JP2003056995A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger channel having high heat transfer performance and directivity by configuring a new channel heating surface profile which can not only accelerate total average heat transfer utilizing a secondary flow but also enhance heat transfer at some fixed part given in the circumferential direction of the pipe wall concentrically. SOLUTION: In the heat exchanger for exchanging heat through a fluid 2 flowing through the inner channel of a circular tube 1, an annular elliptical member for inducing separation/secondary flow (rib part) 10 is provided in the circular tube 1 while inclining against the tube axis in order to generate a secondary flow in the downstream of the rib thus making thin the boundary layer in the vicinity of the heating surface and promoting heat transfer performance on the heating surface.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger for exchanging heat between a fluid flowing in a flow passage and a wall surface of the flow passage, and particularly to a fluid and the flow passage by inducing a secondary flow in the flow passage. The present invention relates to improvement of a flow passage and a shape inside the flow passage for promoting heat transfer performance between inner wall surfaces.

[0002]

2. Description of the Related Art When heat is transferred between a flow in a pipe and a wall surface, the fluid temperature in the vicinity of the pipe wall surface is always higher (when heating the fluid) or lower (when the fluid is heated) than the fluid temperature in the central portion of the tube. In the case of cooling), in other words, the temperature boundary layer is always formed along the wall surface. The basic principle of promoting heat transfer is to make this temperature boundary layer as thin as possible.

Conventional techniques for promoting heat transfer in straight pipes are roughly classified into the following three methods.

(1) The flow near the wall is disturbed. (For example, the wall surface is provided with roughness.) (2) The flow near the wall surface causes separation and reattachment.
[Provide a protrusion such as a rib on the wall surface or insert a wire coil. 13 (a), (b)] (3) A swirl flow is generated in the flow in the pipe. [Insert twisting tape, etc. FIG. 13 (c)] The above three methods are in accordance with the basic principle described above. Among them, (1) aims at promoting heat transfer by controlling the behavior of the fluid near the wall surface, 2) depends on the effect of heat transfer promotion by thinning the boundary layer near the reattachment point due to flow separation / reattachment, and (3) produces an axially symmetric swirl flow to form a temperature boundary layer. It is intended to be thin. However, in both cases, the fluid in the central part of the pipe is positively transported to the vicinity of the pipe wall, and the fluid near the pipe wall is returned to the central part of the pipe, causing a large-scale fluid movement over the entire cross section of the pipe. It's not a tie. If this could be achieved, heat transfer would be greatly enhanced. In addition to such an original average flow in the pipe axis direction, a flow having a velocity component in a cross section perpendicular to the pipe axis is called a secondary flow. Conventionally, such a secondary flow is positively used. Few attempts have been made to enhance heat transfer in a straight flow path.

When the secondary flow is generated, a heat transfer coefficient distribution is generated in the circumferential direction of the pipe wall according to the flow form (rotational direction) of the secondary flow. That is, the heat transfer on the side of the wall surface in the circumferential direction on which the secondary flow is directed is greatly promoted. The presence of such directivity can be extremely desirable and useful depending on the heat transfer system used outside the flow path.

[0006]

The methods conventionally used for promoting heat transfer in a tube are summarized in the above (1), (2) and (3), but all of them are Since the behavior of the fluid near the wall is controlled to promote heat transfer, any heat transfer promotion effect is not so large as compared to the heat transfer promotion by the mixing effect over the entire channel cross section. All of them are intended to promote heat transfer over the entire circumference of the inner wall surface of the pipe.

On the other hand, the present invention not only utilizes the secondary flow to promote the average heat transfer of the whole, but also concentrates the heat transfer of a given certain portion in the circumferential direction of the pipe wall. The purpose of the present invention is to provide a heat exchanger flow path having a high heat transfer performance and directivity by newly constructing a flow path heat transfer surface shape that can be raised.

[0008]

In order to achieve the above-mentioned object, the invention of claim 1 is a heat exchanger for exchanging heat via a fluid flowing through a flow path inside a circular pipe,
An elliptical annular separation / secondary flow inducing member is provided so as to be inclined with respect to the tube axis of the circular tube.

Further, the invention of claim 2 is a heat exchanger in which heat exchanging plates for exchanging heat through a fluid flowing through a channel having a circular cross section are arranged to face each other on the upper and lower surfaces of a thermoelectric module. In the flow path of the heat exchange plate, an elliptical ring-shaped peeling
The secondary flow inducing member is provided so as to be inclined with respect to the tube axis of the flow path.

The invention according to claim 3 is the invention according to claim 1 or 2, wherein a plurality of the separation / secondary flow inducing members are provided in a straight line portion of the flow path at regular intervals in the pipe axis direction. The feature is that they are arranged consecutively.

Further, in the invention of claim 4 according to the invention of claim 3, the constant interval (L) has a relationship of L / d = 1 to 2 with respect to the inner diameter (d) of the flow path. Characterize that.

The invention according to claim 5 is the invention according to any one of claims 1 and 2, wherein the separation / secondary flow inducing member is arranged at an angle of 45 to 60 ° with respect to the pipe axis direction. It is characterized by being done.

The invention according to claim 6 is the invention according to claim 1 or 2, wherein the height (h) and the thickness (t) of the separation / secondary flow inducing member are within the flow path. With respect to the diameter (d), h / d = 0.1 to 0.2, t / d = 0.
It is characterized by having a relationship of 1 to 0.2.

According to the invention of claim 7, in the invention of claim 2, the flow passage surface of the heat exchange plate on the side in contact with the thermoelectric module is the bottom surface, and the separation / secondary flow inducing member is based on the bottom surface. Is arranged so as to be inclined rearward with respect to the flow direction of the fluid.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 is a view showing a schematic structure of a circular pipe for passing a fluid (heat exchange medium) to be cooled or heated used in the heat exchanger according to the present invention.
Secondary flow inducing member (hereinafter, simply referred to as "rib") 10
The outline of the secondary flow generated by the action of is shown.

As shown in FIG. 1, an elliptical ring-shaped rib is provided inside the circular tube 1 in order to mix the fluid near the heat transfer surface and the fluid 2 at the center of the flow path by inducing a secondary flow. 10
Are inclined with respect to the flowing direction of the fluid 2 (tube axis).

As a result, a flow is induced along the ribs 10, and as a result, the fluid near the bottom wall is exposed to the ceiling (To
p) Since the fluid at the center of the circular pipe is transported to the bottom side, the heat transfer performance between the fluid and the inner wall surface of the circular pipe is promoted.

FIG. 2 is a view showing a test section (experimental apparatus) for measuring the heat transfer promotion effect due to the difference in the inclination angle of the rib by a heat transfer experiment using the circular tube 1 shown in FIG. .

In FIG. 2, the circular tube 1 used for this heat transfer experiment has an inner diameter (d) = 31 mm and an outer diameter (D).
= 38 mm, length (L) = 372 mm, made of heat-resistant cured vinyl chloride.

A conductive plastic heater is adhered to the inner wall of the tube, and by heating it electrically,
This is to obtain a uniform heat flux condition.

The rib portion 10 is made of the same material as the circular tube 1 and has a ring shape with a thickness of 3 mm and a height of 3 mm in the direction perpendicular to the flow direction.

In the measurement, the rib attachment angle is θ = 90 °, 75 °, 60 °, 45 ° in the backward tilted state.
Changed to. In each case, a total of 11 ribs were attached at intervals of 30 mm in the flow direction from the heating start point.

The dotted line in FIG. 2 indicates the position of the thermocouple for temperature measurement in the axial direction of the tube, and the circles in the figure indicate the thermocouple. The thermocouples are installed particularly densely in the axial direction after the dimensionless flow path position z / d = 5.5 after dividing the distance z from the heating start point by the tube diameter d, and in the circumferential direction, the upper part It is possible to investigate the detailed heat transfer coefficient distribution in the flow direction and the circumferential direction by attaching 8 points at 45 ° intervals.

FIG. 3 shows the Reynolds number (Re) = 10000 and the rib mounting angle θ = 45 according to the mode of the heat transfer experiment shown in FIG.
It is a figure which shows the heat transfer experiment result in (degree). In the figure, the horizontal axis is the dimensionless distance z / d from the heat transfer tube inlet, and the vertical axis is the value obtained by dividing the Nusselt number Nu indicating heat transfer performance by the Nusselt number Nu∞ sufficiently downstream of the smooth tube. is there.

In FIG. 3, the solid line shows the performance in the case of a smooth tube without ribs or the like. From this figure, it can be seen that the heat transfer performance is significantly improved when the ribs are installed with an inclination, as compared with the smooth tube.

As shown in FIG. 3, the local Nusselt number ratio (Nu / Nu∞) at the bottom (Bottom), which is the front part with respect to the fluid flow of the rib installed at an inclination with respect to the tube axis, is It can be seen that the rib shows a higher value than the top, which is the rear part of the fluid flow.

As described above, the reason why the inclined ribs bring about a remarkable effect of promoting heat transfer is that the cold fluid in the center of the flow path is bottomed by the secondary flow induced by the inclined ribs.
This is because the fluid carried to the wall side and heated near the bottom wall is carried away to the top side along the left and right pipe walls.

The Nusselt number ratio at the top is the lowest of all the circumferences of the pipe wall.
This is because the thermal boundary layer develops in the circumferential direction from the bottom to the top.

In FIG. 3, the Nusselt number ratio periodically fluctuates in the pipe axis direction at any position in the circumferential direction from Top to Bottom because of the effect of separation and reattachment of the flow by the individual ribs. by. In each case, the Nusselt number ratio shows a peak at the flow reattachment position.
That is, in the case of FIG. 3, in addition to the effect of the secondary flow,
Flow separation and reattachment effects also coexist.

FIG. 4 is a diagram showing the distribution of the average Nusselt number ratio Num / Nu∞ at each position in the circumferential direction at z / d = 7 to 9 (between about 3 ribs). The horizontal axis in the figure indicates the circumferential position of the circular pipe wall. 0 ° corresponds to Top and 180 ° corresponds to Bottom.

As shown in FIG. 4, it can be seen that the heat transfer performance of the ribbed tube is higher than the smooth tube (Smooth), but even among the ribbed tubes, the inclination angle is higher than that of the 90 ° ribbed tube. It can be seen that the Nusselt number ratio of the ribbed tube shows a higher value. A rib inclination angle of 90 ° corresponds to a so-called “ribbed tube” that has been widely used in the past, but as can be seen from the results of FIG. 4, even annular ribs having the same cross-sectional shape and dimensions can be It is confirmed that the heat transfer performance is remarkably higher than that of the conventional rib that is not tilted when the is inclined.

The degree of promotion of heat transfer by the inclined ribs depends on the smooth tube.
(smooth) shows a value of 2.5 to 3.5 times the Nusselt number ratio. From FIG. 4, when the average Nusselt number ratio in a ribbed tube with an inclination angle of 45 ° to 60 ° is no rib. (Smooth) and right-angled ribs (90 deg) show higher values, so that in the case of 45 ° to 60 °, the two-dimensional flow along the ribs is strong and the heat transfer performance is considered to be promoted.

Further, it can be seen from FIG. 4 that the heat transfer performance is distributed in the circumferential direction of the circular pipe. In the case of this example, the heat transfer performance of Bottom (180 °) is 30 to 40% higher than that of Top (0 °).

When constructing the heat exchanger, it may be desirable that there is a portion with high heat transfer performance or a portion with low heat transfer performance in the circumferential direction depending on the flow path configuration on the other side. In such a case, it is possible to improve the heat transfer performance on one side of the circumference and decrease the heat transfer performance on the other side by using such a flow path with inclined ribs. In other words, by using the inclined ribs, it becomes possible to give directivity to the circumferential distribution of the heat transfer performance.

That is, in conclusion, when the ribs are installed so as to be inclined with respect to the tube axis, the ribs induce a secondary flow, and the fluid in the central portion of the flow path is exchanged with the fluid in the vicinity of the heat transfer wall surface, resulting in remarkable heat transfer. Be promoted. It is understood that, within the range of the experimental conditions, the secondary flow of the ribbed tube having the rib inclination angle of 45 ° to 60 ° is the strongest, and the heat transfer performance in the entire flow path is the best.
Further, when a plurality of ribs are continuously arranged on the straight portion of the circular tube at regular intervals, the secondary flow induced by the individual ribs gradually becomes stronger, so that the heat transfer performance is further improved.

Further, the heat exchanger can be constructed by utilizing the difference in heat transfer performance between the Top side and the Bottom side.

Next, the case where the present invention is applied to a heat exchanger in which heat exchange plates for exchanging heat through a fluid flowing through an internal flow path having a circular cross section are arranged opposite to each other on both upper and lower surfaces of a thermoelectric module explain.

As this type of heat exchanger, various chemicals used for cleaning silicon wafers in a semiconductor manufacturing line, or various fluids such as organic solvents used for peeling a resist pattern for etching a semiconductor substrate in the same line are used. A heat exchanger using an electronic cooling element (thermomodule) that cools and heats by using the Peltier effect is known in order to cool or heat a fluid to obtain a fluid of a constant temperature. A heat exchanger using a module is used for the purpose of cooling or heating a fluid such as a chemical solution to a target temperature by the action of cooling and heat generation of the thermoelectric element module.

FIG. 5 is a top view of a heat exchanger (heat exchange unit) 100 using the above thermo module, and FIG.
[Fig. 6] is a right side view of the heat exchange unit 100 in Fig. 5.

As shown in FIGS. 5 and 6, the heat exchange unit 100 includes a heat exchanger (water cooling plate) 110a and a heat exchanger.
Between the (heat exchange plate) 110b, the thermo-module 50 and the O-ring 6 that surrounds the entire outer circumference of the thermo-module 50.
It has a structure in which 0 is sandwiched.

Bolt through holes 111 are formed in the heat exchange plate 110b.
b, 112b, 113b, 114b, 115b, 116
b, 117b, 118b, 119b are provided. These bolt through holes 111b, 112b, 113b, 114
b, 115b, 116b, 117b, 118b, 119
The screw holes 111a, 112a, 1 provided in the water cooling plate 110a facing the respective tightening bolts penetrating from b
13a, 114a, 115a, 116a, 117a, 1
By screwing into 18a and 119a (see FIG. 7), the water cooling plate 110a and the heat exchange plate 110b can be fixed with a predetermined tightening force.

The water cooling plate 110a and the heat exchange plate 110b
In order to fix the above as described above, there is another method of tightening with a tightening bolt and a nut.

By this tightening and fixing, the water cooling plate 110
a, a heat exchange plate 110b, an O-ring 60, and an inner O-ring 61 described later form an airtight space between the four members,
The thermo module 50 is enclosed in the space.

The thermo-module 50 is hermetically sealed so that dew condensation generated when the water-cooling plate 110a side or the heat-exchange plate 110b side when the heat exchange unit 100 is operating falls below the dew point of atmospheric air does not flow into the module 50. So that the moist atmosphere is also thermo module 5
There is a measure to prevent continuous invasion around 0.

In the heat exchange unit 100 of the present embodiment, the water cooling plate 110a is a so-called copper jacket type heat exchanger made of copper, and the heat exchange plate 110b is a heat exchanger of a type in which stainless steel or a copper pipe is cast with aluminum. Have flow passages 125a and 125b through which facility water and circulating water flow, respectively.

A fluid inlet 121a, a fluid outlet 122a, a fluid inlet 121b, and a fluid outlet 122b are formed at the ends of the channels 125a and 125b of the water cooling plate 110a and the heat exchange plate 110b, respectively.

The fluid inlet 121b and the fluid outlet 122b of the heat exchange plate 110b are connected to an inflow pipe and an outflow pipe (not shown) of the circulating water to be cooled, respectively. Water passes through the flow path 125b in the heat exchange plate 110b and flows out from the fluid outlet 122b to the outflow pipe.

Further, the fluid inlet 121 of the water cooling plate 110a
a and a fluid outlet 122a are connected to an inflow pipe and an outflow pipe (not shown) of the facility water, respectively, and the facility water flowing from the inlet pipe to the fluid inlet 121a receives the flow passage 1 in the water cooling plate 110a.
25a, and is discharged from the fluid outlet 122a to the outlet pipe.

The heat exchange plate 110b is attached in such a state that it is offset from the water cooling plate 110a by the piping space of the inflow pipe and the outflow pipe to the fluid inlet 121a and the fluid outlet 122a of the water cooling plate 110a.

FIG. 7 is a sectional view taken along line AA of FIG. 6, and FIG. 8 is a sectional view taken along line BB of FIG.

As can be seen from FIGS. 7 and 8, an outer O-ring 60 and an inner O-ring 61 are interposed between the water cooling plate 110a and the heat exchange plate 110b.

The outer O-ring 60 is provided with screw holes 112a, 113a, 114a, 115a, 11 of the water cooling plate 110a.
6a, 117a, 118a, 119a, and the heat exchange plate 1
10b bolt through holes 112b, 113b, 114b,
It has a size that fits just inside the inside of 115b, 116b, 117b, 118b, and 119b, and has a meandering shape so as to avoid (not block) each of these holes.

The inner O-ring 61 has a larger diameter than the bolt through hole 111b of the heat exchange plate 110b, and is arranged so as to concentrically surround the bolt through hole 111b and the screw hole 111a of the water cooling plate 110a.

The thermomodule 50 is mounted in the area between the outer O-ring 60 and the inner O-ring 61.

The thermo module 50 includes a P-type thermoelectric element,
A plurality of thermoelectric element pairs each including an N-type thermoelectric element and an electrode plate that joins these elements are provided. Specifically, the N-type thermoelectric element and the P-type thermoelectric element are alternately arranged in the vertical and horizontal directions. A plurality of pairs of elements are arranged side by side, and adjacent elements are joined to each other so that the upper joining plate (electrode plate) and the lower joining plate are electrically connected in series.

The upper joint plates and the lower joint plates respectively form planes (hereinafter, referred to as upper joint plate surfaces and lower joint plate surfaces) corresponding to the arrangement areas of the thermoelectric elements.

In FIG. 7, on the surface of the heat transfer surface of the water cooling plate 110a, a plurality of bonding plates 501a constituting, for example, the lower bonding plate surface of the thermo module 50 are provided with the above-mentioned O-ring 60.
Area between O-ring 61 and O-ring 61 (O-rings 60, 6
(Avoid the position 1) and are arranged at a uniform density.

A pair of N-type thermoelectric elements 502 and a pair of P-type thermoelectric elements 503 are erected on each of the joining plates 501a arranged on the surface of the heat transfer surface of the water cooling plate 110a. Each joining plate 501b on the (upper) joining plate surface
Connected to.

Similarly, in FIG. 8, the heat exchange plate 110b.
On the surface of the heat transfer surface of the O-ring 60 and the O-rings 60, a plurality of joint plates 501b constituting the upper joint plate surface of the thermo module 50 are formed.
They are arranged at the same density in the entire area between the ring 61 and the ring 61 (avoid the positions where the O-ring 60 and the O-ring 61 are arranged).

Each of the joining plates 501b arranged on the surface of the heat transfer surface of the heat exchange plate 110b has a pair of Ns.
A type thermoelectric element 502 and a P-type thermoelectric element 503 are provided upright, and are connected to the respective joining plates 501a on the opposite (lower) joining plate surfaces.

Regarding the arrangement of the plurality of joining plates 501a on the surface of the heat transfer surface of the water cooling plate 110a and the arrangement of the plurality of joining plates 501b on the surface of the heat transfer surface of the heat exchange plate 110b, a plurality of pairs of joints are used. It is also possible to prepare a plurality of unit thermomodules composed of the plate 501a or the joining plate 501b, and to lay out the thermomodules of a plurality of pairs on the surface of the heat transfer surface.

For example, a positive electrode electrode rod 131 and a negative electrode electrode rod 132 are connected to the two joining plates 501L (for lead electrodes: see FIG. 7) at the end of the thermomodule 50 having the above structure. It

By passing a direct current between the electrode rods 131 and 132, each joining plate 501 on the heat exchange plate 110b side
b is cooled, whereby the heat exchange plate 110b is cooled, and the circulating water flowing through the flow path 125b in the heat exchange plate 110b is cooled.

On the other hand, each joining plate 501 on the water cooling plate 110a side
a generates heat, and this heat is transmitted to the water cooling plate 110a and is exchanged with the facility water flowing in the flow passage 125a therein to be radiated.

Further, since the heat generation and the heat radiation are reversed by reversing the current direction, the circulating water can be easily heated.

In this heat exchange unit 100, the water cooling plate 1
In order to improve the heat exchange efficiency in the heat exchange plate 110a and the heat exchange plate 110b, the flow passage shapes of the water cooling plate 110a and the heat exchange plate 110b are also devised in accordance with the arrangement structure of the thermoelectric elements 502 and 503 described above.

FIG. 9 shows a heat exchange unit 1 according to the present invention.
It is a figure which shows the structure of the flow path 125a of the water cooling plate 110a of 00.

FIG. 9 shows the state of the internal flow path of the heat exchange plate b.

Here, in the present invention, as shown in FIG. 9, in the heat exchange unit 100 described above, a plurality of rib portions 10 are provided in the flow passage 125b of the heat exchange plate 110b.

The rib portion 10 shown in FIG. 9 is arranged in the meandering flow passage 125b including the straight line portion at a position where the straight line portion is continuous and is continuously arranged in each straight flow passage at a constant interval. .

The rib portion 10 suppresses the development of the boundary layer along the wall surface of the flow passage for the fluid (circulation water in this example) flowing through the flow passage 125b and induces the secondary flow in the downstream portion of the rib. Moreover, there is an effect that the fluid in the vicinity of the heat transfer surface and the fluid in the area away from the heat transfer surface are exchanged and mixed.

FIG. 10 shows a heat exchange plate 11 shown in FIG.
It is a perspective perspective view useful for grasping three-dimensionally the rib part 10 continuously arranged at regular intervals in the straight flow path in the flow path 125b of 0b.

As shown in FIG. 10, rib portions inclined by a predetermined angle with respect to the flow direction are arranged at regular intervals in the flow path.

That is, the flow passage surface on the side of the heat exchange plate 110b in contact with the thermo module is the bottom surface, and the rib portion 10 (separation / secondary flow inducing member) is tilted backward with respect to the flow direction of the fluid with the bottom surface as the base point. It is arranged to be tilted to the state. At this time, the heat transfer performance of the side on which the thermo module is attached is promoted, that is, the Bo shown in FIG.
It is important to determine the inclination direction of the rib 10 so that the ttom side is the thermomodule side.

Finally, as a method of forming the rib portion 10 arranged in the flow path of such a form, for example, the heat exchange plate 1
There is a method of arranging an elliptic ring-shaped rib member, which is manufactured separately from these plate members, in a straight line portion of the channel having a circular cross section formed in 10b in a form inclined at a predetermined angle with respect to the flow direction.

FIG. 11 shows an example in which the circular tubular flow channels 125b of FIG. 9 have different arrangement shapes.

The same effect can be obtained by arranging the ribs 10 continuously in a straight line portion of the flow path at regular intervals.

FIG. 12 is a diagram in which the enlarged heat transfer surface and the circular tubular flow path portion of another heat exchanger that does not use the thermoelectric element module as described above are extracted, but the present invention is as follows. The rib portion 10 described in the above embodiment is provided in the flow path (circular pipe) portion.
It is possible to obtain the same effect by providing. In the example of this figure, an enlarged heat transfer surface and a flow path (circular pipe) portion of a heat exchanger for air cooling or the like are shown.

[0080]

As described above, according to the present invention,
In a heat exchanger that exchanges heat via a fluid flowing through a flow path inside a circular pipe, by providing an elliptical annular separation / secondary flow inducing member (rib) inclining with respect to the pipe axis in the circular pipe. A secondary flow is generated downstream of the ribs, which thins the boundary layer near the surface of the heat transfer surface and promotes heat transfer performance on the heat transfer surface.

Further, according to the present invention, in the heat exchanger in which the heat exchanging plates for exchanging heat via the fluid flowing through the internal flow passage having the circular cross section are arranged opposite to each other on the upper and lower surfaces of the thermoelectric module. In the flow path of the plate, an annular separation / secondary flow inducing member for inducing a secondary flow is provided to be inclined with respect to the tube axis of the flow path, and particularly, on the side of the heat exchange plate that is in contact with the thermoelectric module. The flow path surface is the bottom surface (bottom side), and the separation / secondary flow inducing member is arranged with the bottom surface (bottom side) as the base point and is inclined rearward with respect to the flow direction of the fluid. In the cooling and heating of the thermoelectric module attached to the (side), heat transfer can be remarkably promoted.

Further, since the heat transfer performance is promoted in this way, the heat exchanger can be made smaller and have higher performance.

[Brief description of drawings]

FIG. 1 is a diagram showing a schematic configuration of a circular pipe through which a fluid to be cooled or heated used in a heat exchanger according to the present invention is passed.

FIG. 2 is a diagram showing a heat transfer experiment using the circular tube shown in FIG. 1 for grasping an effect of promoting heat transfer performance due to a difference in inclination angle of ribs.

FIG. 3 is a diagram showing a heat transfer experiment result at Reynolds number (Re) = 10000 and θ = 45 ° according to the mode of the heat transfer experiment shown in FIG. 2;

FIG. 4 is a diagram showing an average Nusselt number ratio Num / Nu∞ distribution at each position in the circumferential direction at z / d = 7 to 9 (between about 3 ribs).

FIG. 5 is a top view of the heat exchange unit according to the present invention.

6 is a right side view of the heat exchange unit in FIG.

7 is a sectional view taken along the line AA of FIG.

8 is a sectional view taken along line BB of FIG.

FIG. 9 is a diagram showing application of ribs to the flow paths of the water cooling plate of the heat exchange unit according to the present invention.

10 is a perspective perspective view useful for three-dimensionally grasping rib portions continuously arranged at regular intervals in a straight flow passage in the flow passage of the water cooling plate shown in FIG.

FIG. 11 is a diagram showing an example in which the arrangement shapes of the flow paths in FIG. 9 are different.

FIG. 12 is a view showing another heat exchanger not using the thermoelectric element module.

FIG. 13 is a diagram showing a conventional measure (acceleration method) for promoting heat transfer of a flow in a flow path.

[Explanation of symbols]

100 heat exchange unit 110, 110B, 110C, 110D heat exchanger 110-1, 110-2 material substrate 110a heat exchanger (water cooling plate) 110b heat exchanger (heat exchange plate) 105, 105a, 105b cover plate 111a, 112a , 113a, 114a, 115a,
116a, 117a, 118a, 119a Screw holes 111b, 112b, 113b, 114b, 115b,
116b, 117b, 118b, 119b Bolt through holes 121a, 121b Fluid inlet 122a, 122b Fluid outlet 125 Flow passage 125a Facility water flow passage 125b Circulating water flow passage 1251 Partition plate 1252 Slit 131, 132 Electrode rod 50 Thermo module 501a, 501b Bonding plate 501L Lead electrode bonding plates 502, 503 Thermoelectric element 505 Thermoelectric element array area 60, 61 O-ring

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) H01L 35/32 H01L 35/32 A (72) Inventor Mochizuki Sadanari 4-23-6 Shimochiai, Shinjuku-ku, Tokyo

Claims (7)

[Claims] 1. A heat exchanger for exchanging heat via a fluid flowing through a flow path inside a circular pipe, wherein an elliptical annular separation / secondary flow inducing member is provided in the circular pipe with respect to a pipe axis of the circular pipe. A heat exchanger characterized by being installed with a tilt. 2. A heat exchanger in which heat exchange plates for exchanging heat via a fluid having a circular cross section are arranged on both upper and lower surfaces of a thermoelectric module so as to face each other. A heat exchanger, characterized in that an elliptical annular separation / secondary flow inducing member is provided therein with being inclined with respect to the pipe axis of the flow path. 3. A plurality of the separation / secondary flow inducing members are continuously arranged in a straight line portion of the flow path at regular intervals in a pipe axis direction.
The heat exchanger according to any one of 1. 4. The heat exchanger according to claim 3, wherein the constant interval (L) has a relationship of L / d = 1 to 2 with respect to an inner diameter (d) of the flow passage. 5. The heat according to claim 1, wherein the separation / secondary flow inducing member is arranged so as to be inclined at a rear angle of 45 to 60 ° with respect to the tube axis direction. Exchanger. 6. The height (h) and the thickness (t) of the separation / secondary flow inducing member are such that h / d = 0.1 to 0.
2. The heat exchanger according to claim 1, wherein the heat exchanger has a relationship of t / d = 0.1 to 0.2. 7. The flow passage surface of the heat exchange plate on the side in contact with the thermoelectric module is used as a bottom surface, and the separation / secondary flow inducing member is inclined rearward with respect to the flow direction of the fluid with the bottom surface as a base point. The heat exchanger according to claim 2, wherein the heat exchanger is arranged as follows.