JPS58500080A - Heat exchanger plate with deformation resistant uniform corrugations - 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 is suitable for use in gas turbine recuperators or other types of primary surface heat exchangers. The present invention relates to a low cost, deformation resistant heat transfer plate. The present invention also provides efficient construction from ductile metal sheets. Metal processing method for purposefully and easily forming heat transfer plates and especially primary surface heat exchangers A metal sheet with a wavy pattern of uniform corrugations designed for use as a heat transfer plate for The present invention relates to an apparatus for forming.

Background technology Rising energy costs will affect almost all types of fuel-consuming engines and power plants. or industrial processes release some of the recoverable heat that can be converted into useful work. This has significantly increased the demand for low cost yet effective heat exchangers.

However, the cost of such heat exchangers has decreased in the past due to the wide range of heat exchangers in certain applications. It discourages its use. One of the well-known types of low-cost heat exchangers are arranged to flow heat donor and heat acceptor fluids in heat exchange relationship on opposite sides of each plate. Use multiple stacked plates. The efficiency of such a primary surface heat exchanger is deposited is a linear function of the total surface area of the plate and an inverse function of the wall thickness of the plate separating the heat exchange fluid. One thing has been known for a long time.

Therefore, one approach to forming such heat exchanger plates is to use relatively thin It involves creating a number of corrugations or corrugations in a ductile metal sheet. When the pile is piled up, the board is inserted. In order to prevent this corrugation from occurring, the corrugated folds are given a wavy (or curved) configuration in plan. Ru. When Vcs is made in this way, the apex of the fold of one plate is the apex of the adjacent plate. Form at least some contact points. An example of this type of corrugated heat exchanger plate is r- No. 5,759.525 to Dawson et al. .

Reducing metal plate thickness and increasing fold density (J.K., U.S. Pat. No. 5,759.525) Attempts to increase the heat transfer efficiency of corrugated pleats of the type illustrated in this issue have not always been successful. stomach. The structural opening of the corrugated pleats decreases as the thickness of the metal forming the pleats decreases, and When such weakening is combined with an increase in bulk density, the flow path is restricted or obstructed. The opportunity to do so increases dramatically. In particular, dense folds in weak walls are mechanically It is susceptible to deformation and/or deformation and/or shrinkage from non-uniform temperature induced expansion and contraction. Easy to shake.

In U.S. Patent No. 3,892,119 VC, cost savings without loss of efficiency Manufacture of a heat exchanger consisting of plates as shown in National Patent No. 5,759,525 What is the height and number of pleats on each board? The heat exchange capacity required by increasing It is stated that this can be achieved by reducing the number of boards used. However, the height of each pleat The increase in stiffness further exacerbates the problem of undesired mechanical or temperature-induced crimp deformation, and Until now, there has been no real progress in the efficiencies achievable through the use of primary surface exchangers using pleated plates. There are limits to its use.

The present invention is a low cost, structurally rigid heat transfer plate for use in heat exchangers, It is directed to a board designed to overcome the drawbacks of the prior art mentioned above. especially, The heat exchanger plate of the present invention has corrugations on opposite sides of the plate to form fluid flow passages. shaped pattern, the sidewalls of each pleat have a constant slope along the length of each fluid channel has. This gradient uniformity gives the heat exchanger plate great structural rigidity and overall uniformity. Give sex. Additionally, fluid flow due to mechanical or temperature-induced deformation of the walls forming the fluid flow path. Restrictions and/or obstructions in the flow path are made possible by the efficiency and low cost of prior art pleated heat exchanger plates. can be reduced by this arrangement without sacrificing the structural advantages.

The present invention also has very rigid and uniform properties. To form a heated heat exchanger plate Provided are methods and devices for. This method uses two sets of curved flows on opposite sides of the heat exchanger plate. Continuously note the ductile heat-conducting material to create a series of corrugated folds to form body flow channels. It involves a bending step, where the slope of the sidewall of each pleat is the same as that of the corresponding channel. It is controlled in such a way that it remains constant over its entire length.

Still another object of the invention is to form a heat exchanger plate with uniformly sloped pleats. including a plurality of cooperating channel-forming blades, with at least one blade having a curved configuration and uniformity in plan view; It is an object of the present invention to provide a device having a thickness of The blades each have a non-uniform cross-sectional area. The second and sixth flow path forming blades are arranged to move relative to each other in a reciprocating manner. This first The gap between the blade and each of the second and sixth blades is the fold of the plate formed by this device. uniform over the entire working length of the blade to ensure a constant slope.

A more particular object of the invention is to provide a set of donor fluid channels on one side and a donor fluid flow path on the other side. including corrugated corrugations to form a set of receiving fluid channels between each donor fluid channel. A heat exchanger in which the cross-sectional area of the flow channels is varied in such a way that the gap between the receiving fluid channels is constant. The purpose of the present invention is to provide a switching board.

A more particular object of the invention is to form a receiving fluid channel of the type described above with a uniform cross section. Each fold defines a curvilinear periodic function in plan and has a side wall of constant slope. The purpose of the present invention is to provide a heat exchanger plate characterized by %. Each sidewall has multiple wavelengths The wavelength section can be subdivided into sections, and the wavelength section is located on one of the side walls in plan view. First arc surface? A second arcuate surface is included on the opposite side of the side wall. Both the first and second arc surfaces The other side has an Okaji curvature of medium L-. The remaining portion of each wavelength section of the side wall is the 6th circle in the plan view. and a fourth arc surface, the sixth and fourth arc surfaces being the first and second arc surfaces of the side wall. The center of curvature coincides with the opposite side of the center of curvature of the part.

Additional objects, advantages and features of the invention will be described below with reference to the accompanying drawings. It will become more readily apparent when referring to the detailed description of the embodiments.

Brief description of the drawing Figure 1 shows a plurality of heat exchanger plates designed according to the present invention used in a primary heat exchanger. FIG.

Figure 2 shows the present invention for forming a heat exchanger plate with deformation-resistant uniform corrugated corrugations. 1 is a cross-sectional view of a device designed according to the invention.

FIG. 6 is a cross-sectional view of the apparatus shown in FIG. being moved into position.

FIG. 4 is a cutaway perspective view of a prior art shirring device; Figure 5 shows the prior art shirring shown in Figure 4 with the device moved to the position shown in Figure 2. 2 is a cross-sectional view taken along line 5-5 of FIG. 2; FIG. 6 is a partial cross-sectional view of the plication device of FIG. 5 taken along line 6--6: FIG. 7 is a partial cross-sectional view of the pleating device of FIG. 5 taken along line 7--7.

FIG. 8 is an exploded, cutaway, perspective view of a rib forming device designed in accordance with the present invention: Figure 9 shows the lines when the pleat forming device shown in Figure 8 is moved to the position shown in Figure 2. It is a cross-sectional view according to 5-5VC; FIG. 10 is a partial cross-sectional view of the pleating device of FIG. 9 taken along line IO-IO.

FIG. 11 is a partial cross-sectional view of the apparatus of FIG. 9 taken along line 11--11.

BEST MODE FOR CARRYING OUT THE INVENTION Referring now to FIG. 1, a plurality of heat exchanger plates 2, 4, 6.8 is used to form a stacked plate heat exchanger. Shown in perspective. This general type of heat exchanger is described in U.S. Pat. No. 6,759,32. Although it is fully disclosed and discussed in No. 6, this disclosure is used as a reference here. Incorporate into. As fully explained by this patent, each heat exchanger plate Dano mountain or wave crest? In contact with the folds formed on the adjacent heat exchanger plate. thus having a wavy pattern in plan view designed to prevent each plate from overlapping It includes a plurality of wavy pleats 12.

The sidewalls of each pleat are the entire area actually contacted by the heat transfer fluid between the heat exchanger plates. To increase the surface area, the space between the folds in instant contact is subdivided into multiple fluid flow channels.

Wire rod 14, as more fully described by U.S. Pat. No. 3,759,523. The heat exchanger directs the flow of fluid between the exchangers and causes heat transfer between them. Placed at selected circumferential locations between successive heat exchanger plates to prevent fluid mixing has been done. Inlet section 15 and outlet section 16 direct the heat exchange fluid into the space between the plates. C is attached to the opposite side of each heat exchanger plate to assist in the

For the purposes of this specification, the term “donor fluid” is used to draw thermal energy within a heat exchanger. Refers to a fluid that can be transferred, and may include either gas or liquid.゛Receptive flow The term ``body'' refers to the transfer of thermal energy from a donor fluid when introduced into a heat exchanger. Refers to any fluid, gas, or liquid that can absorb. In Figure 1, heat Exchanger plates 2 and 4 form a receiving fluid flow chamber when each plate is placed next to each other in a folded position. is designed to.

A plurality of receiving fluid channels 18 are provided within the receiving fluid flow chamber from plates 2 and 4. It is formed by the abutting side walls of the corrugations 12 projecting into the fluid flow chamber. similarly , the space between plates 4 and 6 is designed to form a donor fluid flow chamber; The regions between the open corrugations 12 form a plurality of donor fluid flow passages 20 . Features in Figure 1 In certain embodiments, the wire rod 14 and the inlet and outlet sections 15 and 16 carry the donor fluid. C-shaped flow illustrated by arrows 22 in the alternating spaces formed by the deposited plates 11 - 10,000 receiving fluids are arranged to flow in the remaining alternating spaces with arrows 24 The reverse illustrated by (“swept into a zf turn.

To more fully appreciate the unique advantages of the present invention, please refer to U.S. Patent No. 3,892,11. We will first discuss already known pleated heat exchanger plates such as those disclosed in No. 9.

In this patent, a heat exchanger is made of flat, relatively thin deformable sheet metal. A method and apparatus for forming a plate is disclosed. According to this patent, the sheet Sequentially, as the material advances between two pairs of oscillating pleating blades installed on the opposing shaped members, A single fold forming step is then performed thereon. The exact location of each of these four forming members Since purpose and sequential motion are not critical to understanding the invention, the invention is directed to of each of the four forming members used to form a type of pleated heat exchanger plate. See U.S. Pat. No. 5,892,119 for a more complete description of motion and purpose. do. For this invention, the upper donor fluid channel forming blade is connected to the lower receiving fluid channel forming blade. It suffices to note that the Ru. These blades are separated because these blades accept non-pleated ductile sheet material. The ductile sheet material is separated from the corrugated side in the interstitial space between each wave-forming blade. It is designed to move between a second position in which it is deformed to form a wall.

Figure 2 shows that both the method and apparatus of the present invention and that of the colleague prior art can also be used. The shirring is a schematic cross-section of the device. wi, two pairs of relatively movable forming devices 2 6.28.30 and 32 are shown. First forming device 26 and second forming device 28 each support identical donor fluid channeling blades 34 and 36, respectively. Third formation Apparatus 30 (incoming ductile material 37) properly positioned and one of each pleat It is positioned to cooperate with blade 34 to form sidewall 38 . 4th formation Device 32 has a receptacle adapted to enter the space between blades 34 and 36 as shown in FIG. supports the fluid flow path forming blade 40, thereby forming a first A sixth side wall 44 is formed between the second side wall 42 and the gap space between the blades 40 and 36.

Figure 3 is shaped as described in great detail in U.S. Pat. The ductile sheet material 37 is prepared for continuous pleating by all of the forming devices 26 to 32. The first and second Figure 2 shows the apparatus of Figure 2 with the second forming devices 26 and 28 displaced upwardly.

Referring now to FIG. 4, the device used in the device of U.S. Pat. A perspective view of a prior art channeling blade of the type is shown, which includes a pair of donor fluid channeling blades. Includes blades 34' and 36' and receiving fluid channel forming blade 40'.

The prior art blade of FIG. 4 has a uniform thickness. Equipped with this type of wave path forming blade 2, the apparatus of FIG. So, 911! The walls are subject to contraction and expansion caused by external mechanical forces or temperature. create unstable structures that can be easily distorted. To understand this more fully, A cross-sectional view taken along line 5--5 of the device of FIG. Please refer to FIG. 5, which is illustrated as it would appear if it were provided. In particular, Figure 5 the donor fluid channel forming blades 34' and 36' each having a constant thickness dl)l Shows a pair of curved sidewalls consisting of alternating circular arcs arranged in orbits forming a periodic function. vinegar. This receiving fluid flow path forming blade 40' is also made with a constant thickness d2) and the blade 34 A period with the same phase and wavelength as the periodic function defined by the surfaces of ' and 36'. It has side walls each having a cross section formed by a continuous arc defining a period function. One channel forming blade The distance l between the blades in plan view as long as they have a constant thickness! I! The space is determined by the blade surface. Regardless of the shape or configuration of the curved pattern formed, it cannot be constant. Ta Even if each time the surface is made of the same sine wave displaced laterally, the gap space between the blade surfaces will still vary when the gap is measured perpendicular to the central axis of the interstitial space. This out For purposes of application, the central axis between two curves is perpendicular to that line at each point along one of the curves, VC. is defined as the locus of all points located midway between two curves measured along a line. joy However, this definition does not imply any imbalance between these two curves due to the existence of a continuous central axis. I predict that there will be no continuity.

When the height of the pleat is constant and the gap between the blade surfaces is oT, the slope of the side wall of the pleat is flat. It is clear that it must be variable when measured in a plane perpendicular to the central axis of the gap in the plan view. It is clear. Such variations in sidewall slope can have a drastic effect on the lateral stiffness of the folds and of the heat exchanger made with pleated heat exchanger plates. Limit total flow area. To understand this more clearly, let's look at the gaseous donor fluid The total effective cross-sectional area for the flow of Note that the effective cross-sectional area of the receiving fluid flow is usually larger than the available Should. Therefore, the number of donor fluid channels and receiving fluid channels must be equal. Given the requirement that each donor fluid channel not have a cross-sectional area, each of the receiving fluid channels It continues that I have to pick up dogs more and more. As shown in FIG. Each wavelength section (W) has a center of curvature (C1) that coincides with radius (r□) and (R2). It consists of a first part with side walls that draw an arc. This wavelength section of the blade 40' The remaining parts are similarly located on opposite sides of the blade with radii of curvature (r'1) and (r'2) It is shaped to provide a blade surface with a coincident center of curvature (C2). Moshiko If the blades of are made symmetrically such that r□2r' and r22r'2, Each wavelength section of donor fluid forming channel blades 34' and 36' similarly has a radius of curvature (R1) and a radius of curvature (R1). Center of curvature (C3) that coincides with (R3) ′? :Includes a surface that forms an arc.

The second portion of the trough wavelength section of blades 34' and 36' has corresponding radii of curvature (R', ) and (R '2), and the center of curvature (C3) is the point located on the opposite side of the blades 34' and 36'. It has a matching center of curvature (C4). These blades are usually made symmetrically, so R□=R'1 and R3''-F('2).

Since the waveform defined by the blade is symmetrical, the center of curvature of the blade surface is also symmetrical and The position is changed by an amount equal to the wave amplitude vA(H) plus r2'-r1. this The connection facilitates the construction and refurbishment of this heat exchanger board. By referring to Figure 5. As you can understand, the gap between the blades varies from maximum (1'M) to minimum (m). . This minimum clearance (m) is usually the thickness of the board plus the pull-out of the crimper blade. To make it easier, it is made slightly louder than the small amount allowed. This array is a board allows for the maximum number of pleats possible per unit length.

When separated in this way, the side walls made in the area of the minimum gap between each flow path forming blade 1 The slope will have a slope perpendicular to y. The side walls made in this way have very high lateral rigidity. To a small degree, it results in movement of the folds and uncontrolled obstruction of the fluid flow path. donor fluid Some movement of the sidewalls forming the channels is due to the fact that these channels have a fairly large cross-sectional area. And it might be allowed. However, the displacement of the sidewalls forming each of the receiving fluid channels motions can be highly harmful due to their small cross-sectional area.

The disadvantages of sidewall slope changes are illustrated diagrammatically by Figure 6, which shows each pleat formation. FIG. 6 is a partial cross-sectional view taken at 6-6vc of FIG. 5 located at the point of minimum gap between the blades; Special -, the line 6-6 is perpendicular to the central axis of the blade 34'; , and line (C2) in FIG. 6 therefore represents the slope of the side walls 38 and 42. clear As such, the slope of these sidewalls is almost in line with the plane of the ridge exchanger plate being pleated. It is a right angle.

In contrast to the configuration shown in Figure 6 is a heat exchanger formed by the assembly shown in Figure 5. 8 is a cross-sectional view of FIG. 7 taken along line 7-7 of a portion of the switch plate; FIG. %, represented by @(C2) to the slope of the sidewall 38 and the further slope represented by the sidewall 420 line (C3). Please be careful. As can be readily seen, each of the structures formed by the assembly of FIG. This varying slope of the pleat sidewalls 38 and 42 along the longitudinal extent of the pleats arises from fluctuations in time.

Now, referring to FIG. 8, there is a perspective view of the heat exchanger plate forming apparatus of the present invention. It is shown. As clearly illustrated in FIG. 34" and 36U replace the corresponding prior art blades shown in FIG. 4. FIG. As is clear from a comparison between FIG. 8 and FIG. Has a lot of success. To understand the exact function of modified blades 34″ and 3″, See FIG. 9. This FIG. 9 is positioned by the forming assembly shown in FIG. It is a sectional view of the device shown in No. 81A7c by Mari 5-5.

Now, referring to FIG. One with substantial blade thickness variation in the vertical tension of 6 blades from Pl) to maximum (R2) Illustrated as. In contrast, the receiving fluid channel forming blade 40'' is flat. In the direction of the plane that passes through the center and axis of this blade at right angles in the plan view, the vertical direction of this central axis is It has a uniform thickness when measured along its entire length. Variation in donor fluid channel width is significant in terms of the effective width of such channels compared to the narrow cross-sectional width of receiving fluid channels. accepted by. Any variation in the cross-sectional width of such receiving fluid channels Also, due to variations in the cross-sectional area of the donor fluid flow path, the efficiency of an absolute exchanger made from a pleated plate is It would be clearly more detrimental to physical operation. However, the more important and the uniform gap between each surface of the blades 34'' and 36'' is 1 h from the central axis of each flow path. The result is the formation of pleated sidewalls with a constant uniform slope when measured on the plane passing through the corner. The fact is that it will happen.

Sidewall orientation of all pleats with uniform cross-section and curved plan configuration in each receiving channel. Achieving a uniform slope of both blades at each time requires 34″, 36″ and 4″ non- Always requires careful design. Next, each wave of blades 34", 36" and 40" Referring to part (W), there is a string with a constant slope throughout the heat exchange template. Typical cases required to form a receiving channel of uniform cross-sectional area connected to the sidewalls. are shown. In particular, the blade spread between the holes marked (Wl) and (W2) The wavelength portions (W) of 34″, 36″ and 4σ′ are the radius of curvature of the valley side wall of blade 4σ′. It can be divided into first circular arc portions indicated by (Sl) and (C2), respectively.

Adjacent surfaces of blades 34'' and 36'' facing the corresponding surfaces of blade 40'' are each (S 3) and (84).

As shown in Figure 9, each of the arcs identified by the arrows (S□) to (S4) Their centers of curvature coincide at a point (SC). Similarly, blades 34'', 36'' and 40'' The remaining sides of each of arrows (Y□), (Y2), (Y3) and (Y, ) form an arc that touches in plan view.

The arc where the arrows (Yl) and (Sl) touch completes the entire wavelength on one side of the blade 4σ' . Similarly, arrows (Y2) and (S2) complete opposite wavelengths of blade 4σ'. blade The entire wavelength of the surface of the blade 34'' adjacent to 4'' is in contact with the arrows (Y4) and (S4). formed by a circular arc. Finally, the total wavelength on the side of blade 36″ adjacent to blade 4σ′ is It is formed by the circular arc where the arrows (Y3) and (S3) touch. This array The blade is 34".

The gap between 36" and 4σ' is uniform. However, when viewed from the opposite side of the heat exchanger plate, When the waves do not need to be symmetrical, the first and second arcs of each blade surface have equal radius. It is not necessary to have . Furthermore, the wavelength (W) along the vertical spread each time is the same. It is not necessary, nor is it necessary that the amplitudes of each successive wavelength section (W) of the blade be equal. Sl - simply maintain the coincidence of the centers of curvature of each of the arcs touched by the arrow identified by holding and similarly the coincidence of the centers of curvature of each of the arcs touched by the arrows Y1-Y. By maintaining , the cross-sectional area of the receiving fluid flow path formed by blade 4' is They will remain constant throughout their length. At the same time, with this heat exchanger plate The slopes of all the sidewalls forming the pleats are uniform throughout the entire longitudinal extent of each pleat. It will be constant and equal. The side walls 42 and 44 are similarly spaced from the radius (Sl). It has a concentric arc portion with a radius of curvature corresponding to (S4) and (Yl) to (Y4). It includes the wavelength part (W). Each such radius is measured from the corresponding sidewall surface of the blade surface. less than or greater than the corresponding radius by an amount equal to the spacing of .

Turning now to Figure 10, Figure 9 shows a partial cross-sectional view of blades 34'', 36'' and 4''. 1-10-10, where side wall 38 ．． The slopes of 42 and 44 are illustrated by lines 46, 48 and 50. 10th As seen in the figure, lines 46, 48 and 50 are drawn by the outer needle screen of the pleated heat exchanger plate. form a conformal angle to the plane formed by.

FIG. 11 similarly shows blades 34", 36" and 4Ilr' according to line 11-11 of FIG. A partial cross-sectional view is shown. The cross-sectional view in FIG. 11 shows the 1st Q. Note that the cut is made at the maximum width point of the blade 34'' compared to the position in the cross-sectional view shown in K. I want to be Despite this variation in the cross-sectional width of the blade 34'', lines 52, 54 and 56 The slopes of the side walls 38.42 and 44 thus represented are the corresponding lines 46.48 in FIG. and a slope of 50.

The pleated heat exchanger plate forming method and apparatus shown in FIG. and includes a constant cross-sectional area, while the slope of the side walls of the folds forming each fluid flow path It is no longer possible to provide a heat exchanger plate that is constant over the entire longitudinal extent of the flow path. It should be clear enough. 5 This arrangement provides high efficiency, compactness, and rigidity. A type of heat exchanger formed by the apparatus and method shown in Figures 2, 8 and 9 can be formed by depositing a plurality of pleated heat exchanger plates.

Industrial applicability Heat exchangers made by the method and apparatus disclosed herein and in accordance with the present invention The designed heat exchanger plate is suitable for use where heat transfer from one fluid to a second fluid is desired. It can be used for a huge number of purposes. For example, exhaust gas from gas turbines The gas heats the compressed intake air that passes through the combustor and then to the turbine. This intake air forms a donor fluid for the I can do it. Alternatively, a heat exchanger made according to the invention and comprising a pleated plate as described above can be used in boilers, which are steam generators, where the heat from fuel combustion is The gas forms the donor fluid while the receiving fluid is return water or supplementary water from which the steam heat exchanges. Generated in a converter. In still other applications, the receiving fluid is cooling water for internal combustion engines. Including the use of a heat exchanger made in accordance with the present invention where the donor fluid is a base oil.

Additional uses include heat treatment furnaces and heat? Where it is desired to transfer from one fluid to another Includes the use of heat exchangers of the subject type used in filtration and other industrial applications.

Other aspects, objects, and advantages of the invention may be found in the drawings, specification, and appended claims. can be obtained from.

FIG 4. F/θ8゜ international search report

Claims (1)

[Claims] 1 Heat exchanger plates (2, 4, 6, 8) with donor and acceptor flows flowing through this heat exchanger to form a barrier between the bodies and allow heat to be transferred through this plate from the donor fluid to the receiving fluid. This is for forming fluid flow channels (18, 20) arranged as shown in FIG. (2,4,6,8) has a set of donor fluid channels (20) on one side of the membrane plate and this donor fluid flow path (20)? A set of receiving fluid channels (1B) on the other side of the membrane plate a’ Shadow-forming wavy folds (12)? each channel (18, 20) has a pleat (12) bounded on opposite sides in plan by side walls (38, 42, 44) of and flat; Heat with a central axis extending between separate points on the plate periphery in a continuous curved path in plan view In the exchanger plate, the slope of each side wall (3B, 42°44) of the valley membrane plate (12) is When measured in a plane perpendicular to the central axis of the corresponding channel (18, 20), the channel (18, 20) 0) A heat exchanger plate characterized in that it is constant over its entire length. 2. In the heat exchanger plate (2.4°6.8) according to claim 1, the side wall of the valley The slope of (38, 42, 44) The slope of the mold side wall (38, 42, 44) of the pond Equal, % intersection device board. 3. In the heat exchanger plate (2,4°6.8) according to claim 2, the connecting passage (1 All channels (18, 20) in one of the sets of channels (18, 20) Is it a constant cross section m? Heat exchanger plate with. 4. In the heat exchanger plate (2,4°6,.8) Ic according to claim 6, each The cross-sectional area of the channel (18, 20) is - the cross-section of all other channels (18, 20) of the fatty meat. heat exchanger plates equal to the product. 5. In the heat exchanger plate (2,4°6.8) according to claim 4, the flow path (1 8, 20) is the cross-sectional area of each flow path (18, 20) of the other fat meat the length VC? t=i A variable heat exchanger plate. 6. In the heat exchanger plate (2.4°6.8) according to claim 5, the - fat The flow path (18, 20) of the meat is smaller than the cross-sectional area of the flow path (18, 20) in the set of ponds. heat exchanger plate with a large cross-sectional area. Z In the heat exchanger plate (2,4°6.8) according to claim 6, the set of A heat exchanger plate in which the flow path (18) includes the receiving fluid flow path. 8. In the heat exchanger plate (2.4°6.8) according to claim 7, the central axis A heat exchanger plate defining a curved path having a circumference and a function of tA. 9. In the heat exchanger plate (2,4°6.8) according to claim 8, the peripheral a A heat exchanger plate with a constant number of wavelengths. 10 In the heat exchanger plate (2,4°6.8)vc according to claim @9, the - A space exchanger plate in which the width of the periodic function of the valley center axis of the flow path in the set is constant. 11. Heat exchanger plate (2, 4) according to claim 1. In 6.8) the heat exchanger plate wherein the donor and receiving fluids are gases. 12. In the heat exchanger plate according to claim 1, one of the fluids is a gas. and a heat exchanger plate in which the fluid pond is a liquid. 1. In the heat exchanger plate (2.4°6.8) according to claim 10, each side The walls (38, 42, 44) can be divided into multiple wavelength sections (W), and each wavelength section , in the plan view, there is a first circular arc (Y) on the receiving fluid flow path side and a second circular arc (Y) on the receiving fluid flow path side. Y2), and these first and second arcs are on one side of the side wall (3B, 42.44). including a first N portion having a first coincident center of curvature (YC) and sidewalls (38, 42, 4 4), each wavelength section (W) has a sixth circular arc (S2) and a receiving fluid channel on the receiving fluid flow path side in the plan view. A fourth circular arc (Syu) is formed on the fluid flow path side, and the fifth and fourth circular arcs form the first circular arc on the side wall. Contains the remaining part with second coincident curvature center (SC) Y opposite to the coincident curvature center - 〇 heat exchanger plate. 14 Heat exchanger for use as a barrier between donor and receiving fluids flowing through the heat exchanger This plate (2, 4, 6, 8) is used to form the exchanger plate (2, 4, 6, 8), 2, 4, 6, 8) Arranged to transfer heat through the plates (2, 4, 6, 8) ) in a fluid flow path (18°・20　) i′ shape, the method for The method (1) bends a sheet of ductile thermally conductive material (37), and A plane is formed by a pair of side walls (3B, 42.44) made from material seams h (37). Donor fluid channel (2o)' bounded on opposite sides in the figure? Included and flat/plan view A wave with a central axis extending between separate points on the sheet periphery along a continuous curved path at (2) forming the pleats (12) in the form of a sheath (37); Bend the part adjacent to o) to the side opposite to the donor fluid flow path (20) of the see) (37). forming a receiving fluid channel (18), the receiving fluid channel (18) supplying one of the receiving fluid channels (18); bounded by a pair of side walls (3B, 42.44) in common with the feeding fluid flow path and A central axis extending between separate points on the sheet periphery along a continuous curved path in plan view? and (3), a sheet (37) that repeats steps (1) and (2). a set of donor fluid channels (2o) on one side of the and on the opposite side of the seat (37). forming a set of receiving fluid channels, each channel (18, 20) having an adjacent channel (18°2 0) and a common side wall (38, 42, 44)'f. The slope of each side wall (38, 42, 44) of the channel (18, 20) is set to the corresponding channel (1 8°20) when measured at a point along the central axis of the flow path (18, 20). The bending steps (1) and (2) are controlled in such a way that the bending steps (1) and (2) are constant along the entire length of Improvements including control. 156 In the method for forming a heat exchanger plate (2.4°6.8) according to claim 14 Steps (1) and (2) are performed so that the slope of each side wall (38, 42, 44) formed is All sides of the pond’! (37) A method including the step of bending. 16 For forming wavy pleats (12) in a sheet of ductile thermally conductive material (37) Includes slit forming device (26, 28° 30.32.34", 36", 40") Apparatus for forming heat exchanger plates (2, 4, 6, 8), said pleat forming position (26, 2) 8, 30, 32, 34", 36", 4 [r') on one side of the sheet (37) a first channel forming device (26, 28) for forming a supply fluid channel (20); A receiving fluid flow path (18) is formed on the opposite side of the a second channel forming device (30°32.40″) for forming each donor fluid channel. (20) in plan by the l1lli walls (38, 42, 44) of the folds (12) on the sheet periphery along a curved path bounded on opposite sides and continuous in plan. each receiving fluid channel (18) has a central axis extending between separate points; ll [bounded on opposite sides in plan by (38, 42, 44) and flat It has a central axis that extends to separate points on the sheet periphery along a continuous curved path in plan view. In the apparatus, the first and second flow path forming devices! (26°28.30.32.34″ , 36'', 40'') is the slope of the valley side wall (38, 42, 44) of each said pleat (12). , when measured in a plane perpendicular to the central axis of the corresponding fluid flow path (18, 20), the flow path (1 8, 20) Shaped and arranged so as to have a constant distribution over the entire length of ? Featured device. 1Z In the device according to claim 16, the first flow path forming device (26, 2 8, 34", 36") correspond to the desired top view configuration of each donor fluid flow path (20). a first blade (34", 3σ') having an actuating portion having a top view configuration, and The second channel forming devices (30, 32, 40'') define the desired position of each receiving fluid channel (18). a second blade (40”) having an actuating portion with a top view configuration corresponding to the top view configuration; , one of the nuclear forces (34", 36", 40") varies along its longitudinal length. Device with surface thickness. 18. The device according to claim 17, wherein the second blade (40) has a uniform cross section. Equipment with thickness. 19. In the device according to claim 18, the first and second blades are arranged with respect to each other. (37)? received A first position and a ductile seam (37) are separated for the first blade (34"). 36") and the second blade (4σ'), the side walls of the pleat (38, 42, 44 ) an attachment device (26 further including ゜28.30.32), during which time 1! The ljl space is the first and the first in the plan view. Measure in the direction perpendicular to the center line passing between the two blades (34", 36", 40η) and measure evenly. Is it the same thickness? equipment with 20. In the device according to claim 19, each of the first and second blades (34'', 36", 4 rf') plane 1 [-periodic function with constant amplitude and constant wavelength device that includes a central axis that follows a curved path defined by a number. 21. In the device according to claim 19, the gap space has a plurality of wavelength regions (W ), and each wavelength section has the first and second blades (34", 36", 4() ), and the first blade surface (34″, 3 6”) with the first center of curvature on one side of the gap space in plan view. and each wavelength portion of the second blade surface (34", 36", 4σ') The first part of has a center of curvature (C) that coincides with the first center of curvature (C1) in a plan view. and each wavelength portion of the first blade surface (34'', 36', 40'') The remaining part of (W) is the side opposite to the first center of curvature (C1) of the gap space in the plan view. includes a fifth circular arc having a second center of curvature (C2), and the M2 blade surface (34", 3 6'', 4σ') The remaining portion of each wavelength section (W) is located at the second center of curvature (C2 ), the device includes a fourth arc having a center of curvature coincident with ). 22. Heat exchanger plate from sheet (37) deformable into narrow grooved waves across the sheet A method for forming (2, 4, 6, 8), The first forming blade has a wavy and curved profile with a uniform thickness due to its length. (4σ′)? a step of placing the sheet (37) against the -10,000 side; and a second and second 6 forming blades (34”, 36’) to the other side of the sheet (37) and 11 forming blades (4U’) >Continuously and repeatedly moving in a preselected straddling manner with respect to Vc; Each of the second and sixth forming blades (34", 3") has a wavy curvy profile and a wavy shape. The side walls (38, 42, 44) are sloped uniformly across (37). method having a clear variable thickness over its length sufficient to