KR101579540B1 - Improved Primary Surface Heat Exchanger for Micro Gas Turbine - Google Patents

Abstract

The present invention relates to a heat exchanging plate having a wavy fin structure in which unevenness is formed on a plane forming a primary surface of a heat exchanger and is formed by unevenness of the heat exchanging path, And a heat exchanger using the heat exchanger, wherein the heat exchange efficiency is improved by regulating the unbalance of the flow rate distribution caused by conduction in the stiffener and the weld cap, and a heat exchanger using the heat exchanger. To this end, a main body made of a sheet metal sheet; An inflow portion through which the first fluid flows into the body; Wherein the first fluid has a concavity and convexity extending in a plane on the main surface, the first fluid passing through the concave portion of the concavo-convex portion; A discharge portion through which the first fluid is discharged from the main body; A first flow path configured to discharge the first fluid from the inflow portion to the discharge portion via the main heat conduction surface; And a first distribution plate having a plurality of concavities and convexities to distribute the flow rate of the first fluid to the main heat transfer surface, wherein a channel having a relatively large flow rate of the first fluid is smaller than a channel having a relatively small flow rate of the first fluid, Sectional area of the heat exchange plate is narrow. According to this, there is an effect of improving the heat exchange efficiency of the heat exchanger by controlling the flow rate of the short portion of the heat exchange path.

Description

TECHNICAL FIELD [0001] The present invention relates to a heat exchange plate having a main heat transfer surface for a micro gas turbine having improved heat exchange efficiency, and a heat exchanger using the same,

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a heat exchanger having a main heat transfer surface for a micro gas turbine having improved heat exchange efficiency, and more particularly to a heat exchanger having a heat transfer surface, wavy fin structure, it is possible to control the unbalance of the flow distribution caused by the structural problem due to the asymmetry of the heat exchange path and to control the heat loss caused by the conduction in the stiffener and the weld cap to improve the heat exchange efficiency A heat exchange plate, and a heat exchanger using the same.

Heat exchangers are used in various fields as a device for heat exchange between a low-temperature fluid and a high-temperature fluid. For example, as a heater, a preheater, a superheater, a reheater, a cooler, a condenser and an evaporator in a chemical industry such as a power plant, a gas turbine, a heating device, an air conditioner, a refrigerating device and a catalytic reactor.

Such a heat exchanger can be divided into a bulkhead type and a regenerative type according to a heat exchange type. In a bulkhead type heat exchanger, a fluid having a temperature different from each other flows in a space separated by a wall, and heat conduction through the wall and fluid convection at the wall surface It is a type of heat exchanger in which heat exchange takes place. Such a bulkhead heat exchanger may be classified into a tubular type, a finned tube type, and a plate fin type. The present invention relates to a heat exchange plate having a waybifbin structure used in a bulkhead heat exchanger.

1 is a plan view showing a heat exchange plate having a weibifin structure. As shown in Fig. 1, the heat exchange plate can be formed by press-working both sides of a metal sheet provided with concavities and convexities whose corrugations extend in a plane. This is a configuration for generating convection of the fluid and improving the contact area and contact time. When the low-temperature fluid flows from one side of the main heating surface, the heat is transferred from the main heating surface to the other side.

At this time, as shown in Fig. 1, there arises a problem of a flow rate imbalance in which heat exchange is relatively insufficient at a short portion of the flow path in the heat exchange plate due to a structural problem arising from asymmetry of the heat exchange path. In addition, according to the structure of the conventional heat exchange plate, energy loss due to heat conduction is significant in the upper stiffener forming the frame on the main heat transfer surface and the lower weld cap.

Accordingly, there is a need for a heat exchanger and a heat exchanger to regulate the flow rate through relatively insufficient heat exchange, maximize the heat exchange efficiency by regulating energy loss through heat conduction in the stiffener and the weld cap.

In particular, it is difficult to use conventional heat exchangers in power generation systems such as micro gas turbines, solid oxide fuel cells, next-generation reactors, waste heat recovery systems, and gas plants. Due to the microchannel design, the size of heat exchangers is reduced to 1/6 Compact heat exchangers have been utilized. Therefore, in the compact heat exchanger, the heat exchange efficiency becomes an important factor, and it is required to solve the energy loss that flows out due to the flow rate unbalance and the heat conduction.

Patent No. 10-0918607 Patent No. 10-1177359 Registration Practice 20-0324980

Accordingly, the present invention has been made to solve the above-described problems.

It is an object of the present invention to provide a heat exchange plate having a wavy fin structure in which unevenness is formed on a plane forming a primary surface of a heat exchanger, And a heat exchanger using the heat exchanger, wherein the heat exchange efficiency is improved by regulating the unbalance of the flow distribution caused by the conduction and the heat loss generated by the conduction in the stiffener and the weld cap.

Hereinafter, specific means for achieving the object of the present invention will be described.

A first object of the present invention is to provide a heat exchange plate in which a plurality of heat exchangers are used, a first fluid flows on one surface, and a second fluid flows on the other surface, thereby exchanging thermal energy between the first fluid and the second fluid, A body made of a sheet metal sheet; A first inlet (one side of the position where the reference numeral 3 is inserted in FIG. 2, refer to A direction in FIG. 7) provided at one side of the main body and into which the first fluid flows; A main heat conducting surface (10) provided at an end of the main body and having a concave / convex portion extending in a wave form on a plane, the first fluid flowing through the concave portion of the concave / convex portion; A first discharging portion provided on the other side of the main body and discharging the first fluid from the main body (refer to the other side of the position where the reference numeral 3 is inserted in Fig. 2, see A direction in Fig. 7); And a first distribution plate inserted in at least one of the first inlet and the first outlet and having a plurality of concavities and convexities to distribute the flow rate of the first fluid to the main surface, The concavo-convex part of the distribution plate includes a plurality of channels (referred to as a channel, for example, the first distribution plate is constituted by a plurality of channels having different cross-sectional areas at 3 in Fig. 2) The channel is configured such that at least one of height and spacing of the irregularities is made different from each other, and a channel having a relatively large flow rate of the first fluid is configured to have a narrow cross-sectional area of the channel than a channel having a relatively small flow rate of the first fluid And a heat exchange plate made of the same material.

A second inlet formed at one side of the main body of the main body and through which the second fluid flows into the main body (refer to one side of the position where the reference numeral 5 is inserted in FIG. 2, the direction B in FIG. 7); A second discharging portion formed on the other side of the main body at the other side of the main body to discharge the second fluid from the main body (the other side of the position where the reference numeral 5 is inserted in Fig. 2, see the direction B in Fig. 7); And a second distribution plate inserted in at least one of the first inlet, the second inlet and the second outlet and having a plurality of concavities and convexities to distribute the flow rate of the second fluid to the main surface, The concavo-convex portion of the concavo-convex structure includes a plurality of channels (for example, refer to that the distribution plate is constituted by two channels having different cross-sectional areas at 5 in Fig. 2) And a channel having a relatively large flow rate of the second fluid is configured to have a narrow cross-sectional area of the flow channel than a channel having a relatively small flow rate of the second fluid.

The main heat transfer surface may have a cross sectional area of at least a part of the flow path including the shortest distance between the first inflow part and the first discharge part being relatively narrower than the remaining cross sectional area.

In order to reduce the cross-sectional area of the flow passage, the first and second discharge ports are formed on the upper and the other side of the first and second discharge ports, respectively, And a diagonal crimping portion which is pressed by the crimping portion.

Further comprising a bar stiffener configured to surround one end of the body to form a frame of the main body, wherein at least one groove for reducing the cross sectional area is formed at the stop of the stiffener, And at least one cut portion is formed in the transverse direction at the stop.

And a bar-shaped weld cap configured to surround one end of the body to prevent damage to the weld due to friction with the case of the heat exchanger, wherein the weld cap reduces the cross- And at least one cut-out portion is formed in the transverse direction at the end of the weld cap.

A second object of the present invention is to provide a heat exchanger comprising: a heat exchanger body configured to have a plurality of heat exchange plates according to the first aspect therein for exchanging heat between a first fluid and a second fluid; A first inlet configured to allow the first fluid to flow from the outside into the heat exchanger body; A first discharge unit configured to discharge the first fluid to the outside from the heat exchanger main body; A second inlet configured to allow the second fluid to flow from the outside into the heat exchanger body; And a second discharge unit configured to discharge the second fluid to the outside from the main body of the heat exchanger, wherein the first fluid and the second fluid are heat-exchanged through the main heat- And a heat exchanger is provided.

As described above, the present invention has the following effects.

First, according to the present invention, there is an effect that the heat exchange efficiency of the heat exchanger is improved by controlling the unbalance of the flow rate distribution caused by the structural problem resulting from the asymmetry of the heat exchange path.

Secondly, according to the present invention, energy loss due to heat conduction generated in the stiffener and the weld cap is controlled to improve the heat exchange efficiency of the heat exchanger.

BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate preferred embodiments of the invention and, together with the description, And shall not be interpreted.
BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a plan view showing a heat-
2 is a plan view showing a heat exchange plate according to a first embodiment of the present invention,
FIG. 3 is an enlarged view of a stiffener and an oblique crimping portion according to an embodiment of the present invention,
FIG. 4 is an enlarged view showing a rectangular compression bonding unit according to an embodiment of the present invention,
5 is a graph of flow rates of a first fluid and a second fluid according to an embodiment of the present invention,
6 is a plan view showing a heat exchange plate according to a second embodiment of the present invention,
7 is a perspective view illustrating a heat exchange plate bundle according to an embodiment of the present invention,
FIG. 8 is a perspective view illustrating a heat exchange plate assembly constructed in a heat exchanger according to an embodiment of the present invention. FIG.
9 is a schematic diagram showing a test example using a heat exchange plate according to the prior art,
10 is a sectional view showing a first distribution plate according to a first test example of the present invention,
11 is a schematic diagram showing a heat exchange plate used in a second test example of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the following detailed description of the operation principle of the preferred embodiment of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may unnecessarily obscure the subject matter of the present invention.

The same reference numerals are used for portions having similar functions and functions throughout the drawings. Throughout the specification, when a part is connected to another part, it includes not only a case where it is directly connected but also a case where the other part is indirectly connected with another part in between. In addition, the inclusion of an element does not exclude other elements, but may include other elements, unless specifically stated otherwise.

< Heat exchange plate >

FIG. 2 is a plan view of a heat exchange plate according to a first embodiment of the present invention, FIG. 3 is a cross-sectional view of a heat exchanging plate according to an embodiment of the present invention, FIG. 4 is an enlarged view showing a rectangular compression bonding unit according to an embodiment of the present invention. FIG. As shown in FIGS. 2, 3 and 4, the heat exchange plate 1 according to the first embodiment of the present invention can be formed of a metal sheet having an inverted trapezoidal shape, and fluid is introduced and discharged on a wide trapezoidal surface . That is, like the heat exchange plate shown in FIG. 1, a fluid inflow portion is provided at the left upper end and a fluid discharge portion is provided at the right upper end. Which may vary depending on the configuration of the heat exchanger or the heat exchange plate.

The heat exchanging plate 1 according to the first embodiment of the present invention includes a first distributing plate 3, a second distributing plate 5, a main heating surface 10, a stiffener 12, a weld cap 14, (16), an oblique crimping portion (20), and a groove (22).

A plurality of heat exchange plates 1 according to the first embodiment of the present invention can be used by being laminated. In this heat exchange plate 1, two flow paths may be formed, which are referred to as a first flow path and a second flow path. The first flow path is a path passing through the interior of the heat exchange plate (1). The first flow path is a path through which the fluid flows from the upper end of one side of the heat exchange plate 1 to the upper end side of the other side of the heat exchange plate 1. The second flow path is a path through which the heat exchange plate 1 and the other heat exchange plate 1 . A first fluid (Recipient) that receives thermal energy flows through the first flow path, and a second fluid (Donor) that provides thermal energy flows through the second flow path.

The first distribution plate 3 has a plurality of irregularities or fins for distributing the first fluid to the main heating surface 10 in relation to the first flow path, . According to the embodiment of the present invention, the width and the interval of the fin are relatively narrow in the portion where the heat exchange channel is relatively short in the first distribution plate 3, The width and spacing of the pins can be made wide. The width and spacing of the pins may be configured to be gradually widened or narrowed, or may be formed of a plurality of pin groups having different widths and spacings. However, due to various problems such as manufacturing complexity and manufacturing cost, It is preferable to constitute a group of two pins having an interval.

The second distribution plate 5 has a plurality of fins for distributing the second fluid between the heat exchange plates 1 in relation to the second flow path, and is configured in the form of a right triangle. The largest amount of the second fluid flows to the short edge of the heat exchange plate 1 in the trapezoidal shape of the heat exchanger and the smallest amount of the second fluid flows to the long edge of the heat exchange plate 1. [ According to an embodiment of the present invention, the second distribution plate 5 has a structure in which the width and the interval of the fin corresponding to the short edges of the heat exchange plate 1 are narrow and the long edge of the heat exchange plate 1 The width and spacing of the pins can be made wide. The width and spacing of the pins may be configured to be gradually widened or narrowed, or may be formed of a plurality of pin groups having different widths and spacings. However, due to various problems such as manufacturing complexity and manufacturing cost, It is preferable to constitute a group of two pins having an interval.

5 is a graph of the flow rates of a first fluid and a second fluid in accordance with an embodiment of the present invention. As shown in FIG. 5, the second fluid is excessively supplied to the first fluid where a small amount of heat energy is required, and the second fluid is excessively supplied to the first fluid when a large amount of heat energy is required Can be confirmed. Due to the disparity in flow distribution of the low-temperature side channel, the temperature deviation due to the position of the low-temperature side outlet was considerably large, which resulted in lowering the overall usefulness of the heat exchanger.

The present invention aims to solve this problem by adjusting the physical flow distribution. In one embodiment of the present invention, a method of changing the flow rate on the high-temperature side or changing the flow rate on the low-temperature side in order to control the temperature deviation is proposed. As shown in FIG. 5, according to the embodiment of the present invention, the flow rate is appropriately distributed, which has the effect of increasing the usability on the low temperature side.

The main heating surface 10 may be configured to have a concave-convex portion extending in a wave form on a plane. The fluid flowing from one side of the heat exchange plate 1 passes through the concave portion of the irregular portion of the main heat transfer surface 10 to perform heat exchange. The concavo-convex portion is extended in a waveform to increase the flow path through which the fluid passes.

The stiffener 12 is configured to form a frame on the main heat-conducting surface, and may be formed in a bar shape so as to surround one side of the heat-exchange plate 1. [ The stiffeners 12 of the respective heat exchange plates 1 are provided so as to face the center of the heat exchanger.

The weld cap 14 is configured to prevent the welded portion from being damaged at a portion where the case of the heat exchanger and the heat exchange plate 1 are rubbed. The weld cap 14 may be formed in a bar shape to surround one side of the heat exchange plate 1.

The pressing portion 16 presses both sides of the main heating surface 10 so that the fluid can be uniformly distributed to the main heating surface 10. That is, first, a metal sheet having a concave-convex portion extending in a plane on a plane is manufactured, and then the heat exchange plate 1 is manufactured by pressing both sides of the metal sheet to separate the pressed portion 16 and the main heat- .

The diagonal crimping portion 20 may be formed on at least one side of the main heat conductive surface 10 constituting the shortest distance between the inflow portion and the discharge portion. This is configured to reduce the cross-sectional area of the flow path constituting the shortest distance between the inflow portion and the discharge portion, or to close the flow path. Equation (1) below is a formula concerning the flow rate.

In the equation (1), Q is the flow rate (m ³ / hr), A is the cross-sectional area (m ² ), and V is the flow rate (m / hr). As shown in equations (1) and (4), the cross-sectional area of the flow path is reduced when the nozzle is compressed by a diagonal line, thereby reducing the flow rate.

The sectional area of the flow path may be reduced by a method other than the method of constructing the oblique crimping portion 20. [ However, in the case of forming the oblique crimping portion 20, the crimping portion 16 can be constructed simply, the cross-sectional area is appropriately reduced, and the process time is not much added. There is an effect that is possible.

The cross-sectional area of the flow path constituting the shortest distance between the inlet portion and the outlet portion is reduced by the oblique crimping portion 20. As shown in Fig. 1, the heat exchanging is relatively less in the flow path constituting the shortest distance between the inflow portion and the discharge portion. Therefore, the diagonal compression bonding portion 20 has an effect that the flow rate is reduced for the flow path in which the heat exchange is relatively less, and the heat exchange efficiency of the heat exchanger as a whole is increased.

The grooves 22 may be applied to the stiffener 12 or the weld cap 14. At this time, the groove 22 can be applied to a size that does not interfere with the role of the stiffener 12 or the weld cap 14.

The number, shape, size, and spacing distance of the grooves 22 can be appropriately applied according to the shape, size, application temperature, etc. of the heat exchange plate 1. [

With respect to the effect of the grooves 22, the Fourier's law as shown in the following equations (2) and (3) can be applied to calculate the amount of energy transferred per unit time by thermal conduction in a specific medium. The heat transfer coefficient equation for a one-dimensional plane wall with temperature distribution T (x) is as follows.

In Equation (2), q '' _x is the heat transfer coefficient per unit area perpendicular to the x direction which is the transfer direction, k is a constant, and the heat transfer coefficient per unit area is proportional to the temperature gradient dT / dx in this direction.

The heat transfer coefficient q _x (x) through a plane wall having a vertical direction in the heat conduction direction and an area A is obtained by multiplying the heat transfer coefficient per unit area perpendicular to the direction x, which is the transfer direction, and the area,

That is, the effect of the stiffener 12 according to the first embodiment of the present invention and the groove 22 improved in the weld cap 14, as described in Equations 2 and 3, It is possible to calculate by influence.

It can be seen that the cross sectional area in the longitudinal direction is reduced to about half in the middle of the stiffener 12 or the weld cap 14 by forming the groove 22 in at least one of the stiffener 12 and the weld cap 14. [ By reducing the cross-sectional area, the effect of decreasing the heat transfer rate through the plane wall perpendicular to the heat conduction direction can be obtained by Equation (3). That is, the amount of heat energy that escapes from the stiffener 12 or the weld cap 14, which has grooves, to the heat conduction decreases, which ultimately increases the heat exchange efficiency of the heat exchanger.

6 is a plan view of a heat exchange plate according to a second embodiment of the present invention, in relation to the heat exchange plate 1 according to the second embodiment of the present invention. As shown in FIG. 6, the heat exchange plate 1 according to the second embodiment of the present invention may include a cut portion in at least one of the stiffener 12 and the weld cap 14. In FIG. 6, a cut portion is formed in the weld cap 14.

The stiffener 12 or the weld cap 14 provided with the cut-out portion is configured so as to have a predetermined separation distance from each other by cutting and dividing into a plurality of members which are conventionally constituted by one member. In the second embodiment of the present invention, the weld cap 14 is cut and divided into three members to form two cut portions.

The number, shape, size, and separation distance of the cut portions can be appropriately applied according to the shape, size, application temperature, and the like of the heat exchange plate (1).

Regarding the effect of the cut portion, since the stiffener 12 or the weld cap 14 itself is cut midway, the influence of the conduction is blocked. Therefore, in this case, only the internal flow, that is, the heat conduction coefficient due to the convection, is influenced. At this time, the coefficient of thermal conductivity due to convection is extremely low to one-tenth of the coefficient of heat conduction by conduction, so that it is possible to maximize the loss of heat energy due to conduction by a simple structure. That is, the amount of thermal energy exiting the heat conduction path in the stiffener 12 or the weld cap 14 having the cut-off portion is reduced, and the heat exchange efficiency of the heat exchanger is ultimately increased.

<Heat exchanger>

FIG. 7 is a perspective view illustrating a heat exchange plate bundle according to an embodiment of the present invention. FIG. 8 is a perspective view of a heat exchange plate formed in a heat exchanger according to an embodiment of the present invention. Fig. 7 and 8, the heat exchanger according to the embodiment of the present invention is constructed by inserting the heat exchange plate 1 according to the first and second embodiments of the present invention.

As shown in FIG. 7, a first fluid A for receiving heat is introduced and discharged from the upper portion of the heat exchange plate 1, and a second fluid A for transferring heat from the side of the heat exchange plate 1 to the first fluid And the second fluid (B) flows in and out.

As shown in FIG. 8, the heat exchange plate assembly 100 constructed inside the heat exchanger may be configured so that a plurality of heat exchange plates 1 are stacked. The stiffener 12 is provided on the inner side, and the heat exchange plate 1 is disposed such that the weld cap 14 faces outward.

< First test example >

In the first test example of the present invention, only the first distribution plate 3 was subjected to the temperature variation test. In this test, a control group was formed by using a conventional heat exchange plate. 9 is a schematic diagram of a test example using a heat exchange plate according to the prior art. As shown in FIG. 9, the temperature of the introduced first fluid A was set at 190 占 폚, and three temperature sensors were mounted at the portion where the first fluid A was discharged. The first channel is divided into three channels, the longest channel is designated as channel 1, the intermediate channel is defined as channel 2, and the shortest channel is designated as channel 3. The exit of channel 1 is designated as sensor 1, the exit of channel 2 is designated as sensor 2, and the exit of channel 3 is designated as sensor 3. The second fluid B flows through the second flow path between the heat exchange plates 1 and transfers the heat energy to the first fluid A.

number 1 No.2 number 3 Maximum temperature difference Average outlet temperature [캜] 661 580 510 151 Temperature variation relative to entrance [℃] 471 390 320 - ratio One 0.828 0.679 -

As shown in Table 1, depending on the position of the outlet of the first flow path, the temperature deviation averages to a maximum of 151 DEG C, which is a major cause of deteriorating the overall usefulness of the heat exchanger. In order to solve this problem, the present invention proposes adjustment of physical flow distribution.

Assuming that the channels of the first flow path are largely divided into three equal parts, the amount of heat provided by the second flow path is constant, and the heat loss rate of the heat exchanger is neglected, it can be expressed as follows.

_c1,_c2,_c3는 각각 1번, 2번, 3번 채널에서의 유량, C_p는 제1유체(A)의 비열, T_c1,_c2,_c3은 각각 1번, 2번, 3번 채널에서의 온도를 의미한다. In the above equation, Q _{h1 , h2 , and h3} are the amounts of heat provided in the second flow path in the first, second, and third channels, respectively,

_{c1, c2, c3} is the flow rate in one time, two times 1, 3 channels, respectively, C _p is the specific heat of the first fluid (A), T _{c1, c2, c3} are each 1, 2, 3 in the channel &Lt; / RTI &gt;

Substituting the experimental results of Table 1 into equations (4), (5) and (6) yields equation (7). In order to have the same temperature deviation in the three channels, it is possible to adjust Q _{h1 , h2 , h3} by changing the flow rate of the second flow path _, or to adjust the temperature deviation by changing the flow rate of the first flow path. Since the second flow path is very sensitive to the pressure drop, it is judged that a method of adjusting the flow rate of the first flow path having a relatively large pressure margin is more preferable.

In Equation (7), assuming that the amount of heat Q _h provided in the second flow path is the same in all the channels of the first flow path, in order to have the same temperature deviation, the flow ratio in each channel should be as follows.

Since the flow rate in the channel is determined by the total cross-sectional area corresponding to the flow path of the channel, the flow rate can be physically adjusted by dividing the channel cross-sectional area by the above ratio. That is, when the following equations are satisfied, the temperature deviation can be adjusted.

In Equation (9), A _c1 , _c2 , _c3 are the total cross-sectional areas of the channels, respectively. In this case, when the internal channels are divided into three equal parts, various problems such as manufacturing complexity and production cost increase occur. Therefore, it is preferable that the flow distribution is applied by making a bisecting about the third channel in which a large temperature deviation occurs. In configuring the first flow path with two channels, it can be configured as the following equation.

That is, the first distribution plate 3 of the first flow path can be manufactured by using two specifications of fins so as to have the total cross-sectional area of the channel having the same ratio as in Equation (10).

10 is a cross-sectional view of a first distribution plate according to a first test example of the present invention, with respect to an embodiment in which a first flow path is manufactured at a ratio close to Equation (10). As shown in FIG. 10, the temperature deviation of the first flow path outlet can be significantly reduced by fitting the total cross-sectional area of the channel including No. 1 channel, No. 2 and No. 3 to 2.68: 1.

< Example 2 >

11 is a schematic diagram showing the heat exchange plate used in the second test example of the present invention. 11, the second test example of the present invention further includes a first distribution plate 3, a second distribution plate 5, and an obliquely pressed portion 20 unlike the first test example, And the groove 12 is formed in the groove 22 and the groove is formed in the weld cap 14 to adjust the temperature deviation. The first fluid A flows through the first flow path while receiving the thermal energy and the second fluid B flows through the second flow path between the heat exchange plates 1, ).

number 1 No.2 number 3 Maximum temperature difference Average outlet temperature [캜]
(The second fluid has a temperature of 500 DEG C,
Atmospheric pressure condition)
473.85
469.65
458.8
15.05 Average outlet temperature [캜]
(The second fluid is at 680 DEG C,
Atmospheric pressure condition)
666.2
649.55
631.65
34.55 Average outlet temperature [캜]
(The second fluid is at 680 DEG C,
2 bar condition)
654.35
647.85
638.9
15.45

As shown in Table 3, it can be confirmed that the temperature deviation is remarkably alleviated when the second distribution plate and the groove are formed. In addition, an improvement in effectiveness can be confirmed by the following equation.

In Equation (11),? Is the usefulness, q is the actual heat transfer coefficient, and _qmax is the maximum possible heat transfer coefficient. Based on Equation (11), it can be seen that the usefulness of the second flow path, which was only about 85%, is improved by 90% or more as a whole.

In order to use the heat exchanger in a micro gas turbine or the like, the heat exchanger must be made compact, and if the heat exchanger is made compact, the heat transfer area is reduced, and the heat transfer rate is lowered. Therefore, according to the embodiment of the present invention, it is possible to remarkably prevent the lowering of the heat transfer rate, and thus the production of the compact heat exchanger is remarkably advantageous.

As described above, those skilled in the art will appreciate that the present invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. It is therefore to be understood that the above-described embodiments are to be considered in all respects only as illustrative and not restrictive. The scope of the present invention is defined by the appended claims rather than the detailed description, and all changes or modifications derived from the meaning and scope of the claims and their equivalents should be construed as being included in the scope of the present invention.

1: Heat exchange plate
3: First distribution plate
5: Second distribution plate
10: Main Opening
12: Stiffener
14: Weld cap
16:
20:
22: Home
100: Heat exchange plate assembly
A: First fluid
B: Second fluid

Claims (7)

Wherein a plurality of heat exchangers are used, a first fluid flows on one surface and a second fluid flows on the other surface, and heat energy of the first fluid and the second fluid is exchanged,
A body made of a sheet metal sheet;
A first inflow part formed at one side of the main body and through which the first fluid flows into the main body;
A main heating surface which is formed at an end of the main body and has recesses and protrusions extending in a planar wave form on at least one surface of the main body and in which the inflowed first fluid is allowed to pass through the recessed and protruded portions from one surface of the main body;
A first discharging portion formed on the other side of the main body to discharge the first fluid from the main body; And
A first distribution plate inserted into at least one of the inflow portion and the discharge portion and having a plurality of concavities and convexities to distribute the flow rate of the first fluid to the main heat transfer surface;
/ RTI &gt;
The concavo-convex portion of the first distribution plate is composed of a plurality of channels,
Wherein the plurality of channels of the first distribution plate are configured such that at least one of a height and an interval of the concavities and convexities is different from each other and a channel having a larger flow rate of the first fluid is smaller than a cross- Narrowly configured,
Wherein the main-
Sectional area of a flow path for a specific path of the first fluid which forms part of the entire path of the first fluid and includes the shortest distance between the first inflow part and the first discharge part, Sectional area of the heat exchanger plate.
The method according to claim 1,
A second inflow portion formed at one side of the main body to receive a second fluid into the main body;
A second discharge part formed on the other side of the main body to discharge the second fluid from the main body; And
A second distribution plate inserted into at least one of the second inlet and the second outlet and having a plurality of concavities and convexities to distribute the flow rate of the second fluid to the other surface of the body;
Further comprising:
The concavo-convex part of the second distribution plate includes a plurality of channels,
Wherein the plurality of channels of the second distribution plate are configured such that at least one of the height and the interval of the irregularities is different from each other and the channel having a larger flow rate of the second fluid has a cross- And the heat exchange plate is made narrow.
delete The method according to claim 1,
Wherein the main heating surface is formed in a rectangular shape on a plane,
Wherein the first inlet portion and the first outlet portion are provided on one upper side and the other upper side, respectively,
Wherein the upper edge of the main heat-conducting surface includes a diagonal compression bonding portion that is pressed in an oblique direction to reduce a cross-sectional area of the flow passage.
The method according to claim 1,
A bar stiffener configured to surround one end of the main body to form a frame of the main body;
Further comprising:
Characterized in that at least one groove for reducing the cross sectional area is formed at the stop of the stiffener or at least one cut section is formed in the transverse direction at the stop of the stiffener.
The method according to claim 1,
A bar-shaped weld cap configured to surround one end of the main body to prevent damage to the welded portion due to friction with the case of the heat exchanger;
Further comprising:
Characterized in that at least one groove for reducing the cross sectional area is formed at the end of the weld cap or at least one cut is formed in the cross direction at the end of the weld cap.
delete

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