JPS599496A - Single body plate in which inside for plate-fin type heat exchanger is changed into manifold - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

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 obtained in this case, it is extremely difficult to provide a manifolded configuration of the plate stack where fluids must be separated at the inlet and outlet. The manifold configuration of a cross-flow heat exchanger is relatively simple, and therefore it is more widely used, although it is less efficient and generates different thermal and mechanical stresses than counter-flow systems. has been done.

U.S. Patent No. 3,305,010 (Campbell
et al) disclose one countercurrent system that attempts to solve the problems of implementing a countercurrent heat exchanger in a manifold configuration. 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, this Cambθ11 patent does not disclose a plate having both the functions of a plate and a fin, and does not disclose a means for internally manifolding the play 1- in the plane of the plate. do not have.

Another countercurrent system is shown in Figure 1, which was used at the 5th International Conference held in February 1978 in Miami, Florida.
Proceedings of the 0TEC Conference VI 288-
Alfa-Laval, described on page 320. The Alfa-1aval concept consists primarily of a set of thin metal plates, a frame and means for holding the parts together. These plates 1 to 1 are held between the upper and lower parts of a horizontal support rod and are pressed against a fixed frame plate by fixing 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 provided with gaskets 1~, thus dividing the space between the plates into two systems of alternating flow channels. Two media are passed through these channel systems, the hot medium supplying heat to the cold medium by heat conduction through the thin plates. By providing such a configuration with a gasket, the risk of mutual leakage between media is eliminated. This Alfa-
The basic element of the Lava I concept is the plate, which has a corrugated pattern formed by pressing.

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. be. The material selection for the gasket in this case depends on the conditions of use, but the upper limit is about 360 psi, which is about 400 psi.

The present invention is significantly different from the A Ifa-Laval system described above, to name a few examples: (1) The All'a-Laval system requires a gasket, which reduces the operating pressure. (2) Since contact fins are not provided in the Alfa-Laval system and the bottom of the plate is essentially not flat, the plate height required to obtain the optimum heat transfer coefficient is limited. unable to obtain contact between
(3) A: Since the inlet and outlet of the Ira-Laval system are located at opposite ends but on the same side of the plate, the distribution of the flow across the plate is poor and the heat transfer efficiency is poor. (4) A
In the Ifa-Laval system, no means are provided to drive the flow across the face of the plate, and therefore it is impossible to compensate for its inherent inefficiency. Further, the prior art described above does not suggest anything about the annular plate arrangement 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. An open-faced unitary 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. The end of each channel is adjacent to the boat. It is possible to stack a plurality of face-open type Ii-body fin plates having an internal manifold structure in alternating opposition. This internally manifolded plate stack can be combined with an external manifold to form an efficient, low cost, countercurrent heat exchanger. Another embodiment of the surface-to-plane single plate with an internal manifold configuration has an integral auxiliary Roman manifold and an output Roman manifold,
This arrangement eliminates the need for a separate external manifold.

An object of the present invention is to provide a fin plate with a manifold structure inside for use in a plate-fin type heat exchanger.

Another object of the present invention is to provide a single fin plate with a manifold internal structure for use in a plate-fin type heat exchanger. Yet another object of the invention is to provide a heat exchanger plate 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 l-fin heat exchanger. A further object of the present invention is to increase efficiency by providing an external or auxiliary manifold for supplying fluid to the internal manifold, which is constructed in such a way that the length of the fluid flow path is increased. be. Yet another object of the present invention is to create a low-cost assembly by simply reversing the plate 1- and bonding (diffusion bonding, welding, welding, etc.) or bolting a similar set of plates. The goal is to provide the following. Another object of the present invention is to provide a face-to-face fin plate incorporating a plurality of fin geometries capable of increasing heat transfer by increasing plate-to-plate contact and surface area. That's true. Yet 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 manifolding means for a play 1 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 invention is to provide a heat exchanger that can be manufactured in HliIli.

Hereinafter, specific embodiments of the present invention will be described in detail with reference to the accompanying drawings. Based on the present invention, the interior of the plate-fin type heat exchanger has a manifold configuration (
A fin plate with a variety of configurations is provided. 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. A closed end 18 is adjacent to and lateral to the rear end of the internal manifold means 16. Channel 20 formed by fins 22
is adjacent to and extends transversely to the forward end of the manifold means 16 to direct fluid flow to the end opening 2.
It is oriented towards 4. The bottom 8I 126 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 1o 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 also be a solid object as shown, or simply another basic fin plate]
・It is also possible to spell it as 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 an additional means for heat transfer.

FIG. 2d shows a plate stack 30 with a manifold structure inside, which is made up of a plurality of fin plates 10 with a manifold structure inside. In a preferred embodiment, the fin plates are stacked in alternating and opposing directions. What should be noted regarding each embodiment is that the fin 22
are shown aligned on a vertical line, but they can also be arranged in a staggered manner 1+- as shown in FIG. 7b. Also, although in the preferred embodiment the fin plates are identical, it is possible to vary the internal configuration of alternate fin plates to obtain the desired thermodynamic effect. be. In a preferred embodiment, the first fluid is routed into the internal eyebrow fold 16 through the side openings 14 of the alternating fin plates, along the channels 20 formed by the fins 22, and through the side openings 14 of the alternating fin plates. It flows out through the opening 24. 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 allow fluid to flow through the end opening 24 and It is also possible to flow from the channel 20 into the internal manifold 16 and out the side openings 14. Alternatively, one fluid can be introduced through the side openings 14 and the fluid being used can flow through the adjacent fins. Cocurrent flow is also possible by introducing through the end openings 24 of the plates.

It should be noted that the first fluid and the second fluid can be the same or different, and more than one fluid can be used depending on thermodynamic conditions.

Figures 3a and 3b show internal manifold means 16.
Two alternative embodiments are shown. 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 -23- side openings 14.14, the taper becoming narrower as the fluid reaches the intermediate point 32.

A barrier 34 can be inserted at the intermediate point 32, if desired. In the embodiment shown in FIG. 3b, the internal manifold 16 has one side opening 14 and the taper extends across the width of the fin plate so that
It narrows as it reaches the closed side 23. 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 various configurations for the fins 22 and channels 20. 4th a
In the figure, fins 22 and channels 20 are randomly disposed within the main channels 20 of the basic fin plate 10. As shown in FIG. In comparison, the fin shapes in Figures 4b and 4c exhibit aligned and intermittent fin shapes. The intermittent rows of fins can be alternately arranged as shown in FIG. 4b, or arranged in an array as shown in FIG. 40. The surfaces of the channels can be smooth or rough depending on the specific design requirements. Also, whatever fin configuration is used, the fins and channels are constructed to improve structural integrity and to improve overall heat transfer characteristics. Additionally, the channels 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 configuration is that illustrated by channel 20 and fin 22. However, the channel 36 with rounded corners. U-shaped channel 38. It is of course possible to use channels of different shapes, such as the square-shaped channel 409, the trapezoidal channel 42, and the corresponding fin shapes. One important feature of the invention is that although the channels and fins work together to improve heat transfer properties and structural integrity, the channels themselves are open-faced and therefore easier to manufacture. It's easy. Furthermore,
It should be noted that the channels themselves may have smooth or rough surfaces, and may use corrugations or other surface shapes capable of improving flow conditions and heat transfer properties. It is also possible.

Figure 6a shows a plan view of an open-faced fin plate 62 which is internally and sub-manifold configured.

Fin plate 62 is essentially the same as fin plate 10, but fin plate 62 further includes a closed end external manifold 64 and an open end external manifold 6.
6 and two pairs of side manifolds 68.70.

The six pairs of side manifolds include side entry Roman manifolds 68 and diagonally positioned side closure manifolds 70. All of the external manifolds are unidirectional 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-face fin plate 63 internally and internally manifolded. 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 and an open end auxiliary manifold 66.
, two pairs of inner side manifolds 68 and 70, and a pair of inner inlets 65. The six pairs of inner side manifolds include side entry Roman manifolds 68 and diagonally positioned side closure manifolds 70.

FIG. 6C is a perspective view of another embodiment of a fin plate having a manifold formed therein, generally indicated at 67. Fin plate 67 is basically the same as fin plate 63, except that fin plate 67 has an inner corner inlet 69 and a pair of inner corner manifolds, six pairs of inner corner inlets 69. The plate 67 has an inner corner-in Roman manifold 71 located on the same side as the inner Roman manifold 71 but on the opposite end of the plate 67.

As heat exchange fluid enters fin plate 67, it flows through open manifold 71 and inlet 69, then through internal flow guide 75 and through fin 7.
9 and flows through the open end opening 81 to form an inboard Romanifold 73.
It is leaked through. What you should be careful about is the flow guide 7.
5 are similar to manifold fins 28 and serve the same structural and thermodynamic purpose except that the width of the manifold channels 83 increases as the length of the manifold increases. It is something to do.

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 as shown in FIG. The flow guide 75 is configured to supply fluid to the channels 77 of the flow guide. In the case of the set of flow guides shown in FIG. 6C, the spacing 83 between flow guides 75 increases with increasing length to fins 79 and channels 77. A pair of tab manifolds 85 and 87 are provided, one at each of the remaining two corners of fin plate 67.

Tub manifolds 85 and 87 provide the necessary continuous flow path for fin plate 67 when the fin plates are stacked in alternating opposition.

Figures 7a and 7b and Figures 8a, 8b and 80
The figure shows fin play 1 with a manifold configuration inside.
- and a stacked plate assembly 72 is shown. In a preferred embodiment, the fin plates are stacked in alternating and opposing directions.

A first fluid is fed to an inlet side manifold 68 where the fluid is directed to pass through side openings 14 and through internal manifold means 16 to pass through channels 20 formed by fins 22. be converted. This first fluid then exits the end opening 24 and flows into the open end auxiliary cocoon fold 66 . Auxiliary manifold 66
The first fluid exiting 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-entry Roman 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. Closed end auxiliary manifold 6
4 and side closed end manifolds 70 are used to form a continuous secondary manifold between alternating fin plates. It should be noted that 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 the open-face type fin play 1- whose interior has a manifold structure. Fin plates 74 and 76 are transverse in shape and are joined via a sealable manifold to form annular structure 72 . It should be noted that while the most preferred annular structure 72 is circular, it can be any regular even-sided annular geometry; are within the scope of the present invention. Typical annular structures include squares, hexagons, hexagons, 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 not carry fluid and may simply function as spacers or the like. 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-entry Roman manifold 82, flows through the side openings 84, along the internal manifold means 86, and along the channels 88 formed by the fins 90. flows. The first fluid then exits through an end opening 92 in the outer periphery and enters the open secondary manifold region 78, which may be provided with optional collection means. The first fluid is then delivered to the appropriate location. A second fluid that is hotter or colder than the first fluid is flown into the adjacent fin plate 76 through the side manifold 94 and flows through the side openings 96 and along the inner manifold 98; It 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, a stack of plates C is constructed with an internal manifold configuration for generating countercurrent flow, as shown in FIG. 9b. It is possible to obtain by stacking the fin plates 74 alternately on top of the fin plates 1 to 76. It is possible to stack any number of annular structures 72 depending on the desired capacity of the heat exchanger. To complete the stack of annular structures, a ring-shaped cover plate is hermetically joined to the top annular structure of the stack of annular plates with an internal manifold configuration. What should be done is that this cover plate can simply be another heat transfer annular structure 72. The heat transfer fluid is then delivered to the plate and fin heat exchanger and the Conventional means for delivery from the heat exchanger are installed. Figure 9C is an enlarged partial view showing the approximate relative dimensions of the fins and channels.

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 is circular in shape, it is possible that the annular fin plate 106 has 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, but annular formation 72
It should be noted that in the case of , it is composed of several fin plate segments. On the other hand, the fin plate shown in Figure 10a is a single outlet plate. In operation, a first fluid enters through inlet gateway 108 and flows along internal manifold means 110 . From there, the first fluid is redirected to flow along channels 112 formed by fins 114. This first fluid then flows into the end opening 1 at the outer periphery.
16 and flows to open secondary manifold region 118. An inner opening 120 is located at the outer periphery of the outlet fin plate 106 for directing the second fluid to the next play]
・Provides the means to send supplies to FIG. 10b shows the inlet fin plate 122. FIG. A second fluid, which is hotter or colder than the first fluid, is delivered into the fin plate 122 through the opening 120. From there, the second fluid flows along manifold 124 and is redirected to flow along IC channels 126 formed by fins 128 . From there, the second fluid exits through outlet openings 130 formed in the inner periphery and into respective open-ended second manifold regions 132. Inner opening 108
are located at the inner periphery of the fin plate 122 and provide a means for delivering the first fluid to the next plate.

In this particular embodiment, inlet fin plate 122
By alternately stacking the outlet fin plates 106 and the outlet fin plates 106 until a desired height of the plate stack is reached, it is possible to obtain an annular stack of plates having a manifold structure inside. It should be noted that multiple inlets and outlets can be located within each plate if desired.

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, metals, ceramics, polymers, etc. can be used, 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.

Furthermore, by scaling the allowable design, a wide range of dimensions 6
It is possible to use goods and fluids. The superiority of the thermal efficiency of the IMPS (stacked structure with internal manifold structure) structure compared to the conventional structure will be outlined below.

The basic technical advantage afforded by the configuration shown in Figure 8C is that in the basic countercurrent heat exchanger configuration the operating surfaces at all C have the same ΔT as the adjacent surfaces. This means that it is possible. That is, each channel (cold or hot) has adjacent channels (hot or "cold") on both sides. The joints 11 between the plates 10 allow heat conduction from plate to plate, thus A I
It is possible to significantly improve the heat exchange efficiency compared to that in contactless bonding such as in the fa-Laval concept.

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, C1 best heat exchange efficiency is pure I]i! Iij 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, IMP may be improved by coining, etching, milling, etc. at the expense of some flow pressure loss.
It is possible to incorporate wavy shape 2 surface roughness, interrupted fins, etc. into the S configuration. 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 heat exchange in the manifold area due to the internal manifold configuration. , thus making it possible to provide the highest efficiency in a configuration of a given length.

In most 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 a sufficient length, the efficiency approaches 50% for parallel flow, 80% for crossflow, and 90% for counterflow. I understand. Since many fin-and-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.

Figure 12a shows examples of three different types of heat exchangers.

This is shown in FIG. 121) and FIG. 12c. All of these three configurations are of the counter-current type, which allows the best heat transfer efficiency to be obtained, as described above.

In Figure 12a, it has a wave-shaped wall,
The effect of the waveform is to add turbulence, thereby improving heat transfer, but with large pressure effects due to hydrodynamic head losses rather than just frictional losses. Also, unless the surface alignment and spacing between the ia2M side surface and the cold side surface are matched equally, pressure loss will occur and inefficient heat transfer will occur.

Furthermore, in this configuration there is no heat transfer between the plates within the assembly.

In Figure 12b, a self-flowing grooved 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. Additionally, the spacing between the channels is such that only a low pressure difference can be maintained between the plates, so that the heat transfer coefficients vary from plate to plate and for a given plate surface area.

The plate stack configuration proposed by the present invention is the 12th plate stack configuration proposed by the present invention.
The heat exchanger in this case provides an optimal self-flow condition and has a finned configuration, which provides an enlarged surface, and there is no corrugated shape (minimum pressure loss is required). 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-height channel, when the C1 heat transfer coefficient is small compared to the ratio of the thermal conductivity of the material to the average characteristic height (i.e., Nsi ≦1.0)
, Play 1~ comes into contact with the plate, which means that
This means that one benefits from the good heat conduction properties of the metal not only between two adjacent plates, but also from other plates far away from the point of direct thermal bonding.

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.

Note that 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 width of the channel. 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 providing an appropriate geometry, it is possible to obtain values of δ that are about 10 times as large. This is particularly important when it is desired 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 of J: using IMPS plate stacks.

The total heat transfer coefficient Q/A per unit surface area between the plates for the plate-1 to stacked heat exchanger can be expressed (approximately) by the following equation.

It is possible to perform a more detailed analysis by computer analysis based on the above equation. When the heat transfer coefficients (Hh and HC) on the hot and cold sides are specified for a specific driving force, the heat flux of the wall can be optimized by the geometry and material selection. be.

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.

When the low temperature (0) and high m(h) heat transfer coefficients are approximately equal and the wall has high conductivity (K), this ratio φ is as follows.

(4) However, Hh/Hc = 1.0 K = ■ Next, when 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 is obtained.

Therefore, as is clear from the following explanation, the above equation gives a theoretical limit to the heat exchange improvement ratio.

In addition, for the heat transfer coefficients on the low-temperature side and high-temperature side in the case of Mumu, materials in various cases, and practical geometric shapes, use the above equation (3) or perform accurate computer analysis. Must be done.

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 is, for example, a highly conductive material (copper or silver)
represents the percentage of improvement obtained by 'C'. φ-1
, 0 represents a standard heat exchanger configuration (for example, a shell with built-in tubes). Additional limits have been added to represent the theoretical maximum line and the (typical) production limit line. 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. . It is expected that it is possible to obtain values of φ that are more than 10 times greater than the reference heat exchange value under certain predictive circumstances with the same power loss.

Figure 15 shows a specific example in which the shape of the recuperator is determined by computer analysis of a plate stack 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, 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. The value of performance deterioration coefficient is O≦qt≦
In the range of 0.1, the performance degradation 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.

Table product per unit (6) Front unit stacking flow (7) Weight per unit volume (8) 49- These parameters include heat exchange efficiency, driving force.

This is important when determining the weight (price), etc.

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

[Brief explanation of drawings]

Fig. 1 is a plan view showing a corrugated plate of A Ifa-Laval according to the prior art, Fig. 2a is an exploded perspective view showing the configuration of a surface-open type fin plate with a manifold structure inside, and Fig. 2b The figure is a plan view showing an open-face fin plate with a manifold structure inside.
Fig. c is a side view of the open end side of a surface-open type plate with a manifold structure inside, Fig. 2d is a partially cutaway perspective view of a surface-open plate stack with a manifold structure inside, and Fig. 3a is a An explanatory diagram showing one embodiment of the internal manifold of the open-face plate 50-type plate 1- whose interior has a manifold structure, and FIG. FIG. 4a is an explanatory diagram showing another embodiment of the fin channel configuration; FIG. 4b is an explanatory diagram showing yet another embodiment of the fin channel configuration; The figure is an explanatory diagram showing yet another embodiment of the fin channel configuration,
Figure 5 shows an open-face fin play 1 with a manifold structure inside showing channels and fins of various shapes.
6a is a plan view showing an open fin plate with an internal manifold configuration having an integral outer side and end two-fold shield; FIG. 6b is a plan view showing an integral inner fin plate; A plan view showing a face-open type fin plate with a manifold structure inside and side and end manifolds, and FIG. FIG. 6d is a partial perspective view of an alternative flow guide of the fin plate shown in FIG. 6C; FIG. 7a is a perspective view of an alternative embodiment of the fin plate; FIG. Fig. 7b is an explanatory view of one plate 1 to ff1ff showing vertically staggered fins, and Fig. 8a is an enlarged partial perspective view showing the fins arranged in a staggered manner in the vertical direction. A perspective view showing a plate with a fold configuration, and Figure 8b is a surface-open type plate with a manifold configuration inside.
Fig. 8C is a perspective view showing an open-face plate stack having a merfold structure inside and having side and end manifolds connected together. FIG. 9a is an enlarged partial perspective view showing relative side alignment; FIG. 9a 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; FIG. 9b The figure is a partially cutaway perspective view of an annular surface open type ring structure with a manifold structure inside when each ring structure is composed of a plurality of plates, and FIG. 9C shows the relative relationship between the fins and channels. Figure 9a is an enlarged partial perspective view showing the proportions, Figure 10a is a plan view showing an outlet plate for an annular surface open type plate with an internal manifold configuration, and Figure 10b is an internal manifold configuration. A plan view showing the inlet plate for an annular open plate, Figure '11 is a graph showing the effect of flow arrangement on the performance of a heat exchanger, and Figure 12a is a self-flowing corrugated wall heat exchanger. An explanatory diagram showing the configuration of an exchanger, FIG. 1211 is an explanatory diagram showing the configuration of a countercurrent type ribbed fin plate heat exchanger, and FIG. 12c shows the configuration of a countercurrent type plate stacked heat exchanger. Fig. 13 is a graph showing the limit of the heat exchanger wall thickness, Fig. 14 is a graph showing the relationship between the theoretical improvement ratio and the ratio of the height and width of the fins, and Fig. 15 Figure 16 is a graph showing the relationship between the total film coefficient and gas film coefficient of a stack with a manifold structure (abbreviated as IMPS), and Figure 16 is a graph showing the relationship between performance deterioration and Biot's number. Figure. (Explanation of symbols) 10: Fin plate 12: Radiation surface 14: Side opening 16: Marfold configuration 20: Channel 22: Fin 24: End opening 26: Bottom Patent applicant Rockwell International Corporation 13 Secret procedure amendment Written by Kazuo Wakasugi, Commissioner of the Japan Patent Office, dated July 29, 1982. Display of 1.8 items. 1981 Patent Application No. 11055.
No. 1, 3. Relationship with the case of the person making the amendment Patent applicant 4, Agent 5, Date of amendment order Voluntary 6, Number of inventions increased by amendment None 7, Subject of amendment Drawing 8, Contents of amendment As attached, 442-7'3-3A FIG, IOa

Claims (1)

[Claims] 1. A fin plate for a plate-fin type heat exchanger, comprising an open-face plate forming a channel for fluid, and an internal fin plate disposed on an upper part of the open-face plate. an inlet portion, and a pair of internal corner manifolds, the pair of manifolds being on the same side as an internal entry Roman manifold disposed in the internal entry port portion, an inner corner outlet disposed at an opposite end of the plate, and an internal manifold means including a plurality of flow guides and a manifold channel. and the manifold channel is configured to increase in width with increasing length, and includes a plurality of contact fins and channels to direct fluid flow and improve heat transfer. and wherein said contact fins and channels are provided adjacent to and across said internal manifold means to provide a continuous flow path when said fin plates are stacked in alternating opposition. a pair of closed manifolds respectively disposed at the remaining two corners of said fin plate to provide a flow guide and a fin having a bottom portion abutting said open face of said fin and adjacent plate; plate. 2. The heat exchanger has an external manifold means, and has a plate stack having a manifold structure inside, and the plate stack has a cover plate, and the plate stacks are stacked alternately facing each other. The plate has a plurality of internally manifolded plates having the same or different internal shapes, and each plate 1 has an open-face plate forming a channel for fluid; a side opening disposed transversely through an upper end of the open plate, and having an internal manifold means adjacent the side opening; a plurality of contact fins and channels having a closed end adjacent and lateral to the means for directing fluid flow and improving heat transfer; is located adjacent to and transverse to said internal manifold means and has an open end opening adjacent said channel means and in contact with said open surface of an adjacent plate in said fin and plate stack. A heat exchanger having a bottom portion and having each of the above elements. 3. In the above item 2, the plate is a single play 1
A heat exchanger characterized by being ~. 4. The heat exchanger according to item 2 above, characterized in that the plate has side openings on each of its two sides. 5. The heat exchanger according to item 4 above, characterized in that the openings face each other and are aligned. 6. The heat exchanger according to item 2 above, wherein the internal manifold means has at least one manifold fin. 7. The heat exchanger has an integral auxiliary plate stack internally configured as a manifold, and the plate stack includes a cover plate and a plurality of integral plates stacked alternately facing each other. auxiliary and internally manifolded plates, each plate having an open-faced plate defining a fluid channel extending through the upper end of the open-faced plate; at least one side opening disposed transversely; a pair of integral auxiliary side manifolds for each of said side openings; a second integral auxiliary side manifold disposed diagonally on the opposite side wall; an internal manifold having a closed end adjacent to the side opening, the internal manifold having a closed end adjacent to and lateral to the rear end of the internal manifold; a closed end external integral manifold integral with and sealingly separable from the closed end, with a plurality of contact fins and channels to provide directionality to fluid flow and improve heat transfer; said contact fins and channels being adjacent to and transverse to said internal manifold means, and having an end disposed through an upper end of said open face plate and adjacent said channel means. an open-ended external integral internal manifold opposite the closed M-ended integral external manifold for collecting and providing directionality of fluid; the open surface of the plate adjacent to the fin; A heat exchanger having a bottom portion in contact with the above-mentioned elements. 8. The heat exchanger according to item 7 above, wherein the plate is a single plate. 9. Heat exchanger according to item 7 above, characterized in that the plate has side openings on each of its two sides. 10. The heat exchanger according to item 9 above, wherein -C1 the openings are arranged facing each other and aligned. 11. The heat exchanger according to item 7, wherein the internal manifold means comprises at least one manifold fin. 12. The heat exchanger according to item 7, characterized in that two pairs of the integral auxiliary side manifolds are provided. 13. The heat exchanger of claim 7, wherein said plate has an integral external end manifold disposed at each end thereof. 14. A heat exchanger comprising a stack of plates integrally internally configured as a manifold, the stack of plates including a cover plate;
a plurality of integral internally manifolded plates stacked in alternating opposition, each plate having an open-face plate defining a channel for fluid; at least one internal inlet section laterally disposed on the top of the inlet section, and a pair of integral internal side manifolds for each of the internal inlet sections; an integral internal side open manifold disposed at the internal inlet portion and an integral side closed manifold diagonally disposed on the opposite side wall, the integral side closed manifold having a front end and a rear end. an integral manifold, the integral manifold being adjacent to the interior inlet section, and having a closed end adjacent to and lateral to the aft end of the interior manifold; a closed end external integral manifold integral with and sealably separated from the closed end, including a plurality of contact fins and channels for directing fluid flow and improving heat transfer; said contact fins and channels are disposed adjacent to and transverse to said internal manifold means and are disposed through an upper end of said open face plate and are disposed in said channel means. an open-ended external one-way manifold opposite the closed-ended one-way external manifold for fluid collection and directionality; A heat exchanger having each of the above elements, the bottom portion being in contact with the open surface of the plate adjacent to the fin. 15. The heat exchanger according to item 14 above, wherein the plate is a single plate. 16. The heat exchanger according to claim 14, wherein the internal manifold means includes at least one manifold fin. 17. The heat exchanger of claim 14, wherein said plate has an integral external end manifold disposed at each end thereof. 18.-11. The heat exchanger according to item 14, characterized in that two pairs of the single-piece internal side manifolds are provided. 19. A heat exchanger comprising an annular stack having a manifold configuration externally and internally, wherein said annular stack has a cover plate and a plurality of external stacks stacked with alternating phases. A3 with an annular structure with a central and internal manifold configuration
each annular structure has at least one interfacial discharge lobe plate, said plate having an inlet plate defining a channel for fluids, said plate having an inlet plate defining a channel for fluid at the outer periphery of said play i. at least one side aperture adjacent to and disposed transversely through the upper end of the face-to-face lobe plate; a pair of integral external side apertures for each side aperture; a manifold, one external side manifold disposed in the side opening and a second integral external side closure manifold disposed diagonally on the opposite side wall. , an internal manifold means adjacent the side opening and adjacent an outer periphery of the inlet plate; and an occlusion aligned with the outer periphery of the inlet plate. an end having a plurality of contact fins and channels for directing fluid flow and improving heat transfer, the contact fins and channels being connected to the internal manifold. adjacent to and transverse to the channel means, having an open end opening adjacent to the channel means, and having a bottom in contact with the fins and the open faces of the stacked plates. a face-to-face discharge lobe plate for each inlet plate, the outlet plate having an outer plate defining a channel for fluid adjacent the inner periphery of the outlet plate and having an outer plate defining a channel for fluid; at least one side opening disposed transversely through the upper end of the open-faced outer plate and having at least a pair of integral outer side manifolds, one outer side of the open-faced outer plate; a second integral external side closure manifold is located diagonally on the opposite side wall and has internal manifold means; an internal manifold means is adjacent the side opening and adjacent the inner periphery of the outlet plate, and has a closed end aligned with the outer periphery of the inlet plate; a plurality of contact fins and channels for providing directionality and improving heat transfer, the contact fins and channels being adjacent to and transverse to the internal manifold means; , having an open end opening adjacent said channel means, and having a bottom portion contacting said fin and an open surface of an adjacent plate, said inlet plate via said integral inner and outer side manifolds; and means for sealingly connecting the outlet plate and the outlet plate, the heat exchanger having each of the above elements. 20. The heat exchanger according to item 19 above, wherein the plate is a single plate. 21. The heat exchanger according to item 19 above, characterized in that the plate has side openings on each of its two sides. 22. The heat exchanger according to item 21 above, characterized in that the openings face each other and are aligned. 23. The heat exchanger according to item 19 above, wherein the C1 front manifold means has at least one manifold fin. 24. The heat exchanger according to item 19, characterized in that two pairs of the integral auxiliary side manifolds are provided.