefore, in order to increase the effective heat transfer area of the fluid and increase the heating efficiency, it is possible to obtain a sufficiently high heating efficiency without increasing the size of the heat exchanger in the longitudinal direction as in the conventional case. Moreover, the fluid can be retained in the compartment for a long time simply by devising the penetration direction of the discharge hole, and the fluid is heated with extremely high efficiency, so that the increase in power consumption is suppressed. can do.

[Aspect 2]
For each of the plurality of discharge holes of the metal member, the inlet and outlet of the discharge holes are formed on concentric circles centered on the center point of the metal member, and are equally spaced on the same circumference. The straight line connecting the inlet and the outlet of the discharge hole and the shaft are in a twisted position, and each of the straight lines connecting the inlet and the outlet of the discharge hole is formed with the shaft. The angles may be the same.

According to the above configuration, the straight line connecting the inlet and the outlet of the discharge hole and the shaft are in a twisted position, and each of the straight lines connecting the inlet and the outlet of the discharge hole is formed by the shaft. If the angles are the same, the fluid discharged from the metal member is discharged in the same direction with respect to the facing surfaces of the opposing metal members. As a result, the vortex flow by the fluid in the compartment between the metal members becomes faster, the fluid can be retained in the compartment for a longer period of time, and the fluid is heated with extremely high efficiency. Therefore, it is possible to suppress a large increase in power consumption.

[Aspect 3]
Each of the metal members is a position on a straight line connecting the inlet and outlet of the discharge hole of the metal member arranged adjacent to the upstream side of the metal member on the surface of the plate surface on the fluid inflow side. In addition, a diffusion member for diffusing the fluid discharged from the discharge hole may be formed.

According to the above configuration, the fluid discharged from the discharge hole of the metal member surely hits the diffusion member formed on the inflow surface of the fluid of the opposing metal member and becomes a turbulent flow. As a result, more high-speed rotating vortices of the fluid can be formed.

[Aspect 4]
The metal member has a first portion formed with a constant thickness from the peripheral end surface toward the center of the compartment to a predetermined distance, and the first portion beyond the first portion to the center of the compartment. It may include a second portion formed gradually thinner than the thickness of the portion.

According to the above configuration, since the thickness of the second portion of the metal member is gradually reduced from the thickness of the first portion, the second portion is easier to dissipate heat than the first portion having a constant thickness. As a result, even if heating is performed from the first portion near the heat source, heat is dissipated at the second portion far from the heat source, so that the heat from the heat source is easily transferred to the entire metal member, and as a result, the metal is concerned. It is possible to heat the entire member to a very high temperature. Therefore, since the metal member constituting the wall of the compartment is heated to a very high temperature, the fluid staying in the compartment is heated to a very high temperature by contacting or radiating heat from the metal member.

Therefore, since the effective heat transfer area of the fluid is increased and the heating efficiency is increased as in the conventional case, a sufficiently high heating efficiency can be obtained without increasing the heat exchanger itself. In other words, the heat exchanger of the present invention can be smaller than the conventional heat exchanger in order to obtain the same heating efficiency.

[Aspect 5]
Of the two metal members constituting the wall of the compartment, the metal member arranged on the downstream side in the inflow direction of the fluid has a spiral shape centered on the center of the metal member on the surface on which the fluid flows. Grooves may be formed.

According to the above configuration, of the two metal members constituting the wall of the compartment, the center of the metal member is centered on the surface of the metal member arranged on the downstream side in the inflow direction of the fluid into which the fluid flows. By forming the spiral groove, the turbulent flow formed on the surface of the other metal member by the fluid discharged from the discharge hole of one metal member constituting the wall in the compartment swirls along the groove. Move into a shape. As a result, a high-speed rotating vortex of the fluid is formed in the compartment, so that the fluid circulates in the compartment and repeatedly contacts the high-temperature wall surface at high speed. As a result, the effect of increasing the effective heat transfer area is obtained, and the heating efficiency is improved. Can be enhanced.

[Aspect 6]
The metal member may be formed so that the inner side portion thereof is thinner than the peripheral portion.

According to the above configuration, the metal member is formed so that the inner side portion thereof is thinner than the peripheral portion, so that the heat supplied from the outside is efficiently transferred from the peripheral portion to the central portion of the metal member. It will be transmitted well. Therefore, since the wall constituting the compartment is sufficiently heated, the fluid guided to the compartment can be sufficiently heated as compared with the conventional case.

[Aspect 7]
The wall thickness of the adjacent metal member arranged in the heating tank may be thinner in the metal member arranged on the downstream side than in the metal member arranged on the upstream side in the inflow direction of the fluid.

According to the above configuration, the wall thickness of the adjacent metal member arranged in the heating tank is larger in the metal member arranged on the downstream side than in the metal member arranged on the upstream side in the inflow direction of the fluid. By being thin, the heat on the upstream side is transferred to the downstream side at high speed and with high efficiency, so that the heat transfer characteristics can be further improved and the fluid can be heated more preferably. As a result, the sufficiently heated fluid on the upstream side in the inflow direction of the fluid is guided to the downstream compartment while maintaining the high temperature, so that the sufficiently heated fluid can be obtained.

The present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the claims, and the embodiments obtained by appropriately combining the technical means disclosed in the different embodiments. Is also included in the technical scope of the present invention.

Possibility of industrial use

The heat exchanger according to the present invention can be suitably used for heating by circulating a fluid in a heating tank.

1 Heat exchanger 10 Metal member

10a First surface

10b Second surface 10c Through hole 10d Peripheral end surface 10e Discharge hole 10f Protrusion 10g Protrusion (diffusion member: protrusion)
10i recess 10h recess (diffusion member: recess)
11 Supply port 12 Discharge port 13 Shaft 14 Section chamber 30 Heating tank 30a Inner surface 101 Heat exchanger 110 Metal member 110a First surface 110b Second surface 110c Through hole 110d Peripheral end surface 110e Discharge hole 111 Supply port 112 Discharge port 113 Shaft 114 section Room 130 Heating tank 130a Inner surface

Claims

A heat exchanger provided with a heating tank having a compartment for retaining the inflowing fluid inside, and heating the fluid retained in the compartment by heating from the outside of the heating tank.
It has a plurality of substantially disk-shaped metal members having a plurality of discharge holes which are fluid passages, and has a plurality of discharge holes.
Each of the metal members is arranged so that the plate surfaces face each other in the heating tank, and the axis connecting the center points of the plate surfaces is arranged along the inflow direction of the fluid.
The wall of the compartment is composed of at least two adjacent metal members.
For each of the plurality of discharge holes of the metal member,
A heat exchanger characterized in that the straight line connecting the inlet and the outlet of the discharge hole is oblique to the facing surface of the metal member on the outlet side.
For each of the plurality of discharge holes of the metal member,
The inlet and outlet of the discharge hole are formed on concentric circles centered on the center point of the metal member, and are formed at equal intervals on the same circumference.
The straight line connecting the inlet and outlet of the discharge hole and the shaft are in a twisted position.
The heat exchanger according to claim 1, wherein the angle formed by the shaft is the same for each of the straight lines connecting the inlet and the outlet of the discharge hole.
Each of the metal members is a position on a straight line connecting the inlet and outlet of the discharge hole of the metal member arranged adjacent to the upstream side of the metal member on the surface of the plate surface on the fluid inflow side. The heat exchanger according to claim 1 or 2, wherein a diffusion member for diffusing the fluid discharged from the discharge hole is formed therein.
The metal member has a first portion formed with a constant thickness from the peripheral end surface toward the center of the compartment to a predetermined distance, and the first portion beyond the first portion to the center of the compartment. The heat exchanger according to any one of claims 1 to 3, further comprising a second portion formed gradually thinner than the thickness of the portion.
Of the two metal members constituting the wall of the partition chamber, the metal member arranged on the downstream side in the inflow direction of the fluid has a spiral shape centered on the center of the metal member on the surface on which the fluid flows. The heat exchanger according to any one of claims 1 to 4, wherein a groove is formed.
The heat exchanger according to any one of claims 1 to 5, wherein the metal member is formed so that the inner side portion thereof is thinner than the peripheral portion.
The wall thickness of the adjacent metal member arranged in the heating tank is characterized in that the metal member arranged on the downstream side is thinner than the metal member arranged on the upstream side in the inflow direction of the fluid. The heat exchanger according to any one of claims 1 to 6.
The heat exchanger according to any one of claims 1 to 7, wherein the metal member is a magnetic material.