JPH045920B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a plate and fin heat exchanger, and more particularly to a single face open plate for a plate and fin heat exchanger using countercurrent or cocurrent flow. It is.

Plate-fin heat exchangers primarily have a channel-rib configuration. Although countercurrent flow can be achieved in this case, it is extremely difficult to provide a manifolded configuration of the plate stack where the fluid must be separated at the inlet and outlet. The manifold configuration of cross-flow heat exchangers is relatively simple and therefore more widely used despite being less efficient and generating different thermal and mechanical stresses than counter-flow systems. has been done.

U.S. Patent No. 3305010 (Campbell et al)
One countercurrent system is disclosed that attempts to solve the problems of manifold configurations of countercurrent heat exchangers. The heat exchanger disclosed in this patent has stacked plate and fin elements and complex manifold means for introducing fluids at different temperatures from both ends. However, the Campbell patent does not disclose a plate having the functions of both a plate and a fin, nor does it disclose a means for internally manifolding the plate in the plane of the plate. .

An alternative countercurrent system is shown in Figure 1, which was taken from the Proceedings of the Fifth OTEC Conference, February 1978, in Miami, Florida.
Alfa-Laval, described on pages 288-320. The Alfa-Laval concept consists primarily of a set of thin metal plates, a frame and means for holding the parts together. These plates are held between the upper and lower parts of the horizontal support rods and are pressed against the fixed frame plate by anchor bolts and a movable pressure plate. The frame plate is provided with nozzles to the inlet and outlet connections. Each plate is sealed around its periphery with a gasket and secured in a press-formed groove. The flow openings in each corner of the plates are individually gasketed, thus dividing the space between the plates into two systems of alternating flow channels. Via these channel systems, two media are passed, the hot one supplying heat to the cold one by heat conduction through the thin plates. By providing such a gasket, the risk of mutual leakage between media is eliminated. The basic element of this Alfa-Laval concept is the plate, which has a corrugated pattern formed by press molding. These corrugations can be configured into a myriad of plate pattern shapes. However, the particular pattern is determined by careful break-even considerations between pressure drop and convective heat transfer characteristics.

The gasket in the Alfa-Laval system is secured to a press-formed groove in the plate and is typically constructed of an elastomer such as natural rubber, nitrile, butyl, neoprene, Viton, etc. The choice of material for the gasket in this case depends on the conditions of use, but the upper limit is about 360 psi and about 400°F.

The present invention differs significantly from Alfa-Laval's as described above, to name a few examples: (1) Alfa-Laval requires a gasket, which limits operating pressures and temperatures; (2) Since contact fins are not provided in the Alfa-Laval system and the plate bottoms are basically not flat, it is difficult to obtain the contact between the plates necessary to obtain the optimum heat transfer coefficient. I can't do it (3)
Since the inlet and outlet sections of the Alfa-Laval system are located at opposite ends but on the same side of the plate, the flow distribution across the plate is poor and the heat transfer efficiency is poor. (4)Alfa
- In the Laval system, no means are provided to drive the flow across the face of the plate, so it is not possible to compensate for its inherent inefficiency. Furthermore, the above-mentioned prior art
There is no suggestion whatsoever of the annular plate structures and plate segments of the present invention.

The present invention has been made in view of the above points, and an object of the present invention is to provide a single face-open fin plate having an internal manifold structure for use in a plate-fin type heat exchanger. A unitary open-faced fin plate having an internal manifold configuration has a side opening adjacent an internal manifold means, the manifold means being disposed transversely to the plurality of channels. and each channel is adjacent to an end port. It is possible to alternately stack a plurality of face-open single fin plates internally having a manifold structure so as to face each other. This internally manifolded stack of plates can be combined with an external manifold to form an efficient, low cost countercurrent heat exchanger. Another embodiment of an open-face unitary plate with an internal manifold configuration has an integral auxiliary inlet manifold and an outlet manifold, such that a separate external manifold can be used. This eliminates the need for having an old.

An object of the present invention is to provide a fin plate with a manifold structure inside for use in a plate-fin heat exchanger.
Another object of the present invention is to provide a single fin plate with a manifold structure inside for use in a plate-fin heat exchanger. A further object of the present invention is to
An object of the present invention is to provide a plate for a heat exchanger that can be manufactured from a single mold. Yet another object of the present invention is to provide a highly efficient countercurrent or cocurrent plate and fin heat exchanger. A further object of the present invention is to achieve high efficiency by providing an external or auxiliary manifold for supplying fluid to the internal manifold, which is particularly designed to increase the length of the fluid flow path. It is. It is a further object of the present invention to create a low cost assembly by simply reversing the plates and gluing (diffusion bonding, brazing, welding, etc.) or bolting together a similar set of plates. The goal is to provide the following. Another object of the present invention is to provide an open-faced fin plate incorporating a plurality of fin shapes capable of improving heat transfer by increasing contact and surface area between the plates. That's true. Another object of the invention is to provide a heat exchanger with a simplified auxiliary manifold. It is a further object of the present invention to provide a simple manifold means for a plate stack having an internal manifold configuration. Yet another object of the present invention is to provide a countercurrent or cocurrent heat exchanger that is inexpensive and efficient. Yet another object of the invention is to provide a heat exchanger having plates that are relatively free from mechanical and thermal stresses.
Yet another object of the present invention is to provide a heat exchanger that can be manufactured at low cost.

Hereinafter, specific embodiments of the present invention will be described in detail with reference to the accompanying drawings. Based on the present invention, a fin plate with a manifold configuration (various configurations) is provided for use in a plate/fin type heat exchanger. Although the plate 10 is preferably constructed as a single unit, it is also possible to combine a plurality of components into a single plate. As shown in FIGS. 2a, 2b and 2c, the basic unitary fin plate 10 has an open surface 12 and a side opening 14 disposed transversely through the upper end 17 of the fin plate 10. , 14. The side openings 14, 14 are integral with, adjacent to, and connected by the internal manifold means 16. Closed end 1
8 is adjacent to and lateral to the rear end of the internal manifold means 16. Finn 2
A channel 20 formed by 2 extends adjacent to and transversely to the forward end of manifold means 16 and directs fluid flow toward end opening 24 . The bottom 26 provides a heat transfer surface for connecting the fins 22 of adjacent plates and provides a means for fluid separation and for sealingly connecting the fin plates 10 in a plate stack. It should be noted that this plate stack can be used for high and low pressure conditions, and internal leakage channels are less important. The plate cover 15 can be a solid object as shown, or it can simply be another basic fin plate 10. Furthermore, although FIG. 2b shows manifold fins 28, these fins can be provided as desired. However, these manifold fins 28 increase the support of the plate and provide additional means for heat transfer.

FIG. 2d shows a plate stack 30 with a manifold structure inside, which is composed of a plurality of fin plates 10 each having a manifold structure inside. In a preferred embodiment, the fin plates are alternately stacked facing each other. It should be noted with respect to each embodiment that although the fins 22 are shown aligned on a vertical line, they may also be arranged in a staggered manner as shown in FIG. 7b. Also, although in the preferred embodiment the finplates are identical, it is possible to vary the internal configuration of alternate finplates to obtain the desired thermodynamic effect. In a preferred embodiment, the first fluid is fed into the internal manifold 16 through side openings 14 in alternating fin plates and along a channel 20 formed by the fins 22. , end opening 24
drain through. A second fluid, either hotter or colder than the first fluid, is similarly introduced through the side openings 14 of the next fin plate to form a countercurrent flow. Although this method of flow is preferred, it is also within the scope of the invention to reverse this flow, i.e., to have the fluid enter through the end opening 24 and exit the channel 20. It is also possible to flow into the internal manifold 16 and exit through the side openings 14. Cocurrent flow can also be achieved by introducing one fluid through the side openings 14 and the other fluid through the end openings 24 of adjacent fin plates. It should be noted that the first fluid and the second fluid may be the same or different, and more than one fluid may be used depending on thermodynamic conditions.

Figures 3a and 3b show two alternative embodiments of the internal manifold means 16. This manifold means 16 may have a tapered shape determined by an angle 33. As shown in FIG. 3a, the internal manifold 16 has two side openings 14, 14 with a taper that narrows as the fluid reaches an intermediate point 32.
A barrier 34 can be inserted at the intermediate point 32, if desired. In the embodiment shown in Figure 3b, the internal manifold 16 has one side opening 14 with a taper extending across the entire width of the fin plate, which 23
It gets narrower as you reach . Although three internal manifold configurations are shown herein, other internal manifold configurations capable of delivering fluid to the channels 20 from the side openings 14 are possible.

Figures 4a, 4b and 4c show the fin 2
2 and various shapes for the channel 20 are shown. In FIG. 4a, the fins 22 and channels 20 are randomly disposed within the main channels 20 of the basic fin plate 10. In FIG. In comparison, the fin shapes in Figures 4b and 4c exhibit aligned and intermittent fin shapes. The intermittent rows of fins can also be arranged alternately as shown in Figure 4b, or as shown in Figure 4c.
It is also possible to arrange them in a line as shown in the figure. The surface of the channel can be smooth or rough depending on the specific design requirements. Also, whatever fin shape is used, the fins and channels are constructed to improve structural integrity and to improve overall heat transfer characteristics. Additionally, the channel can be tapered both in depth and width.

FIG. 5 shows the shapes of a plurality of channels and fins. The most common channel and fin shapes are those shown with channel 20 and fins 22. However, the channel 36 with rounded corners, the U-shaped channel 38, the V
Of course, different shaped channels such as a letter-shaped channel 40, a trapezoidal channel 42, etc., and corresponding fin shapes can be used. An important feature of the invention is that although the channel and fins work together to improve heat transfer properties and structural integrity, the channel itself is open-faced and therefore easier to manufacture. It's easy. Additionally, it should be noted that the channels themselves may have smooth or rough surfaces, and may also include corrugations or other surface shapes capable of improving flow conditions and heat transfer properties. It is also possible to use

FIG. 6a shows a plan view of an open-faced fin plate 62 which is internally and supplementally manifolded. The fin plate 62 is essentially the same as the fin plate 10, but the fin plate 62 also has a closed end external manifold 6.
4, an open-ended external manifold 66, and two pairs of side manifolds 68,70.
Each pair of side manifolds has a side inlet manifold 68 and a diagonally positioned side closure manifold 70. All of the external manifolds are integral and adjacent to the fin plate 10. Although the external manifold is shown as having a rectangular shape, it will be appreciated that any shape capable of delivering fluid to and from the fin plates can be used.

FIG. 6b shows a plan view of an open-faced fin plate 63 which internally and internally constitutes a manifold. The plate 63 is basically the same as the fin plate 62, but the fin plate 63 further includes a closed end auxiliary manifold 64.
, an open-end auxiliary manifold 66 , two pairs of inner side manifolds 68 and 70 , and a pair of inner inlet portions 65 . Each pair of inner side manifolds includes a side inlet manifold 68;
Diagonally located side closure manifold 7
0.

FIG. 6c is a perspective view of another embodiment of a fin plate having a manifold formed therein, generally indicated at 67. The fin plate 67 is basically the same as the fin plate 63, but
The fin plate 67 has respective inner inlet portions 69 and a pair of inner corner manifolds, each pair including an inner corner inlet manifold 71 located at the inner corner inlet portion 69 and an inlet manifold 71. and an inner corner outlet manifold 73 located on the same side but at the opposite end of plate 67.
As heat exchange fluid enters fin plate 67, it flows through open manifold 71 and inlet 69, and then through internal flow guide 75.
, through the channel 77 formed by the fins 79 and through the open end opening 81 and out through the inner corner outlet manifold 73 . It should be noted that the flow guide 75 is similar to the manifold fin 28 and is of identical construction except that the length of the manifold increases and the width of the manifold channel 83 increases. and thermodynamic objectives. With such a configuration, it is possible to provide an optimal flow distribution over the entire surface of the plate 67.

Another configuration of the flow guide 75 that can provide an optimal flow distribution over the entire surface of the fin plate 67 is to connect the flow guide 75 integrally with the fins 79 as shown in FIG. A flow guide 75 configured to supply fluid to channel 77 is used. In the case of a set of flow guides shown in FIG. 6c, flow guide 7
The spacing 83 between the fins 79 and the channels 7
It increases with increasing length to 7. A pair of tab manifolds 85 and 87 are provided, one at each of the remaining two corners of fin plate 67. Tab manifolds 85 and 87 provide the necessary continuous flow path for fin plates 67 when the fin plates are stacked opposite each other in alternating fashion.

Figures 7a and 7b, 8a, 8b and 8c show an assembly 72 of stacked fin plates and plates with internal manifold configurations. In a preferred embodiment,
Stack the fin plates alternately facing each other.
The first fluid is delivered to the inlet side manifold 68 where the fluid passes through the side opening 14 and through the internal manifold means 16 to the fin 22.
The vehicle is then redirected to pass through a channel 20 formed by This first fluid then flows out of the end opening 24 and into the open end auxiliary manifold 6.
It flows into 6. The first fluid exiting the auxiliary manifold 66 is then delivered to any suitable location. A second fluid, either hotter or colder than the first fluid, is delivered to adjacent fin plates through respective side inlet manifolds 68. Similar to the flow of the first fluid, the second fluid is then flowed through the inlet opening 14 into the internal manifold 16 and then along the channels 20 and fins 22. From there, the second fluid exits into respective open-ended auxiliary manifolds 66, from where it is delivered to the appropriate location. Open end auxiliary manifold 64 and side closed end manifold 70 are used to form a continuous secondary manifold between alternating fin plates. Things to note are:
Although the side and end manifolds are shown as having a rectangular shape, they can have any functional shape to achieve the desired effect. Further, the heat exchange fluid may be either liquid or gas, or may be a mixed fluid of liquid and gas.

FIG. 9a shows another embodiment of a face-open type fin plate having a manifold structure inside. Fin plates 74 and 76 are wedge-shaped and are joined through a sealable manifold to form annular structure 72 . It should be noted that while the most preferred annular structure 72 is circular, any regular even-sided annular geometry is possible;
Any annular geometric configuration is within the scope of this invention. Typical annular structures include squares, hexagons, octagons, and the like. In the most preferred form, it is comprised of six interconnected fin plates, although one or more fin plates may function equally well. Additionally, some fin plates may function simply as spacers, etc., without delivering fluid. In a preferred embodiment, the annular structure 72 includes at least one outlet fin plate 74 and an inlet fin plate 76. In operation, a first fluid enters through the side inlet manifold 82;
It flows through side openings 84, along internal manifold means 86, and along channels 88 formed by fins 90. Then, the first
Fluid exits through an end opening 92 in the outer periphery and enters an open secondary manifold region 78, which may be provided with optional collection means. The first fluid is then delivered to the appropriate location. Fin plate 76 adjacent to a second fluid that is hotter or colder than the first fluid
through side inlet manifold 94 , flows through side openings 96 and along internal manifold 98 , and flows along channels 100 formed by fins 102 . From there, the second fluid exits through outlet openings 104 provided in the inner periphery and exits into respective open-ended secondary manifolds 80 . In this particular embodiment, as shown in Figure 9b, it consists of a stack of plates with an internal manifold configuration for generating countercurrent flow. Such a flow causes the fin plate 7 to flow over the fin plate 76.
4 can be obtained by stacking them alternately. Any number of annular structures 72 can be stacked depending on the desired capacity of the heat exchanger. To complete the stack of annular structures, a ring-shaped cover plate is sealingly joined to the top annular structure of the stack of annular plates with an internal manifold configuration. It should be noted that this cover plate can simply be another heat transfer annular structure 72. Conventional means for delivering heat transfer fluid to and from the plate and fin heat exchanger are then installed. 9th c
The figure is a partially enlarged view showing approximate relative sizes of the fins and the channel.

In a preferred embodiment, annular structure 72 is comprised of a plurality of annular segments. On the other hand, it is also possible for the annular structure to be a single unit, and it is also possible to configure it to deliver one or more types of fluid. Additionally, the stack of annular structures may be configured to rotate about its axis if certain design parameters indicate desirability.

FIG. 10a shows another embodiment of an open-face fin plate having a manifold structure inside and inside. It should be noted that although the annular fin plate 106 has a circular shape, it is possible to have any regular annular geometry and is within the scope of the present invention. It is something that goes inside. Annular formation 72 is similar to fin plate 106, except that annular formation 72
It should be noted that in the case of , it is composed of multiple fin plate segments. on the other hand,
The fin plate shown in Figure 10a is a single outlet plate. To explain the operation, the first
Fluid enters through inlet opening 108 and flows along internal manifold means 110 . From there,
The first fluid is redirected to flow along a channel 112 formed by fins 114 . This first fluid then flows out of the end opening 116 at the outer periphery and into the open secondary manifold region 118. an inner opening 120 is located at the outer periphery of the outlet fin plate 106;
A means is provided for delivering the second fluid to the next plate. Figure 10b shows the inlet fin plate 12.
2 is shown. A second fluid that is hotter or colder than the first fluid is fed into the fin plate 122 through the opening 120 . From there, the second fluid flows along manifold 124 and fins 12
is redirected to flow along a channel 126 formed by 8. From there, the second fluid exits through outlet openings 130 formed in the inner periphery and exits each open end second manifold region 132.
leaks into The inner opening 108 is the fin plate 1
22 and provides a means for delivering the first fluid to the next plate.
In this particular embodiment, the inlet fin plates 122 and the outlet fin plates 106 are stacked alternately until a desired plate stack height is achieved, thereby forming an annular shaped plate with an internal manifold configuration. It is possible to obtain stacks. It should be noted that if desired,
It is possible to locate multiple inlets and outlets within each plate. To complete the plate stack, a ring-shaped cover plate is sealingly connected to the top plate of the annular plate stack with an internal manifold configuration. It should be noted that this cover plate can be simply another annular plate, or it can also be a separate solid plate. Any conventional delivery means can then be fitted for delivering heat transfer fluid to and from the plate and fin heat exchanger.

Depending on the final use and desired heat transfer rate, different plate thicknesses, channel and fin length and width proportions, and different thermally conductive materials can be used. For example, it is possible to use metals, ceramics, polymers, etc., but the material is not limited to these materials in any way.

By adopting the configuration as described above, it becomes possible to automate the manufacturing of a heat exchanger for the first time. By doing so, it is possible to reduce the working time required for cutting, brazing, welding, leak testing, etc. compared to tube-built-in shell and plate-fin type heat exchangers. Additionally, a wide range of dimensions, materials, and fluids can be used by scaling the permissive design. Below, we will briefly explain the superior thermal efficiency of the IMPS (stacked structure with internal manifold structure) structure compared to conventional ones.

The basic technical advantage provided by the configuration shown in Figure 8c is that all operating surfaces can operate with the same ΔT as the adjacent surfaces in the basic countercurrent heat exchanger configuration. That is to say. That is, each flow path (low temperature or high temperature) has adjacent flow paths (hot or low temperature) on both sides.
The joints 11 between the plates 10 allow heat transfer from plate to plate, thus making it possible to significantly improve the heat exchange efficiency compared to a contactless connection such as in the Alfa-Laval concept. It is. In this configuration, the coolant passages can be adjusted to provide a variable flow area by appropriately varying the width and height to vary the thickness of the walls and supports. is possible. In the basic heat exchange process, the best heat exchange efficiency is obtained with a pure frictional flow process. If there is turbulence due to corrugations, protrusions or surface roughness, etc., pressure effects will occur which will actually reduce the overall heat transfer.
If the basic requirement is to miniaturize the heat exchanger, corrugations, surface roughness, etc. can be added to the IMPS configuration by coining, etching, milling, etc. at the expense of some flow pressure loss. , intermittent fins, etc. can be incorporated. Another feature of this configuration is the ability to obtain different groove dimensions and shapes simply by changing the processing method.

As shown in the accompanying drawings, the internal manifold configuration feature of the present invention minimizes inlet flow losses and allows for heat exchange in the manifold section due to the internal manifold configuration. It is possible to provide the highest efficiency in a configuration of a given length.

In normal cases, the best thermal efficiency can be obtained by providing good countercurrent flow. FIG. 11 shows a basic comparison of co-current, cross-flow, and counter-flow cases. Given sufficient length, efficiency approaches 50% for parallel flow, 80% for crossflow, and even 90% for counterflow. I understand. Since most fin-plate heat exchangers are of the cross-flow type, this alone means that the efficiency of the one proposed in the present invention is increased by 10-15%.

However, the IMPS design can also handle cross-flow or co-current flow, and can additionally use cross-flow and counter-flow fluids and channels.

Examples of three different types of heat exchangers are shown in Figure 12a,
This is shown in Figures 12b and 12c. All three configurations are of the countercurrent type and, as mentioned above, are capable of obtaining the best heat transfer efficiency.

In Figure 12a, the wall has a wavy shape, and the effect of the wavy shape is to add turbulence, thereby improving heat transfer, but not just friction loss. This is accompanied by a large pressure effect due to hydrodynamic head loss. Also, unless the surface alignment and spacing between the hot and cold surfaces are equally matched, pressure losses will occur and inefficient heat transfer will occur. Furthermore, in this configuration there is no heat transfer between the plates within the assembly.

In FIG. 12b, a counter-current ribbed fin plate is shown. In this case, the effect of enlarging the fin surface can be obtained, but the effect of heat conduction between the plates cannot be obtained. Furthermore, the spacing between the channels is such that only a low pressure difference can be maintained between the plates, so that the heat transfer coefficient varies from plate to plate and for a given plate surface area. .

The plate stack configuration proposed by the present invention is shown in Figure 12c, in which the heat exchanger provides optimal countercurrent conditions and is finned to provide an enlarged surface. , and there is no corrugation (minimum pressure loss is possible). Furthermore, a major advantage is that the plate stack provides a close thermal bond, which in (almost) all cases provides improved thermal efficiency. In the case of a high channel height, when the heat transfer coefficient is small compared to the ratio of the thermal conductivity of the material to the average characteristic height (i.e.
N _B i≦1.0), plate-to-plate contact means that there is good contact between the metal not only between two adjacent plates, but also from other plates far away from the direct thermal bond. This means that it benefits from its thermal conductivity properties. Thus, the additional ability to improve heat transfer properties results from three-dimensional heat transfer within the plate stack. Furthermore, by obtaining good three-dimensional heat conduction characteristics in this configuration, the peak value of thermal stress is reduced, and the peak value of the surface temperature within the heat exchanger is proportionally reduced.

The effect of contact between the plates can be expressed by the improvement ratio of the following equation.

δ=K/hS'(L/L+W) (1) where K is the conductivity of the material, h is the average heat transfer coefficient, L is the width of the rib, and W is the channel width. Also, S' is approximately the wall thickness S plus half the channel height. As understood from the above equation, the value of δ greater than 1.0 represents the effect of connecting the plates. In practice, by giving an appropriate geometrical shape, it is possible to obtain a value of δ that is about 10 times larger. This is particularly important if one wants to keep the heat transfer coefficient low to save on pressure effects and driving forces.

FIG. 13 shows the relationship between S' and heat transfer coefficient for various configurations. It is found that in all but the highest heat transfer coefficient cases it is possible to obtain practical thicknesses by using IMPS plate stacks.

The total thermal conductivity q/A for a plate stack heat exchanger per unit surface area between the plates can be expressed (approximately) by the following equation.

q/A=H _h ΔT/(Hh/Hc) (L+W/h+W) _h +(
L+W/h+W) _h +Hh/K(S+1/4(h _h +h _c )) A more detailed analysis can be performed by computer analysis based on the above equation. For a specific driving force, the heat transfer coefficients (H _h and
Once H _c ) is specified, the wall heat flux can be optimized by geometry and material selection.

The ratio of the heat transferred by the plate stack heat exchanger to the reference plane wall configuration (Equation (2), shell with built-in tubes) is expressed as follows.

φ≡q/A/(q/A) ₀ = (1+Hh/Hc+HhS/K)
/(L+W/h+W) _h +Hh/Hc(L+W/h+W) _c +
(Hh (S + 1/4 (hh + hc)) / K) (3) If the low temperature c and high temperature h heat transfer coefficients are approximately equal and the wall has high conductivity K, this ratio φ is as follows: .

φ=2/(1+L/W/1+h/W) _c +(HL/W/
1+h/W) _h (4) However, H _h /H _c = 1.0 K = ∞ Next, if the geometric shapes of the low temperature side and the high temperature side are the same, and the width of the rib and the width of the channel are narrow, the following equation It becomes like this.

φMAX=(1+h/W) (φ maximum value) (5) Therefore, as is clear from the following explanation, the above equation gives the limit of the theoretical heat exchange improvement ratio.
In addition, for the heat transfer coefficients on the low-temperature side and high-temperature side in various cases, materials in various cases, and practical geometric shapes, use equation (3) above or perform accurate computer analysis. Must be.

It is possible to read from FIG. 14 the maximum theoretical heat enhancement ratio that can be obtained by stacking the plates. The value of φ represents, for example, the percentage improvement obtained by high conductivity materials (copper or silver). The case of φ=1.0 represents a standard heat exchanger configuration (for example, a shell with built-in tubes). Other limitations include:
A representation of the theoretical maximum line and (typical) manufacturing limit line has been added. As shown in this figure, in a typical configuration for the same heat transfer coefficient (same driving force), a typical value is obtained that is 3 to 4 times the heat transfer coefficient of the tube built-in shell type. . φ more than 10 times higher than the standard heat exchange value under certain predictive conditions for the same power loss.
It is expected that it will be possible to obtain the value of

Figure 15 shows a specific example where the shape of the recuperator is determined by plate stack computer analysis when the nominal value of φ is 1.4, which is 40% better than the shell with built-in tubes. be. In the case of the plate stack configuration as shown in the figure, it is possible to reduce the required cold side heat transfer coefficient to 50% of the value for the tube-in-tube shell (25% of the original driving force).

In the case of a material with low thermal conductivity, performance deterioration occurs as shown in FIG. 16. When the value of the performance deterioration coefficient Ψ is in the range of 0≦Ψ≦0.1, the performance deterioration is minimal as shown. This ensures that the sizing and thickness values of the plate stack heat exchanger to ensure that the selected material is satisfactory compared to the lowest heat transfer coefficient (cold side or hot side) in the stack. It means that.

For example, it is important to use some derived parameters when the cold and hot side plate geometries are identical (these parameters can also be derived when the geometries are not identical). Is possible). These parameters are as follows.

Surface area per unit area β=2/W (1+W/H) (6) Flow area per front unit area α=1/(1+L/W) (1+S/H) (7) Weight per unit volume γ= ρ[1-1/(1+S/H)(1+L/W)](8
) These parameters include heat exchange efficiency, driving force,
This is important when determining the weight (price), etc.

Although the specific configuration of the present invention has been described in detail above, the present invention should not be limited to these specific examples, and various modifications can be made without departing from the technical scope of the present invention. Of course.

[Brief explanation of drawings]

Fig. 1 is a plan view showing a conventional Alfa-Laval wave-shaped plate, Fig. 2a is an exploded perspective view showing the structure of an open-face fin plate with a manifold structure inside, and Fig. 2b is A plan view showing an open-face type fin plate with a manifold structure inside, Fig. 2c is a side view of the open end side of the face-open type plate with a manifold structure inside, and Fig. 2d shows a manifold structure inside. Fig. 3a is an explanatory view showing one embodiment of the internal manifold of the face-open type plate with a manifold structure inside, Fig. 3b is An explanatory diagram showing another embodiment of the internal manifold of a face-open type plate with a manifold configuration inside, FIG. 4a is an explanatory diagram showing another embodiment of the fin channel configuration, and FIG.・An explanatory diagram showing yet another embodiment of the channel configuration, FIG. 4c is an explanatory diagram showing yet another embodiment of the fin channel configuration,
FIG. 5 is a front view of an open-face fin plate with an internal manifold configuration showing channels and fins of various configurations, and FIG. 6a is a front view of an internal manifold configuration with integral outer side and end manifolds. Fig. 6b is a plan view showing an open face fin plate having an integral inner side and end manifold configuration, Fig. 6c FIG. 6 is a perspective view showing another embodiment of an open-face fin plate having an internal manifold configuration with an integral inner corner manifold;
Figure d is a partial perspective view of an alternative flow guide for the fin plate shown in Figure 6c, Figure 7a is an enlarged partial perspective view showing the relative proportions between the fins and the channel, and Figure 7b is a partial perspective view of the fin plate shown in Figure 6c. Illustration of a plate stack showing vertically staggered fins, No. 8
Fig. 8a is a perspective view showing a plate with one internal and external manifold configuration, and Fig. 8b is a perspective view showing an open-face plate with an internal manifold configuration integrally connected to the sides and ends. FIG. 8c is an enlarged partial perspective view showing the relative proportions of fins, channels, and manifold means; FIG. 9a is a perspective view showing an open-faced plate stack having a manifold structure; is a plan view of an open-face annular structure with a manifold structure inside when each annular structure is composed of a plurality of plates, and FIG. 9b is a plan view of an annular structure in which each ring structure is composed of a plurality of plates. Fig. 9c is an enlarged partial perspective view of Fig. 9a showing the relative proportions of the fins and channels; Fig. 10a The figure is a plan view showing an outlet plate for an annular open type plate with a manifold structure inside, and FIG. 10b is a plan view showing an inlet plate for an annular open plate with a manifold structure inside. Fig. 11 is a graph showing the influence of flow arrangement on heat exchanger performance, Fig. 12a is an explanatory drawing showing the configuration of a counterflow type corrugated wall heat exchanger, and Fig. 12b is a graph showing the influence of flow arrangement on heat exchanger performance. An explanatory diagram showing the configuration of a flow type ribbed fin plate heat exchanger, Fig. 12c is an explanatory diagram showing the configuration of a counterflow type plate stacked heat exchanger, and Fig. 13 shows the limit of the heat exchanger wall thickness. Figure 14 is a graph showing the relationship between the theoretical improvement ratio and the height-to-width ratio of the fins, and Figure 15 is a graph showing the relationship between the theoretical improvement ratio and the height-to-width ratio of the fins. FIG. 16 is a graph showing the relationship between the total film coefficient and the gas film coefficient, and FIG. 16 is a graph showing the relationship between performance deterioration and Biot's number. Explanation of symbols, 10...fin plate, 12...
... open surface, 14 ... side opening, 16 ... manifold means, 20 ... channel, 22 ... fin, 24 ... end opening, 26 ... bottom.

Claims (1)

[Scope of Claims] 1. A closed end is provided along one side of the plate and stands up from one surface of the plate to form an internal manifold region along the closed end, and the plate is upright on the one surface. A plurality of channels are provided with a plurality of fins extending from the internal manifold region toward an open end formed at an opposite end of the closed end, the outermost of the plurality of fins being Each of the pair of outer fins is formed with a side opening corresponding to the inner manifold region and extends continuously from the side opening to the open end;
The plate is formed substantially symmetrically with respect to a center line connecting the center of the closed end and the center of the open end, and the internal manifold region is provided along the closed end and is located on each side at both ends. It forms a long and narrow flow path that communicates with the opening.
A heat exchanger characterized in that one side of the flow path communicates with a plurality of channels, and a plurality of the plates are stacked with closed ends and open ends alternately stacked. 2. The heat exchanger according to claim 1, wherein the internal manifold region becomes wider from the center of the closed end toward each of the side openings. 3 In claim 1 or 2,
A heat exchanger characterized in that at least a portion of the plurality of fins except for the pair of outer fins are partially cut off. 4. A closed end is provided along one side of the plate and stands up from one surface of the plate to form an internal manifold region along the closed end; a plurality of fins extending toward an open end formed at an end opposite to the closed end to form a plurality of channels, each of a pair of outermost outer fins among the plurality of fins; a side opening is formed corresponding to the inner manifold area and each of the outer fins extends continuously toward the open end, and the plate is formed with a side opening corresponding to each of the side openings and extending continuously toward the open end. a side inlet manifold integrally connected to the closed end and a corresponding outer fin, and integrally connected to the corresponding outer fin at a diagonal position with respect to the side inlet manifold on the side of the closed end; and a side-closed manifold, the internal manifold region defining an elongated passage along the closed end and communicating with the respective side openings at both ends; A heat exchanger characterized in that one side communicates with a plurality of channels, and a plurality of the plates are stacked with closed ends and open ends alternately stacked. 5. In claim 4, the plate includes a first auxiliary manifold that is formed integrally with the closed end and on a side opposite to the internal manifold area with respect to the closed end, and a first auxiliary manifold that is formed integrally with the closed end, and a first auxiliary manifold that is formed integrally with the closed end. A heat exchanger comprising: a second auxiliary manifold integrally formed with the pair of outer fins. 6 In claim 4 or 5,
A heat exchanger characterized in that the plate is formed symmetrically with respect to a center line connecting the center of the closed end and the center of the open end. 7 a pair of inlet and outlet manifolds are formed by spaced apart openings extending through the plate, communicating with each of the inlet and outlet manifolds to form a pair of interior manifold regions; a plurality of fins extending between the pair of internal manifold regions to form a plurality of channels communicating the pair of internal manifold regions, and the plate connecting the pair of internal manifold regions and the A pair of connecting manifolds are formed by openings passing through the plate having the same positional relationship as the pair of inlet and outlet manifolds at positions other than the fins and channels, and each of the internal manifold areas is formed wide from a first connecting portion with the corresponding inlet or outlet manifold to a second connecting portion with one end of the plurality of channels, and the plurality of plates are connected to the pair of inlets. and a heat exchanger characterized in that the outlet manifold and the pair of connection manifolds are stacked alternately. 8. In claim 7, a plurality of manifold fins are provided within each of the internal manifold regions, and at least some of the plurality of manifold fins are located between adjacent manifold fins. A heat exchanger characterized in that the distance becomes wider from the first connecting portion to the second connecting portion. 9. The heat exchanger of claim 8, wherein the manifold fins are formed as extensions of the channel-forming fins and are provided across each of the internal manifold regions. 10. According to any one of claims 7 to 9, each of the pair of inlet and outlet manifolds and the pair of connecting manifolds is located substantially at each corner of the plate. A heat exchanger characterized by being located. 11. A heat exchanger comprising a plurality of stacked annular structures having at least one substantially sector-shaped inlet fin plate and at least one substantially sector-shaped outlet fin plate, wherein the inlet fin plate is An outer closed end is formed along the outer peripheral end, and a first internal manifold region as an elongated curved flow path is formed radially inwardly along the outer closed end, and the first inner manifold region is formed as an elongated curved flow path.
The internal manifold region communicates with a first inlet manifold extending through the annular structure through a first side opening formed in one side thereof, and the inlet fin plate includes a first inlet manifold. A plurality of fins extending radially from an internal manifold region to an inner open end formed at an inner circumferential end of the inlet fin plate are provided to form a plurality of channels, while the outlet fin plate is provided with a plurality of channels. An inner closed end is formed along the inner circumferential end, and a second internal manifold region is formed as an elongated curved flow path radially outward along the inner closed end, and the second internal manifold region The old region communicates with a second inlet manifold extending through the annular structure through a second side opening formed in one side thereof, and the outlet fin plate has a second inner manifold. A plurality of fins extending radially from the old region to an outer open end formed at the outer peripheral end of the exit fin plate are provided to form a plurality of channels, and between two adjacent annular structures, a plurality of channels are formed. A heat exchanger characterized in that the inlet fin plates and outlet fin plates of one annular arrangement are stacked on the outlet fin plates and inlet fin plates of the other annular arrangement. 12. The heat exchanger according to claim 11, wherein each of the annular structures has a unitary structure. 13. Claim 12, wherein the first and second inlet manifold regions are located between the inlet and outlet fin plates, and the first inlet manifold region is adjacent to the second inlet manifold region. A heat exchanger characterized in that it is located radially outward. 14. According to any one of claims 12 and 13, the first side openings are formed on both sides of the first internal manifold region, and the second side openings are formed on both sides of the first internal manifold region. are formed on both sides of the second internal manifold region. 15 In a heat exchanger in which a first annular plate and a second annular plate are stacked, the first annular plate has an inner closed end formed along an inner circumferential edge, and a radially outer side formed along the inner closed end. an annular first internal manifold region as an elongated annular flow passageway, and a first internal opening extending through the first annular plate and communicating with the first internal manifold region; , a plurality of fins extending radially from the first inner manifold region to an outer open end formed at an outer peripheral end of the first annular plate to form a plurality of channels; The first annular plate has a first outer opening located near and extending therethrough and separated from the channel, while the second annular plate has an outer closed end formed along the outer circumferential edge thereof. and an annular second internal manifold region as an elongated annular flow path is formed along and radially inwardly of the outer closed end, passing through the second annular plate and forming a second internal manifold region. A second outer opening is formed in communication with the first outer opening and in the same positional relationship as the first outer opening, and the second inner manifold region extends from the inner open end formed at the inner peripheral end of the second annular plate. A plurality of radially extending fins are provided to form a plurality of channels, and the second annular plate extends through the second annular plate in the same positional relationship as the first inner opening and is separated from the channels. a second inner opening formed therein, and the first and second annular plates are stacked with the first and second inner openings aligned with the first and second outer openings. exchanger.