JP2014059139A - Channel system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a channel system to optimize a relationship between pressure drop and movement of at least one of heat, water content and a substance flowing through the system.SOLUTION: A channel system has at least one channel 4 having at least one channel wall 6a, and at least one flow guide unit 7 having a prescribed height. The flow guide unit is extended in a fluid flowing direction while crossing the channel. The flow guide unit has an upstream part 9, a downstream part, and an intermediate part between the upstream part and the downstream part, the upstream part turns away inward from the channel wall 6a to the channel 4 in the fluid flowing direction, the downstream part is directed to the channel wall 6a and returned to the fluid flowing direction, and a transition portion between the intermediate part and the downstream part is curved with a prescribed radius.

Description

    The present invention is a channel system that optimizes the relationship between pressure drop and at least one transfer of heat, moisture and material of a fluid flowing through the system, the channel system comprising at least one channel. At least one channel having a wall and at least one flow guide having a predetermined height, the flow guide extending in a fluid flow direction and across the channel, and The flow guide has an upstream portion, a downstream portion, and an intermediate portion between the upstream portion and the downstream portion, the upstream portion being in the fluid flow direction from the channel wall to the channel. The downstream portion returns toward the channel wall in the fluid flow direction, and the transition between the intermediate portion and the downstream portion has a predetermined radius. For the channel system being curved.

    A heat exchanger / catalyst is often a channel system having a body formed to have a number of small channels arranged in parallel, these channels, for example, a fluid or fluid mixture being exchanged. Flow through the channel. Such channel systems are made of various materials, such as ceramic materials or metals, eg stainless steel, aluminum.

    Channel systems made of ceramic materials typically have a channel cross-sectional area that is rectangular or polygonal, for example hexagonal. Such a channel system is formed by extrusion, which means that the cross-sectional area of the channel is the same along the entire length of the channel and that the channel walls are smooth and flat. .

    In the manufacture of a metal channel body, one corrugated strip and one flat strip are usually wound around a spool. This results in a cross-sectional area of the channel that is triangular or trapezoidal. Most of the metal channel systems available on the market have multiple channels of the same cross-sectional area along their entire length, and smooth and flat channels such as ceramic channel bodies Has a wall. Both of these types can be covered with a coating, for example with a catalyst comprising a catalytically active material.

    Most important in the background is the movement of at least one of heat, moisture, and material between the fluid or mixed fluid flowing through the channel and the channel wall of such a channel system.

    The above types of channel systems are used, for example, in vehicles and industrial internal combustion engines, and these backgrounds typically use relatively small cross-sectional channels and relatively slow fluid velocities. And the fluid flows along these channels in a relatively regular layer. Thus, the flow is essentially laminar. At the entrances of these channels, a predetermined flow occurs across the channel walls only along a short distance.

    As is generally known in the art, a boundary layer is formed in the layered fluid flow next to the channel wall, where the velocity is essentially zero. This boundary layer, especially when referred to as a fully developed flow, significantly reduces the mass transfer coefficient, and at least one transfer of heat, moisture, and mass is primarily due to relatively slow diffusion. Arise. The mass transfer coefficient is a measure of the mass transfer rate and should be large so as to obtain a high efficiency of at least one of heat exchange and catalyst exchange. In order to increase the mass transfer coefficient, the fluid must be formed to flow towards the sides of the channel so that the boundary layer is reduced and the flow movement from one layer to the other is increased. Don't be. This can be caused by what is referred to as turbulence. In a smooth and flat channel, laminar flow becomes turbulent when the Reynolds number reaches a value greater than approximately 2000. If it is desired to reach a Reynolds number of this magnitude in the channels of the channel system included here, a much faster than normal fluid velocity is required in these backgrounds. At low Reynolds numbers for channel systems of the type described above, it is therefore necessary to generate turbulence by artificial means, such as by placing a special flow guide for the channel.

    US 4,152,302 discloses a catalyst with a channel. Here, the flow guide is arranged in the form of a transverse metal flap perforated from the strip. Catalysts with flow guides significantly increase the transfer of at least one of heat, moisture and mass. At the same time, however, the pressure drop increases dramatically. However, it has been found that the effect of increased pressure drop is greater than the effect of increased heat, moisture and / or mass transfer. The pressure drop depends inter alia on the form, size and arrangement of the flow guide. However, it is generally known that the types of flow guides generate excessive pressure effects, and therefore they are not widely used commercially.

    EP 0 869 844 uses a turbulence generator extending across a catalyst or heat / moisture exchanger duct to obtain an improved ratio of pressure drop to at least one transfer of heat, moisture and material. Disclosure.

    WO 2007/078240 discloses a flow converter extending across a channel. However, further improvements in the ratio of pressure drop to at least one transfer of heat, moisture, and material are always a desire for manufacturers of such systems.

    It is an object of the present invention to provide a channel system with a further improved ratio of pressure drop to at least one movement of heat, moisture and material.

    The above objective is accomplished by a channel system having the features defined in the appended claims.

    A channel system according to the present invention that optimizes the relationship between pressure drop and at least one transfer of heat, moisture and material of a fluid flowing through the system comprises at least one channel having at least one channel wall And at least one flow guide having a predetermined height. The flow guide extends in a fluid flow direction and across the channel. Further, the flow guide has an upstream portion, a downstream portion, and an intermediate portion between the upstream portion and the downstream portion. The upstream portion deviates inwardly from the channel wall to the channel in the fluid flow direction, and the downstream portion returns toward the channel wall in the fluid flow direction, the intermediate portion and the downstream The transition between the parts is curved with a predetermined radius. The curved transition between the intermediate portion and the downstream portion reduces the pressure drop and, as a result, against at least one movement of fluid, heat, moisture, and material flowing through the channel system. Further improve the ratio of pressure drop. A decrease in pressure drop results in an increase in fluid flow through the channel system, thus reducing the need for system power. This results in a more efficient system with increased or equal heat, moisture and at least one transfer rate of material. In addition, when a coating is required, a curved (curved) surface is preferred because the coating adherence to the bottom surface is increased and the coating of the entire channel can be flatter. There is also less flash / burr generation during the coating process. The flash / mechanical sound can be, for example, due to accumulation of material at a given spot on a sharp edge. When used at high temperatures by vibration, the buildup that can be thicker than the rest of the coating can be reduced. Moreover, the flash almost increases the pressure drop. A smoother surface suggests that the amount of noble metal required is reduced rather than simply reducing the pressure drop. Production costs are also reduced because production costs are highly dependent on the amount of noble metal required.

This radius improves the quality of the system by reducing the pressure drop, but guiding the fluid increases at least one transfer of heat, moisture, and matter, so the vortex is expanded, ie Controlled turbulent movement of the fluid caused by the cross-sectional area can be caused. This turbulent movement is necessary to increase the rate of movement of at least one of heat, moisture and matter. Preferably, the radius of the first transition between the intermediate part and the downstream part is 0.1 h ₁ -2.1 h ₁ , preferably 0.35 h ₁ -2.1 h ₁ , more preferably 0. it is a .35h ₁ -1.1h _1.

    Suitably, the height of the flow guide is taken in the same direction as the first height to be greater than 0.35 times the height of the channel. This height mixes the fluid flow layer and creates a turbulent movement that increases the rate of movement of at least one of heat, moisture, and material to produce the majority of the fluid flowing through the channel. It is necessary to have an effect on.

The middle portion of the flow guide may have a flat portion that is substantially parallel to one channel wall of the channel. This flat portion is utilized to direct fluid in a direction parallel to the channel. This increases the velocity of the fluid in a direction parallel to the channel. A flat portion may also be needed in order to be able to manufacture a flow guide. Effectively, the length of the flat part may be 0 to 2H, preferably 0 to 2h ₁ , more preferably 0 to 1.0h ₁ in the fluid flow direction.

Preferably, the transition between the downstream portion and the channel wall is curved with a predetermined radius. The radius of the transition between the downstream portion and the channel wall is 0.5h ₁ −1.7h ₁ . The purpose of this radius is to prevent a second vortex from appearing after the flow guide. Such an improper second vortex increases the pressure drop without increasing at least one transfer of heat, moisture, and matter. Thus, by avoiding such vortices, the ratio of pressure drop to at least one movement of heat, moisture, and matter is increased. Thus, the pressure drop is further reduced and instead increases the efficiency of the channel system. In addition, this smooth transition prevents flash / loud noise during the coating process. This transition therefore has the same effect as the transition between the intermediate part and the downstream part as described above in terms of flash / loud sound generation.

Preferably, the third transition between the upstream part and the intermediate part is curved with a predetermined radius. This is to smoothly direct the fluid in a predetermined direction parallel to one side of the channel after passing through the upstream portion. The smooth direction further reduces the pressure drop. The radius of the transition between the upstream portion and the intermediate portion may be 0.2h ₁ -0.5h ₁ . In addition, this smooth transition prevents flash / loud sound generation during the coating process. This transition therefore has the same effect as the transition between the intermediate part and the downstream part as described above in terms of flash / loud sound generation. Alternatively, the radius of the transition between the upstream portion and the intermediate portion can be equal to the radius of the transition between the intermediate portion and the downstream portion. Equal radii are effective for applications where fluid can flow in the opposite direction of the fluid flow direction described above.

Advantageously, the transition between the channel wall of the channel of the flow guide and the upstream portion is curved with a predetermined radius. This is to smoothly guide the laminar fluid flow across the channel, increasing the fluid velocity because the cross-sectional area is reduced. In addition, this smooth transition prevents flash / loud noise during the coating process. This transition therefore has the same effect as the transition between the intermediate part and the downstream part as described above in terms of flash / loud sound generation. Preferably, the radius of the transition between the channel wall and the upstream portion of the channel _may be a 0.2h ₁ -0.5h 1.

    Suitably, the flat portion of the upstream portion has a first angle of inclination relative to the surface of the channel wall from which the upstream portion deviates. This is to direct the fluid in a direction that is not parallel to the channel, so that turbulence can be developed to increase at least one transfer of heat, moisture, and matter. The first tilt angle can be 10 ° to 60 °, more preferably 30 ° to 50 °.

    Preferably, the flat portion of the downstream portion has a second angle of inclination with respect to the surface of the channel wall to which the flow portion returns to this surface. This is due to vortices, i.e., controlled turbulent movement of the fluid, and is caused by a deviated cross-sectional area. This turbulent movement is necessary to increase the rate of movement of at least one of heat, moisture and matter. The second inclination angle is preferably 50 ° to 90 °, more preferably 60 ± 10 °.

Suitably, the channel is at said flow director, the first cross-sectional area A _1, the second cross-sectional area A _2, has a ratio of the area A1 with respect to the area A2, i.e. A1 / A2 is greater than 1.5, preferably greater than 2.5, more preferably greater than 3. The magnitude of this ratio A1 / A2 is necessary to form the desired turbulent movement of fluid in the channel and thus to increase the rate of movement of at least one of heat, moisture and material. It is indispensable to get a good speed.

    In a preferred embodiment according to the present invention, the intermediate portion remains on the inner surface of the channel wall from where the upstream portion is offset. This is to further reduce the pressure drop.

    The channel may have at least one flow guide mirrored with respect to the flow guide. Such mirror-inverted flow guides increase the rate of movement of at least one of heat, moisture, and material throughout the system when several channels are placed in relation to each other.

    According to a preferred embodiment of the present invention, the cross-sectional area of the channel is an upward shape, preferably a triangle. Such a shape is preferable from the viewpoint of manufacturing. In particular, the equilateral triangular cross-sectional area minimizes friction loss along the channel wall per unit area, thus providing maximum flow per unit area. Therefore, an equilateral triangular cross-sectional area is preferred in order to increase the rate of movement of at least one of heat, moisture, and material.

    In general, all terms used in the claims are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All reference signs, definite articles [elements, devices, components, means, steps, etc.] are at least one example of such elements, devices, components, means, steps, etc., unless expressly stated otherwise. It is interpreted openly with reference. The steps of the methods disclosed herein do not have to be performed in the exact order disclosed, unless explicitly stated.

    Other objects, features and advantages of the present invention will be apparent from the following detailed disclosure and from the attached independent claims and drawings.

    The above-described objects, features, and advantages of the present invention will be understood by the non-limiting detailed description of the preferred embodiments of the present invention illustrated below with reference to the accompanying drawings. In the following, the same reference numerals are used for similar elements.

FIG. 1 is a perspective view of a roll according to the present invention. FIG. 2 is a perspective view of a partially opened channel of a channel system according to the present invention. FIG. 3 is a cross-sectional view of an alternative embodiment channel. 4 is a cross-sectional view of the two channels of FIG. 2 positioned on top of each other. FIG. 5 is a cross-sectional view of the channel of FIG. 2 as viewed from one end of the channel. FIG. 6 shows a layer with a channel in the longitudinal direction of the channel.

    The present invention will be described in detail below with reference to the accompanying schematic drawings for the purpose of illustrating preferred embodiments.

    FIG. 1 shows a roll (rotary body) 1 provided with a channel system 2 according to the present invention. This roll 1 can be used, for example, as a catalyst in a heat exchanger such as a heat wheel, gas cooled reactor, gas turbine blade cooling or other suitable application.

    A corrugated strip 13 integral with at least one flat strip 14 forming a plurality of channels 4 is wound with a desired diameter so as to form a cylinder (see FIG. 6), and the channel system of roll 1 2 constitutes the actual core. The indentation 15 (see FIG. 6) of the corrugated strip 13 and the essentially flat strip 14 prevents the formation of the formed roll, i.e. the different layers of the strips 13, 14 are connected to each other. Against being placed against. In addition, a casing 3 surrounds the channel system 2 and holds the channel system 2 together and secures this channel system to an adjacent structure.

    Instead, the number of corrugated strips 13 and flat strips 14 are alternately arranged in layers to form channels 4 (see FIG. 6). This arrangement is suitable, for example, for a plate heat exchanger.

    FIG. 2 shows a perspective view of a partially opened channel 4 having a first flow director 7 and a flow guide 8 that is mirror-inverted with respect to the first flow guide 7. It is. However, at least one of each flow guide 7, 8 can be distributed along the entire length of the channel 4. The various types of flow guides can be randomly arranged as shown in FIG. 2 as well as alternating. Alternatively, only one of the two types of flow guides may be used. In this case, the guides are also distributed along the entire length of the channel 4. These flow guides 7, 8 guide the fluid introduced through the inlet 5 in a predetermined direction.

    Channel 4 is a channel of small dimensions, i.e. usually less than 4 mm in height. Preferably, referring to FIG. 3, the channel height H is between 1 mm and 3.5 mm. Channel 4 has an equilateral triangular cross-sectional area with channel walls 6a, 6b, 6c, which can be less than 5 mm. However, the shape of the cross-sectional area is not limited to an equilateral triangle, and any shape suitable for this application can be taken. Also, the number of channel walls is not limited to 3 and can be any suitable number. Furthermore, in the fluid flow direction, the channel walls 6a, 6b, 6c surround the channel 4, which results in the fluid not having to flow from one channel 4 to the other. On the other hand, the invention is not limited to channels surrounded by channel walls. The channel wall 6 can also partially surround the channel 4 so that fluid can flow from one channel 4 to another.

    The length of channel 4 can vary depending on the application. For example, for a catalyst, the length of channel 4 can be 150-200 mm, and for a heat exchanger, the length of channel 4 can be 150-250 mm. However, the present invention is not limited to the length of these channels. Also, any number of channel systems 2 can be placed one after the other to form a system with the required length.

    Furthermore, the channel 4 may take any axial direction. That is, the present invention is not limited to horizontal channels.

    The first flow guide 7 is arranged on one channel wall 6a of the channel 4, so that the fluid flow (arrow) from the inlet 5 is directed towards the side surfaces 6b, 6c of the two other channels. Led. On the opposite side of the first flow guide 7 there is a bulge 12. By using these flow guides 7, 8 having a special arrangement arranged at a predetermined distance from each other and from the inlet of the channel 4, at least one moving speed of heat, moisture and substance and pressure drop The optimal relationship is obtained.

    After passing precisely through the inlet 5, the fluid flow has an inlet turbulence at the inlet. As the fluid passes through the channel 4, this turbulence decreases, which results in a constant velocity laminar fluid flow inside the channel 4. As fluid approaches the first fluid guide 7, the velocity increases locally depending on the reduced cross-sectional area. After passing through the first fluid guide 7, the enlarged cross-sectional area and fluid velocity cause a vortex, i.e. a controlled turbulent movement of the fluid. The fluid guide 7 affects the main part of the fluid flowing through the channel 4 and results in mixing of the flowing layers. This turbulent movement is necessary to increase the rate of movement of at least one of heat, moisture and matter.

In FIG. 3, two flow guides 7a of the same type are arranged next to each other. The two flow guides 7 extending inwardly into the channel 4 have an upstream part 9, an intermediate part 10 and a downstream part 11. These flow director 7a, 7b has a predetermined height _{h 1.} The first fluid guide 7 a is disposed at a predetermined distance A from the inlet 5. The optimal arrangement of the first flow guide 7a depends on the operating conditions.

The upstream portion 9 has a flat portion 21 that deviates in the fluid flow direction at a predetermined first inclination angle α ₁ with respect to the surface of the channel wall 6a. The first inclination angle α ₁ is defined as the angle between the surface of the channel wall 6a and the extension of the flat part 21 relative to the surface of the channel wall 6a, this angle being the extension of the flat part 21 and the channel wall. It is located downstream of the intersection with the surface 6a.

Further, the first inclination angle α ₁ is defined as the angle α _{1 in} FIG. Furthermore, the first inclination angle alpha ₁ is, 10 ° to 60 °, preferably from 30 ° to 50 °.

    The slope of the upstream portion 9 increases the velocity of the fluid and directs the fluid towards the other surface so that a controlled turbulent movement is the movement of at least one of heat, moisture and matter. Be started to increase.

    The intermediate portion 10 is disposed between the upstream portion 9 and the downstream portion 11. The intermediate part 10 remains inward on the side from the channel wall 6 from which the upstream part 9 extends. Alternatively, the intermediate portion 10 may be both inside and outside the channel wall 6.

Between the intermediate part 10 and the upstream part 9, a curved transition 19 having a predetermined radius R2 is arranged. The radius R ₂ of the transition 19 between the upstream part 9 and the intermediate part 10 is 0.1 to 2 times the height of the flow guide 7, ie 0.1h ₁ -2h ₁ . This is to smoothly guide the fluid flow in a direction parallel to one side of the channel after passing through the upstream portion. For the embodiment with the smallest preferred channel height H, this is equal to 0.04-1.08 mm. For the embodiment with the largest preferred channel height H, this is equal to 0.14 to 4.31 mm.

The intermediate part 10 is parallel to one channel wall 6 a of the channel 4 and has a flat part 16 that is short with respect to the length of the upstream part 9 and the downstream part 11. Also, with respect to the channel wall 6 from which the flow guide 7 extends, the maximum height h ₁ of the flow guide 7 is at the flat part 16 of the intermediate part 10. The height h ₁ is preferably greater than 0.35 times the height H of the channel 4. For the embodiment with the smallest preferred channel height H, this is equal to 0.35-0.54 mm. For the embodiment with the largest preferred channel height H, this is equal to 1.40-2.15 mm. However, the flat part 16 can be provided for manufacturing reasons, but after being directed towards the opposing wall 6b, the fluid flows so that it flows in the direction of the channel 4 in the channel 4, ie in the channel walls 6a, 6b, 6c. Help guide you. Flat portion 16 is 0 to 2H, preferably, 0 to 2.0 h _1, more preferably, 0 to may have a predetermined length in the fluid flow direction of 1.0 h _1. Instead of the upstream portion 9 being parallel to the extending channel wall 6, the flat portion 16 of the intermediate portion 10 may have a predetermined inclination with respect to the channel wall 6a. The inclination can be in the direction of fluid flow inwardly towards the channel 4 or towards the channel wall 6a. In other embodiments, the intermediate portion 10 can have a slightly curved shape, such as a convex shape. The transitions 17, 19 need not be curved, they can be straight.

Downstream portion 11 of the flow director 7, the fluid flow direction, with respect to the predetermined surface of the second inclination angle alpha ₂ in the channel wall 6a, the flat part 22 back. The second inclination angle alpha ₂ is the plane of the channel wall 6a, is defined as the angle between the extension of the flat part 22 with respect to the plane of the channel wall 6a, the angle of the flat portion 22 extend and the channel wall 6a Located upstream of the intersection with the plane. The second tilt angle α ₂ is also defined as angle α _{2 in} FIG. Further, the second inclination angle alpha ₂ is, 50 ° to 90 °, preferably, 60 ± 10 °. Preferably, the flat portion 22 is sufficiently short, downstream portion 11 preferably can be returned to the channel wall 6a of the flat transition portion 18 having a large radius R _4. The flat portion 22 allows a controlled turbulent movement to be created with an enlarged cross-sectional area, which can provide a ratio between the at least one movement of heat, moisture and material and the pressure drop. Optimize.

Said predetermined radius _{R 3} of the transition 17 between the intermediate portion 10 and said downstream portion, from 0.1 to 2.1 times the height of the flow director 7, _i.e., 0.1h _{1 -2.1h} 1 Preferably 0.35 to 2.1 times the height of the flow guide 7, ie 0.35h ₁ -2.1h ₁ , more preferably 0.35 to ₁ of the height of the flow guide 7. .1 times, ie, 0.35h ₁ -1.1h ₁ . For the embodiment with the largest preferred channel height H, this is equal to 0.14 to 4.52 mm, 0.49 to 4.52 mm and 0.49 to 2.37 mm, respectively. This radius guides the majority of the fluid towards the channel wall 6a which forms the vortex caused by the expanding cross section, ie the controlled turbulent movement of the fluid. This turbulent movement is necessary to increase the rate of movement of at least one of heat, moisture and matter.

Alternatively, the radius R ₂ of the transition 19 between the upstream part 9 and the intermediate part 10 can be equal to the radius R ₃ of the transition 17 between the intermediate part 10 and the downstream part 11. That is, 0.1 to 2.1 times the height of the flow guide 7, ie, 0.1h ₁ -2.1h ₁ , preferably 0.35 to 2.1 times the height of the flow guide 7 That is, 0.35 h ₁ -2.1 h ₁ , more preferably 0.35-1.1 times the height of the flow guide 7. For the embodiment with the smallest preferred channel height H, this is equal to 0.04-1.13 mm, 0.12-1.13 mm and 0.12-0.59 mm, respectively. Also, for the embodiment with the largest preferred channel height H, this is equal to 0.14 to 4.52 mm, 0.49 to 4.52 mm, and 0.49 to 2.37 mm, respectively. Equal radii are effective in some applications where fluid can flow further in the opposite direction to the fluid flow direction described above.

A channel wall 6a of the channel 4, between the upstream portion 9, there is a smooth transition 20 having a predetermined radius R _1. The transition 20 radius R ₁ between the channel wall 6 a of the channel 4 and the upstream portion 9 helps to direct the fluid upward towards the channel 4 and is 0 for the height h ₁ of the flow guide 7. .1 to 2 times the height, i.e. 0.1h ₁ -2h ₁ . For the embodiment with the smallest preferred channel height H, this is equal to 0.04-1.08 mm. For the embodiment with the largest preferred channel height H, this is equal to 0.14 to 431 mm.

The optimum radius R ₁ of the transition between the channel wall 6a and the upstream portion 9, and the optimum radius R ₂ between the upstream portion 9 and the intermediate portion 10, respectively, and heat, and moisture, and material Can be determined by the use of a number of empirical parameters. Such parameters are, for example, the ratio of the cross-sectional area A ₂ of the cross-sectional area A ₁ and channel 4 of the channel 4 at the flow director 7, 8, at the flow director 7, 8 relative to the cross-sectional area A ₁ The ratio of the change in the cross-sectional area of the channel 4, the first inclination angle α ₁ and the second inclination angle α ₂ of the upstream portion 9 and the downstream portion 11. The cross sectional area A ₁ of the channel 4 is defined as the cross sectional area at the inlet 5 of the channel 4. Further, the cross-sectional area _{A 1} of the channel 4 is also defined as _{A 1} in FIG. The cross-sectional area A ₂ of the channel 4 of the flow guides 7, 8 is defined as the cross-sectional area at the intermediate part 10 at the height h ₁ . The cross sectional area A ₂ of the channel 4 is also defined as A _{2 in} FIG. If the upstream part 9 is an intermediate part extending therefrom, which is not parallel to the channel wall 6, the cross-sectional area A ₂ is defined as the average cross-sectional area at the intermediate part 10.

Between the downstream portion 11 and the channel wall 6a of the channel ₄ is a smooth transition 18 having a radius R4. The radius R ₄ of the transition 18 between the downstream portion 11 and the channel wall 6a of the channel 4 can reduce the formation of the second vortex and increase the pressure drop. The radius R ₄ is 0.2 to 2 times the height of the flow guide 7, ie 0.2h ₁ -2h ₁ , preferably 0.5 to 1.5 times the height of the flow guide 7; That _is, 0.5h ₁ -1.5h 1. For the embodiment with the smallest preferred channel height H, this is equal to 0.01-2.15 mm and 0.18-0.81 mm, respectively. For the embodiment with the largest preferred channel height H, this is equal to 0.03-8.62 mm and 0.70-3.23 mm, respectively. However, these transitions 18, 20 are not limited to having a predetermined radius, and they can be straight.

    The smooth transitions 18, 19, 20, 21 result in a smooth fluid flow throughout the flow guide 7. At the same time, the transition part guides the fluid in a predetermined direction. A smooth transition also reduces the pressure drop because the pressure drop is established by friction between the fluid and the walls of the channel.

2 and 3, the upstream portion 9 of the flow guide has a flat portion 21. In other embodiments not shown, the upstream portion 9 can have two portions that are curved with respect to each other without a flat portion therebetween. That is, the upstream portion 9 may be formed by a concave transition portion 20 between the channel wall 6a and the upstream portion, which is continuous with the convex transition portion 19 between the upstream portion 9 and the intermediate portion 10. Good. In this case, the first inclination angle α ₁ refers to the angle between the tangent line at the intersection and the plane of the channel wall 6a found in the cross-sectional area of the two curved portions. In other aspects, the first tilt angle is similarly defined when having a flat portion 21.

In other embodiments, the downstream portion 11 can have a concave or convex shape, or the downstream portion 11 can have two portions that are curved with respect to each other without a flat portion 22 therebetween. it can. That is, the downstream portion 11 can be formed by a convex transition 17 between the intermediate portion and the downstream portion that is continuous with the concave transition 18 between the downstream portion and the channel wall. In this case, the second inclination angle α ₂ refers to the angle between the tangent line at the intersection and the plane of the channel wall 6a as seen in the cross-sectional area of the two curved portions. In other aspects, the second angle of inclination is similarly defined when having a flat portion 22.

    In FIG. 3, the second flow guide 7b is located at a predetermined distance B from the first flow guide 7a, and the second flow guide 7b has the same arrangement as the flow guide 7a. Has a shape. The second flow guide 7b can also have a different arrangement shape compared to the arrangement shape of the first flow guide 7a. Since the distance B should be sufficiently large, the turbulent movement formed after passing through the first flow guide 7a can be utilized to the maximum, and the fluid The direction can be taken, that is, the direction parallel to the channel 4 and the channel walls 6a to 6c. With this distance, unnecessary pressure drops are prevented without reducing at least one transfer rate of heat, moisture and material. The present invention is not limited to having flow guides at equal distances B from each other. On the contrary, it is possible to arrange the flow guides at any distance from each other.

The bulging part 12 is arrange | positioned on the flow guides 7a and 7b. Preferably, the height h ₂ of the bulge 12 is less than the height h ₁ of the flow guide 7. This reduces unnecessary turbulence in the bulge 12. Furthermore, preferably the bulges 12 have a shape on the bottom surface of the second channel that is well adapted to the corresponding bulges 12 defined by the flow guide (see FIG. 4). The height of the bulge 12 is preferably very high so that a stable assembly is obtained when the channels are arranged in layers, to prevent it from getting stuck. Here, the fit refers to the unwanted movement of the channel layers relative to each other. The present invention is not limited to having one bulge at each flow guide 7. Alternatively, for example, there can be one bulge in the fluid flow direction at the first flow guide 7 and the last flow guide 7.

    FIG. 4 shows two channels 4 arranged in relation to each other, as in the channel system 2, each of which has a first flow guide 7 and a first flow guide 7. And a second flow guide 8 that is mirror-inverted. If only flow guides that extend into the channel are used, only half of the channel is wrapped when they are wrapped together or arranged relative to each other as shown in FIG. Have Further, each second flow guide is a flow guide 8 mirrored with respect to the first flow guide 7 in order to increase the movement of at least one of heat, moisture and material. Since it is appropriate, every channel is provided with a flow guide. The second flow guide 8 that is mirror-inverted with respect to the first flow guide 7 is located at a predetermined distance B from the first flow guide 7. This distance B is such that the movement of the turbulent flow formed after passing through the first flow guide 7 can take the direction of the channel 4, i.e. parallel to the channel 4 and the channel wall 6a. Should be pretty big. Fluid approaching the mirror-inverted second flow guide gains a large enlarged area and the velocity decreases locally.

    FIG. 5, which is the cross-sectional area of the channel of FIG. 2 as viewed from one end of the channel, shows how the cross-sectional area is affected by irregularities 5 from both sides. Both a first flow guide 7 and a mirror-inverted flow guide 8 are shown in the drawing, which extend over the entire channel wall 6a (see also FIG. 1). The cross-sectional area of the channel is triangular, but any top-shaped cross-sectional shape is suitable. Therefore, a trapezoidal cross section can also be realized.

In order to create the desired turbulent movement, a predetermined velocity V ₂ of the fluid is required at the middle portion 10 of the flow guide 7. The velocity V _2, the channel cross-sectional area A ₂ of at the intermediate portion _10, for example, the velocity V ₁ of the part of the channel having a cross-sectional area A ₁ and the cross-sectional area A ₁ of the channel 4 at the inlet of the channel It depends. By using the equation ^{_{A 2 = A 1 (v 1}} ) 2 / v 2, area _{A 1} to the area _{A 2, i.e.,} the most effective ratio of A 2 / _{A 1} is calculated depending on the application be able to. The ratio of the area _{A 1} to the area _{A 2} is greater than 1.5, preferably greater than 2.5, more preferably greater than 3.

According to an alternative form of the invention, the flow guide is such that the intermediate part between the upstream part and the downstream part is parallel to the triangular side of the channel cross-sectional area from the side from which the flow guide extends. Arranged in such a way. In another alternative, the flow guide is such that the intermediate portion between the upstream and downstream portions is perpendicular to one of the triangular sides of the triangular cross-sectional area of the channel. This means that the upstream part and the downstream part respectively have an inclination with respect to the two sides of the channel not only on the side where the flow guide deviates from here, but also on the adjacent side. Further, in an alternative embodiment, the flow guide has a predetermined slope with respect to the side that the middle portion departs from the flow guide, i.e. the flow guide has four inclined surfaces. The convex surface provided with is formed. Alternatively, one flow guide may extend from one channel wall 6a and back to the other channel wall 6b, or the flow guide may extend from any order of different channel walls 6a-6c and back. Also good. For example, all the third flow guides may extend from the channel wall 6a, or the flow guides between the channel walls 6a may instead extend from the two remaining channel walls 6b, 6c. . Furthermore, in an alternative embodiment, the flow guide is from two or several channel walls 6a-6c at the same distance from the inlet of the channel 4 or from the flow guides 7, 8 of the channel 4. It can extend upstream. This results in narrow channels from multiple walls. This type of flow guide can be combined with the flow guides 7, 8 shown in the drawings.

    FIG. 6 shows a layer with the channel 4 of the channel system 2 in the longitudinal direction of the channel according to the invention. One corrugated strip 13 is preferably such that the flow guides 7, 8 form both a recess 15 at the folded edge and an extruded portion at the inner folded edge. Used as pressed from one side. The recess 15 is here the same as the flow guides 7, 8 described above. In this embodiment, a substantially flat strip 14 in which uneven portions 15 corresponding to the uneven portions of the corrugated strip 13 are further formed is used. The flat strip 14 and the corrugated strip 13 press the other against one upper portion, and as a result, the uneven portion of the flat strip fits into the uneven portion of the corrugated strip.

    In order to further increase the movement of at least one of heat, moisture, and material, the channel with the tip of the triangular cross-sectional area pointed downward and the channel with the tip of the triangular cross-sectional area pointed upwards Conveniently, a recess / extrusion part is provided, which results in all channels being provided with flow guides.

    For all channels provided with flow guides, it is convenient to form the recess / extrusion part from both sides, so that the triangular base, which is the cross-sectional area of the channel, is pressed inward, thereby Achieve a reduction in cross-sectional area. The recesses / extrusions of the channels having triangular cross-sectional tips that point inwardly and outwardly are each offset relative to each other along the channel and are preferably spaced equidistant from each other. The cross-sectional area of the exact same channel at different points along the same thus has a recess in the triangle / triangle of the triangle tip and a recess in the triangle / triangle of the triangle base. This is primarily a reduction in cross-sectional area that helps turbulence be generated. This means that as the cross-sectional area is reduced, the base is pressed inward toward the center of the channel to create turbulence. When the tip of the triangle is pressed inward toward the center of the channel and the base is pressed outward, the cross-sectional area increases instead at these portions.

While the foregoing invention has been described in connection with a preferred embodiment of the present invention, it will be appreciated that certain changes can be made without departing from the invention as defined by the appended claims. Will be apparent to those skilled in the art. For example, as described above, the corrugated strip can be corrugated in other ways to obtain other channel profiles. If it does not constitute an obstacle to the fitting of the flow guide, for example, if the angle between the upstream part and the downstream part is small compared to the longitudinal direction of the channel, the acute angle with respect to the longitudinal direction of the channel is slightly less It is possible to form special recesses / extrusions that are small. And such a snap-in failure should be small compared to the cross-sectional area of the channel compared to the flow guide to minimize the pressure drop. Such an obstruction can, of course, be a supplemental flow guide that functions to pre-fit the obstruction. Number of recesses / flow director is dependent on the cross-sectional area A ₁ of the length and the channel of the channel. In order to optimize the ratio of pressure drop to at least one movement of heat, moisture and material, channels with smaller cross-sectional areas require shorter distances between flow guides, resulting in larger cross-sectional areas More flow guides are required than channels with Furthermore, from a manufacturing point of view, it is appropriate to have a predetermined distance that can be reused for different applications. For the preferred embodiment, the number of flow guides can be 5 to 6 channels 150 mm long. However, the number of flow guides is not limited to this number at all.

Claims (20)

A channel system (2) that optimizes the relationship between the pressure drop and the movement of at least one of heat, moisture and material of the fluid flowing through the system,
This channel system
At least one channel (4) having at least one channel wall (6a);
And at least one flow guide (7a, 7b) having a predetermined height (h ₁ ),
The flow guide extends in a fluid flow direction and across the channel;
The flow guide is
An upstream part (9);
A downstream portion (11);
An intermediate part (10) between the upstream part (9) and the downstream part (11),
The upstream portion (9) deviates inward from the channel wall (6a) to the channel (4) in the fluid flow direction; and
In the channel system, the downstream part (11) returns in the fluid flow direction towards the channel wall (6a),
The channel system transition between the intermediate portion (10) and said downstream portion (11) (17), characterized in that it is bent at a predetermined radius (R ₃₎ (2). The radius (R ₃ ) of the transition part (17) between the intermediate part (10) and the downstream part (11) is 0.1h ₁ -2.1h ₁ , preferably 0.35h _1- 2.1H _1, and more _preferably, the channel system of claim 1 wherein 0.35h ₁ -1.1h 1 (2). Said height of said flow director (h _1), the said height of the flow director in the same direction as (h _1), greater than 0.35 times the height of said channel (4) (H) 3. A channel system (2) according to claim 1 or 2 being taken.   The channel system (2) according to any one of the preceding claims, wherein the intermediate part (10) has a flat part (16) substantially parallel to the channel wall (6a) of the channel (4). Said flat portion (16), the fluid flow direction, 0 to 2H, preferably, 0 to 2h _1, more preferably, 0 to channel system according to claim 4 having a length of 1.0 h ₁ (2) . The transition between the downstream portion (11) and said channel wall (6a) (18) is claims 1 is curved at a predetermined radius (R ₄₎ 5 any one of the channel system (2 ). The radius (R ₄ ) of the transition (18) between the downstream part (11) and the channel wall (6a) is 0.2h ₁ -2h ₁ , preferably 0.5h ₁ -1. 5h ₁ channel system according to claim 6 which is (2). A channel system (2) according to any one of the preceding claims, wherein the transition (19) between the upstream part (9) and the intermediate part (10) is curved with a predetermined radius (R ₂ ). ). The channel system (2) according to claim 8, wherein the transition (19) between the upstream part (9) and the intermediate part (10) is 0.1h ₁ -2h ₁ . The radius (R ₂ ) of the transition (19) between the upstream portion (9) and the intermediate portion (10) is equal to the radius between the intermediate portion (10) and the downstream portion (11). the radius channel system _{(R 3)} equal to claim 8 of the transition portion (17) (2). The transition (20) between the channel wall (6a) of the channel (4) and the upstream part (9) of the flow guide (7a, 7b) is curved with a predetermined radius (R ₁ ). A channel system (2) according to any one of the preceding claims. The transition between the channel wall and the upstream portion of the channel (8) (20) the radius of _{(R 1),} the channel system of claim 11, which is a 0.1 h ₁ -2h ₁ (2) . The flat portion (21) of the upstream portion (9) has a first angle of inclination (α ₁ ) with respect to a plane from which the upstream portion (9) deviates from the channel wall (6a). Any one of 12 channel systems (2). The channel system (2) according to claim 13, wherein the first tilt angle (α ₁ ) is between 10 ° and 60 °, preferably between 30 ° and 50 °. The flat part (22) of the downstream part (11) has a second inclined angle (α ₂ ) with respect to the channel wall (6a) returning to the downstream part (9). Or one channel system (2). The channel system (2) according to claim 13, wherein the second tilt angle (α ₂ ) is 50 ° to 90 °, preferably 60 ° ± 10 °. It said channel (4) is at said flow director (7a, 7b), has a first cross-sectional area _{A 1,} the second cross-sectional area _{A 2,} and
The ratio of the area _{A 1} with respect to the area _{A 2,} rather than 1.5, preferably than 2.5, more preferably, no claim 1 greater than 3 to 16 any one of the channel system (2 ).   18. A channel system (2) according to any one of the preceding claims, wherein the intermediate part (10) remains on the inner surface of the channel wall (6a) where the upstream part (9) is offset from the channel wall (6a). ).   19. A channel system (2) according to any one of the preceding claims, wherein the channel (4) comprises at least one flow guide (8) mirrored with respect to the flow guide (7).   A channel system (2) according to any one of the preceding claims, wherein the cross-sectional area of the channel (4) is an upward shape, preferably a triangle.

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