JP2011158140A - Plate-type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a plate-type heat exchanger capable of reducing pressure loss without degrading performance and pressure capacity, and being manufactured by a simple manufacturing method suitable for miniaturization and superior in heat transferring efficiency. <P>SOLUTION: This plate-type heat exchanger includes: first partitioning sections 35a extending from the center of a plate 10a to both end directions, and formed to section a an upstream side and a downstream side of a first fluid flow channel R1 at the center, and communicate the sections at first communicating sections disposed on both ends; and second partitioning sections 35b extending to the center direction from both ends of the plate 10a, and formed alternately with the first partitioning sections 35a to section the upstream side and the downstream side of the first fluid flow channel R1 at both ends, and communicate the sections at a second communicating section disposed on the center. The first partitioning sections 35a and the second partitioning sections 35b are respectively formed by making the plate 10a bulge to the first fluid flow channel R1, and permanently bonded to a plate 20b opposed thereto through the first fluid flow channel R1. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a plate heat exchanger, and more particularly to a plate heat exchanger that heats or cools a fluid.

  In a so-called plate heat exchanger, a plurality of plates are stacked. As an example of such a plate heat exchanger, it has been proposed that an opening is provided in the side wall (partition part) of the fluid flow guide channel as a pressure loss reducing means when the first fluid channel is a meandering flow. (Patent Document 1).

  Moreover, as a heat exchanger suitable for use in the vapor compression refrigeration cycle, the cross-sectional areas of the first fluid channel and the second fluid channel are made different and meandering flow is prevented, thereby preventing refrigerant drift and performance. An improved plate heat exchanger has been proposed (Patent Document 2).

Special table 2009-530582 JP 2009-186142 A

  According to Patent Documents 1 and 2, the flow path of one or both fluids is a meandering flow. By adopting a meandering flow, the cross-sectional area of the flow path can be reduced and the flow velocity can be increased, so that the performance can be improved. However, on the other hand, since the flow path becomes long, an increase in pressure loss is unavoidable. In particular, when the size of the plate increases, the tendency becomes more prominent.

  For example, according to Patent Document 1, a flow is partially short-passed by providing an opening in a side wall in a meandering flow, thereby reducing pressure loss. However, since a short path is generated, performance degradation is caused. Specifically, taking the low temperature side fluid as an example, the flow is as shown in FIG. 18A. The meandering flow Z and the short path X are separated by the separation portion P # 1, and the meandering flow Z and the short path X are separated. The temperature change before and after the junction P # 2 is as shown in FIG. The meandering flow Z side distributes the flow rate to the short path X side to reduce the flow rate, so that the temperature rises quickly by exchanging heat with the high temperature side fluid. On the other hand, without making a detour through the opening provided in the side wall, it mixes with the short path X side where the temperature is low without being heated so much, and the temperature on the meandering flow Z side is lowered. As a result, the low temperature side fluid undergoes a characteristic temperature change like the merge portion P # 2. If there is no short path X, the temperature changes as shown in FIG. 18 (C). However, the presence of the merging portion P # 2 is exchanged because the temperature of the high-temperature fluid partially approaches. Since the amount of heat becomes small, it becomes a factor of performance degradation.

  In addition, as shown in Patent Document 1, if a large number of small openings are provided, in other words, if a large number of small short paths Y are provided, the temperature difference at the junction P # 2 can be reduced, and the meandering flow Z and The influence at the junction of the individual short paths X and Y is reduced. However, since there are many junctions over the entire surface of the plate, the performance of the entire heat exchanger is eventually lowered. The presence of the short paths X and Y is a performance degradation due to the fact that the temperature difference between the high temperature side fluid and the low temperature side fluid is substantially reduced. Therefore, when the temperature difference between the high temperature side fluid and the low temperature side fluid is large, the performance degradation occurs. The degree of is small and not a problem. However, this is a problem that cannot be overlooked in general heat exchangers.

  Further, according to Patent Document 2, it has been proposed to use a meandering flow for the purpose of improving performance as a heat exchanger for a vapor compression refrigeration cycle. However, for example, taking an evaporator as an example, the refrigerant supplied to the heat exchanger in a two-phase state of gas and liquid (usually 70 to 85 wt% is liquid) exchanges heat with the high-temperature side fluid, and the liquid portion refrigerant. Evaporates and vaporizes. By evaporating, the volume of the refrigerant increases rapidly. As a result, the flow velocity increases toward the downstream side where the refrigerant evaporates, and there is a problem that the flow velocity becomes excessively large and the pressure loss increases near the outlet of the heat exchanger in which almost all the gaseous components of the refrigerant occupy. . On the other hand, if the refrigerant flow rate near the outlet of the heat exchanger is optimized, the flow rate becomes too small on the upstream side of the heat exchanger and the heat transfer performance on the upstream side becomes low.

  The inventor eliminates the contact portion with the adjacent plate other than the partition portion in the heat transfer portion of the first fluid flow path to prevent the accumulation of impurities and cool the water to near 0 ° C. or below 0 ° C. However, a plate-type heat exchanger that is difficult to freeze is proposed (Japanese Patent Application No. 2009-81031).

  According to this, in the first fluid flow path, the plates other than the adjacent plate and the partitioning portion are not in contact with each other in the heat transfer portion of the plate, so that dirt or the like can be prevented from being trapped or fibrous foreign matters or the like can be caught. It has a structure. However, since the first fluid flow path becomes a meandering flow, the flow path must be long, pressure loss tends to increase, and this tendency becomes more prominent when the plate is large.

  In order to reduce the pressure loss of the first fluid, the gap between the partition part and the partition part may be widened. However, since the heat transfer section of the first fluid flow path has a structure in which only the partition section is in contact, the pressure resistance strength of the first fluid flow path is significantly reduced. In order to compensate for this, it is necessary to attach a large reinforcing member.

  As another means for reducing the pressure loss, it is conceivable to increase the height (depth) of the partition portion. In order to increase the height of the partition portion, the width of the partition portion must be increased for manufacturing reasons (for example, in the case of manufacturing by press molding or the like). However, although the partition part is a heat transfer part, it is a part where the cross-sectional area increases for the second fluid, and the flow rate of the second fluid is small, so the heat transfer performance of the part is low. Therefore, increasing the width of the partition portion increases the area of the portion having low heat transfer performance, and causes a decrease in the performance of the entire heat exchanger.

  The present invention provides a plate heat exchanger that can be manufactured by a simple manufacturing method that reduces pressure loss without causing performance degradation or pressure strength reduction, is suitable for downsizing, has excellent heat transfer efficiency, and the like. Objective.

  The plate-type heat exchanger of the present invention is a first fluid flow path in which a plurality of plates are stacked, the adjacent plates are permanently joined together at their peripheral edges, and the first fluid flows between the adjacent plates. And the 2nd fluid flow path through which the 2nd fluid flows is formed alternately, and heat exchange is performed via the heat transfer part of the plate in which the 1st fluid and the 2nd fluid exist between them. The plate heat exchanger according to the present invention extends from one center of the plate to both or both heat transfer portions facing each other across the first fluid flow path from the center of the plate toward both ends of the plate. A first partition portion that is formed so as to partition the upstream side and the downstream side of the first fluid flow path at the center and to communicate the partition at first communication portions provided at both ends of the plate. And a second partition portion formed alternately with the first partition portion on the heat transfer portion of the plate provided with the first partition portion, from both ends of the plate to the center of the plate Extending in the direction, dividing the upstream side and the downstream side of the first fluid flow path at both ends of the plate, and communicating the partition at a second communication portion provided at the center of the plate Formed second And a cut portion. The first partition portion and the second partition portion are each formed by causing the plate to bulge into the first fluid flow path. The first partition portion and the second partition portion are each permanently joined to plates facing each other across the first fluid flow path.

  According to the plate heat exchanger of the present invention, the first partition portion and the second partition portion are alternately formed in the heat transfer portion of the plate, and the first fluid flow paths are alternately arranged at both ends and the center of the plate. And communicate with each other. As a result, in the first fluid flow path, two meandering flow lines symmetrical with respect to the center of the flow path (that is, the center line in the longitudinal direction of the plate) can be formed between the plates. The flow path can be shortened to avoid an increase in pressure loss, and the flow rate can be increased by reducing the cross-sectional area of the flow path, so that the heat exchange performance can be improved.

An example of the plate type heat exchanger of this invention is shown. It is a perspective view which shows an example of the structure of the plate in the plate type heat exchanger of this invention. It is an expansion perspective view of a plate. It is an expansion perspective view of a plate. It is the perspective view which laminated | stacked the plate. FIG. 6 is a partial cross-sectional view of the stacked plates of FIG. 5. FIG. 6 is a partial cross-sectional view of the stacked plates of FIG. 5. FIG. 6 is a partial cross-sectional view of the stacked plates of FIG. 5. It is explanatory drawing of a 1st fluid flow path. It is explanatory drawing of a 2nd fluid flow path. It is explanatory drawing of the heat exchange of a plate. It is a partial cross section figure of a plate. It is a partial cross section figure of a plate. It is an expansion perspective view of a plate. It is a top view which shows an example of the structure of a plate. It is a top view which shows another example of the structure of a plate. It is a top view which shows another example of the structure of a plate. It is a figure explaining the technique used as the background which this inventor examined.

(First embodiment)
FIG. 1 shows an example of a plate heat exchanger 1 according to the present invention. In particular, FIG. 1 (A) is a perspective view showing the external appearance, and FIG. 1 (B) is a perspective view showing an outline of the internal structure. It is.

  As shown in FIG. 1A, the plate heat exchanger 1 has a structure in which a plurality of plates (heat transfer plates) 2 are stacked. The plate 2 is formed, for example, by press-molding a flat plate of a stainless alloy or a titanium alloy into a shape described later.

  As shown in FIG. 1B, the first fluid flow paths R1 and the second fluid flow paths R2 are alternately formed between the adjacent plates 2. The first fluid channel R1 is a channel through which the first fluid flows. The second fluid channel R2 is a channel through which the second fluid flows. The first fluid and the second fluid exchange heat through the heat transfer section 30 (see FIG. 2) of the plate 2 existing therebetween. Thereby, any one fluid is heated (or cooled) by the other fluid.

  For example, when the plate heat exchanger 1 is used for heating hot water in a bathtub, the hot water of the bathtub (a heated medium including dirt) flows as the first fluid in the first fluid flow path R1, and the second fluid flow A clean heating medium (hot water or steam) as the second fluid flows through the path R2. Further, for example, when the plate heat exchanger 1 is used as a condenser, water (a medium to be cooled including dirt) flows through the first fluid channel R1 and flows into the second fluid channel R2. Flows a clean heating medium (high temperature medium) as the second fluid.

  In the plate heat exchanger 1, contamination or the like rarely becomes a problem in both the first fluid and the second fluid, and it is almost always a problem in only one of them. Therefore, in this example, as will be described later, a fluid (first fluid) that may contain dirt or the like is circulated through the first fluid flow path R1 that is less likely to be contaminated and that can be easily cleaned. On the other hand, a clean fluid (second fluid) is circulated through the second fluid channel R2.

  In FIG. 1B, the number of plates 2 is shown as six. However, in reality, the plate heat exchanger 1 has a large number of plates as shown in FIG. The number of plates 2 is as follows.

  FIG. 2 is a perspective view showing an example of the structure of the plate 2 in the plate heat exchanger 1 of the present invention. 3 and 4 are enlarged perspective views of the plate 2 (10a, 20a).

  FIG. 2 shows the structure of four adjacent plates 2 in FIG. The four plates 10a, 20a, 10b, and 20b are provided adjacent to each other in this order, and form a first fluid channel R1 and a second fluid channel R2.

  The plates 10a and 10b and the plates 20a and 20b have the same shape. Accordingly, the plate heat exchanger 1 of the present invention includes two types of plates. However, for example, the plate 10a and the plate 10b are different in the direction of the longitudinal direction in the case of being stacked (180 degrees different). The same applies to the plate 20a and the plate 20b. This will be described later.

  The plate 10a and the plate 20a form a first fluid flow path R1. The plate 20a and the plate 10b form a second fluid flow path R2. Further, the plate 10b and the plate 20b form a first fluid flow path R1. Lamination is repeated in this order using four plates 10a, 20a, 10b, and 20b as a unit. Accordingly, as described above, the plurality of first fluid flow paths R1 and the plurality of second fluid flow paths R2 are alternately formed.

  In FIG. 2, the first fluid flow path R1 is formed first and then the second fluid flow path R2 is formed. However, the order of formation is not limited to this. That is, conversely, the second fluid flow path R2 may be formed first (for example, the example of FIG. 1B).

  As shown in FIG. 2, the plates 10 a, 20 a, 10 b, and 20 b include a heat transfer section 30, a second fluid inlet 31, a second fluid outlet 32, a first fluid inlet 33, and a first fluid. The outlet 34, a plurality (seven in this example) of partition portions 35, and a plurality of uneven portions 36 are provided. The plurality of partition portions 35 and the plurality of uneven portions 36 are formed in the heat transfer portion 30. The plurality of partition portions 35 include a plurality (three in this example) of first partition portions 35a and a plurality (four in this example) of second partition portions 35b. In this example, the plurality of concave and convex portions 36 are formed such that a plurality of concave portions or a plurality of convex portions extend linearly. That is, it is formed as a plurality of concave stripes or convex stripes.

  Note that the second partition portion 35 b closest to the first fluid inlet 33 is provided with only one second partition portion 35 b that faces the first fluid inlet 33. The second partition part 35b closest to the first fluid outlet 34 is provided with only one second partition part 35b facing the first fluid outlet 34.

  Moreover, in this example, although the seven partition parts 35 are provided, the total number is not restricted to this. Therefore, the number of the first partition portions 35a and the second partition portions 35b is not limited to three and four. For example, one first partition part 35a and one second partition part 35b may be provided. Moreover, the number of the 1st partition parts 35a and the number of the 2nd partition parts 35b may be the same, or may differ. Therefore, the total number n of the partition portions 35 is an even number or an odd number. In any case, as will be described later, the first fluid flow path R1 is divided into (n-1) sections in the longitudinal direction of the plate 10a and the like. The dimensions of each compartment in the longitudinal direction are equal to each other in the example of FIG.

  Further, the second partition portion 35b closest to the first fluid inlet 33 may be omitted. The second partition 35b closest to the first fluid outlet 34 may also be omitted. In these cases, the total number n of the second partition portions 35b is 2, and the relationship of the number of sections is (n + 1).

  First, an outline of the structure of the plate 10a and the like will be described.

  The plate 10a is shown in FIG. 2 (A), and an enlarged view thereof is shown in FIG. In the plate 10a, the partition part 35 is formed in a straight line so as to protrude from the back surface of the plate 10a (the surface not shown in the figure, the same applies hereinafter). Therefore, the partition part 35 in the plate 10a is formed in a concave shape when viewed from the surface thereof.

  Further, in the plate 10a, the concavo-convex portion 36 includes a linear portion (protrusion) protruding on the surface of the plate 10a (surface shown in the figure, the same applies hereinafter), and a linear portion (concave protrusion) protruding on the back surface. Are alternately formed. Therefore, the projections and depressions 36 in the plate 10a are alternately formed with ridges and depressions when viewed from the surface. Here, the part (convex part) that appears as a convex line on the surface of the plate 10a is a concave line (or a concave part) when viewed from the back surface. The portion (concave portion) that appears as a concave strip on the surface of the plate 10a is a convex strip (or convex portion) when viewed from the back side. The extending direction of the uneven portion 36 is changed from the first direction to the second direction at the center of the longitudinal direction of the plate 10a. The first direction and the second direction are, for example, orthogonal directions. The above is the same for the other plates 20a, 10b, and 20b.

  In FIGS. 2A and 3, the uneven portion 36 of the plate 10 a is illustrated as a concave line.

  Furthermore, the 1st partition part 35a and the 2nd partition part 35b are each formed by expanding the plate 10a to 1st fluid flow path R1. The first partition part 35a and the second partition part 35b formed in this way are each permanently joined to the opposing plate 20a across the first fluid flow path R1.

  The above is the same for the other plates 20a, 10b, and 20b.

  The plurality of concavo-convex parts 36 are formed in regions other than the first partition part 35 a and the second partition part 35 b in the heat transfer part of the plate 2. For example, the plurality of concavo-convex portions 36 of the plate 10a are formed so as to come into contact with the convex portions of the adjacent plates 20a in the second fluid flow path R2. The plurality of concavo-convex portions 36 are each permanently joined to the convex portion of the adjacent plate 20a brought into contact with each other in the second fluid flow path R2 at the convex portion.

  Moreover, the height of the plurality of uneven portions 36 is formed lower than the height of the first partition portion 35a and the second partition portion 35b.

  The above is the same for the other plates 20a, 10b, and 20b.

  The plate 20a is shown in FIG. 2 (B), and an enlarged view thereof is shown in FIG. In the plate 20a, the partition part 35 is linearly formed so as to protrude from the surface of the plate 20a. Therefore, the partition part 35 in the plate 20a is formed in a protruding line when viewed from the surface thereof. Further, as described above, the projections and depressions are alternately formed on the plate 20a in the plate 20a. However, in FIG. 2B and FIG. It is illustrated as a ridge.

  As can be seen from a comparison between FIG. 3 and FIG. 4, the plate 20 a is formed so that the protruding direction of the partition portion 35 in the plate 10 a is reversed in the front and back direction (vertical direction in FIG. 2) of the plate 10 a. Has a shape. As described above, the plate 10a and the plate 20a are a pair of plates that form the first fluid flow path R1.

  Accordingly, in the first fluid flow path R1 formed by the plate 10a and the plate 20a, both of the plates 10a and the partition portion 35 of the plate 20a bulge inside the first fluid flow path R1. That is, the plate 10a and the plate 20a are bulged as described above to form the partition portion 35. Therefore, the partition part 35 may be considered to be a part of the plate 10a or the plate 20a. At this time, the position where the partition part 35 of the plate 10a and the plate 20a bulges is the same position as can be seen from the comparison between FIG. 3 and FIG. As a result, the partition portions 35 of the plate 10a and the plate 20a bulge at positions facing each other, and as a result, come into contact with each other and can be permanently joined as will be described later.

  Moreover, one uneven | corrugated | grooved part 36 of the plate 10a and the plate 20a is made not to contact the other uneven | corrugated | grooved part 36 in 1st fluid flow path R1. At this time, in the first fluid flow path R1, the ridges in which the concavo-convex portions 36 of the plate 10a and the plate 20a bulge are used as the first fluid flow path R1 without being permanently joined therebetween, as will be described later. Therefore, it is made to extend linearly in the same direction.

  The plate 10b is shown in FIG. In the plate 10b, the partition part 35 is linearly formed so as to protrude from the back surface of the plate 10b. Accordingly, the partition portion 35 in the plate 10b is formed in a concave shape when viewed from the surface thereof. Further, as described above, the projections and depressions are alternately formed on the plate 10b as described above.

  As can be seen from the comparison between FIG. 2A and FIG. 2C, the plate 10b is used after being rotated 180 degrees so that the plate 10a is opposite in the longitudinal direction (lamination). ) At this time, the positions of the second fluid inlet 31 and the like are left as they are. That is, the opening present at the position is used as the second fluid inlet 31 or the like. Since the details of the shape of the plate 10b are clear from the relationship with the plate 10a and FIG. 3, the enlarged illustration is omitted.

  The plate 20b is shown in FIG. In the plate 20b, the partition part 35 is linearly formed so as to protrude from the surface of the plate 20b. Therefore, the partition part 35 in the plate 20b is formed in a protruding line when viewed from the surface thereof. Further, as described above, the projections and depressions are alternately formed in the uneven portion 36 on the plate 20b.

  As can be seen from the comparison between FIG. 2B and FIG. 2D, the plate 20b is used after being rotated 180 degrees so that the plate 20a is opposite in the longitudinal direction (lamination). ) At this time, the positions of the second fluid inlet 31 and the like are left as they are. That is, the opening present at the position is used as the second fluid inlet 31 or the like. Since the details of the shape of the plate 20b are clear from the relationship with the plate 20a and FIG. 4, the enlarged illustration is omitted.

  As described above, the plate 20a and the plate 10b are a pair of plates that form the second fluid flow path R2. Accordingly, in the second fluid flow path R2 formed by the plate 20a and the plate 10b, both the partition portions 35 of the plates 20a and 10b bulge outside the second fluid flow path R2. That is, in contrast to the partition portion 35 of the plate 10a and the plate 20a, it swells in the opposite direction at the same position.

  Further, one uneven portion 36 of the plate 20a and the plate 10b is brought into contact with the other uneven portion 36 in the second fluid flow path R2. At this time, in the second fluid flow path R2, the ridges on which the concavo-convex portions 36 of the plate 20a and the plate 10b bulge are different directions (perpendicular directions) in order to permanently join them as will be described later. It extends in a straight line, and intersects at a predetermined position. As a result, the ridges on which the concavo-convex portions 36 of the plate 20a and the plate 10b bulge come into contact with each other at a predetermined position where they intersect, and can be permanently joined as will be described later.

  The plate 10b and the plate 20b are a pair of plates that form the first fluid flow path R1. The space between the plate 10b and the plate 20b is formed as the first fluid flow path R1 similarly to the space between the plate 10a and the plate 20a. The partition part 35 and the uneven | corrugated | grooved part 36 are also the same as the relationship between the plate 10a and the plate 20a.

  Next, the some partition part 35 in the plate 10a etc. is demonstrated. Hereinafter, the plate 10a will be described, but the same applies to the other plates 20a, 10b, and 20b.

  For example, in the plate 10a, as shown in FIGS. 2A and 3, the plurality of first partition portions 35a and the plurality of second partition portions 35b are in the longitudinal direction (long side) of the plate 10a. Are alternately formed.

  The plurality of first partition portions 35a extend from the center of the plate 10a in the direction of both ends of the plate 10a. The plurality of first partition portions 35a are prevented from reaching both ends of the plate 10a. Thus, the plurality of first partition portions 35a partition the upstream side and the downstream side of the first fluid flow path R1 at the center of the plate 10a, and connect the partitions at both ends of the plate 10a. A portion that communicates the section at both ends of the plate 10a is referred to as a first communication portion.

  Here, one end of the plate 10a is one side in the longitudinal direction (long side) of the plate 10a, and the side (end portion) on the side where the second fluid outlet 32 and the first fluid outlet 34 are provided. ) The other end of the plate 10a is one side in the longitudinal direction of the plate 10a and is the side (end) on the side where the second fluid inlet 31 and the first fluid inlet 33 are provided. That is, the both ends of the plate 10a refer to one end and the other end of the plate 10a. The center of the plate 10a refers to a position that bisects the plate 10a in the direction (width direction) perpendicular to the longitudinal direction (long side) of the plate 10a. The plate 10a has a shape with rounded rectangular corners. The first partition part 35a is provided so as to be orthogonal to the long side of the rectangle.

  As can be seen from FIG. 2 and the like, the partition portions 35a and 35b have a predetermined length in the width direction of the plate 10a. Therefore, in practice, both ends of the plate 10a may be considered as a region where most of the length of the partition portion 35b exists. Further, the center of the plate 10a may be considered as a region where most of the length of the partition portion 35a exists. On the other hand, in the width direction of the plate 10a, it may be considered that the region where the partition portions 35a and 35b overlap is neither at both ends nor at the center.

  In the plate 10a, as will be described later, the fluid flowing in the first fluid flow path R1 flows in from the first fluid inlet 33 and immediately collides with the first partition portions 35a and 35b. Need to be made. That is, the first fluid inlet 33 and the first partition portions 35a and 35b need to be provided to face each other. On the other hand, the 2nd fluid inflow port 31 does not need to be such a relationship with the partition parts 35a and 35b.

  The plurality of second partition portions 35b extend from both ends of the plate 10a toward the center of the plate 10a. The plurality of second partition portions 35b are prevented from reaching the center of the plate 10a. Accordingly, the plurality of second partition portions 35b partition the upstream side and the downstream side of the first fluid flow path R1 at both ends of the plate 10a, and communicate the partition at the center of the plate 10a. A portion that communicates the section at the center of the plate 10a is referred to as a second communication portion.

  Next, the plurality of uneven portions 36 in the plate 10a and the like will be described. Hereinafter, the plate 10a will be described, but the same applies to the other plates 20a, 10b, and 20b.

  The plurality of concavo-convex parts 36 are formed in the plate 10a in regions other than the first partition part 35a and the second partition part 35b in the heat transfer part 30 of the plate 10a.

  The plurality of uneven portions 36 are formed so as not to contact the protrusions of the uneven portions 36 of the adjacent plates in the first fluid flow path R1. Therefore, for example, the convex portion of the uneven portion 36 of the plate 10a is prevented from contacting the convex portion of the uneven portion 36 of the plate 20a. In addition, the convex part said here is a convex part seen from 1st fluid flow path R1. That is, it is a portion that bulges toward the first fluid flow path R1 side of the uneven portion 36.

  The projections (projections) of the concavo-convex portion 36 of the plate 10a and the plate 20a are formed so as to intersect at a predetermined angle (obliquely) with respect to the first partition portion 35a and the second partition portion 35b. The predetermined angle is, for example, an acute angle (45 degrees). On the other hand, the direction in which the first fluid flows in the first fluid flow path R1 is parallel to the first partition portion 35a and the second partition portion 35b, as will be described later. Accordingly, the projections (projections) of the concavo-convex portion 36 of the plate 10a and the plate 20a intersect the first fluid flow path obliquely at a predetermined angle. As a result, the first fluid generates a moderate turbulent flow without forming a so-called short pass. As a result, heat exchange can be performed efficiently in the heat transfer section 30.

  In addition, the plurality of concavo-convex portions 36 are formed so as to come into contact with the convex portions of the adjacent plates in the second fluid flow path R2. Therefore, for example, the convex portion of the uneven portion 36 of the plate 20a comes into contact with the convex portion of the uneven portion 36 of the plate 10b. In addition, the convex part said here is a convex part seen from 2nd fluid flow path R2. That is, it is a portion that bulges to the second fluid flow path R2 side of the uneven portion 36.

  The convex portions of the concave and convex portions 36 that are in contact with each other in the second fluid flow path R2 are permanently joined as will be described later. However, since the fluid in the second fluid flow path R2 is a clean fluid that does not include dirt or the like, there is no problem even if the flow stagnates at the part of the permanent joint. There is no need to clean.

  In the second fluid flow path R2, for example, the convex portions of the concave and convex portions 36 of the plate 20a may be formed so as not to contact the convex portions of the concave and convex portions 36 of the plate 10b. In this case, the two are not permanently joined. However, the heat transfer efficiency in the heat transfer section 30 can be improved by forming the uneven portion 36 on the plate 20a or the like.

  Next, with reference to FIGS. 5-10, the permanent joining of the partition part 35 in the plate 10a etc. and the permanent joining of the uneven | corrugated | grooved part 36 are demonstrated.

  FIG. 5 shows a state in which the four plates 10a, 20a, 10b, and 20b having the above structure are stacked in this order. Actually, as shown in FIG. 1B, a larger number of plates 2 are stacked.

  FIG. 6 shows a partial cross-sectional view taken along the line AA in FIG. 5, FIG. 7 shows a partial cross-sectional view taken along the line BB, and FIG. 8 shows a partial cross-sectional view taken along the CC cut line. .

  As shown in FIGS. 6, 7, and 8, the first partition part 35 a and the second partition part 35 b are formed so as to swell and contact the first fluid flow path R <b> 1 at the same position. Is done. In addition, for example, as shown in FIGS. 6, 7 and 8, the first partition part 35a of the plate 10a is connected to the second partition part 35b of the adjacent plate 20a in the first fluid flow path R1. These are permanently joined to each other by the brazing material 40a. Thereby, the 1st partition part 35a and the 2nd partition part 35b are united, and form the partition part 35. FIG. For example, the partition portion 35 and its permanent joint appear remarkably on the center side in FIG. 7 and on both sides in FIG. Moreover, the area | region where the 1st partition part 35a and the 2nd partition part 35b are permanently joined is shown with the oblique line in the figure of the lower stage of FIG.

  The permanent joining is performed by brazing (welding) using a known copper plate (or copper foil), for example (the same applies to others). The means for permanent joining is not limited to this, and other means such as welding may be used.

  By permanent joining of the partition portions 35a and 35b, the upstream side and the downstream side of the first fluid channel R1 can be reliably partitioned in the first fluid channel R1, and the overall strength is ensured. be able to. Furthermore, in 1st fluid flow path R1, the space | interval of the adjacent plates 10a and 20a can be correctly maintained, for example by making the partition parts 35a and 35b contact each other.

  The 1st partition part 35a and the 2nd partition part 35b can also be made into various shapes other than the shape described above.

  For example, in the above-described example, the first partition portion 35a is provided on both of the plates (for example, the plates 10a and 20a) facing each other with the first fluid flow path R1 interposed therebetween. However, you may make it provide the 1st partition part 35a only in one of the plates which oppose on both sides of 1st fluid flow path R1. For example, the first partition portion 35a may be provided only on the plate 10a and not provided on the plate 20a (the reverse may be true). Even in this case, the distance between the plate 10a and the plate 20a is made equal to the above-described example. Accordingly, the height of the first partition portion 35a is twice the height in the above example (the dimension in the direction of the interval, the same applies hereinafter).

  Further, in the above-described example, for example, the height of the first partition portion 35a of the plate 10a facing each other across the first fluid flow path R1 is set to be equal to the height of the first partition portion 35a of the plate 20a. It is done. However, the height of the first partition portion 35a of the plate 10a may be different from the height of the first partition portion 35a of the plate 20a. Even in this case, the distance between the plate 10a and the plate 20a is made equal to the above-described example. Therefore, if the ratio of the height of the first partition portion 35a of the plate 10a to the height of the first partition portion 35a of the plate 20a is 5: 5 in the above example, this ratio is 1: 9 to 9: 1 may be used.

  The same applies to the second partition portion 35b. That is, the second partition portion 35b is provided on the plate provided with the first partition portion 35a in the same manner as the first partition portion 35a.

  The projections and depressions 36 of the plate 20a are permanently joined at the projections by the brazing material 40b and the projections of the projections and depressions 36 of the adjacent plate 10b that are in contact with each other in the second fluid flow path R2. The uneven portion 36 and its permanent joint appear prominently on, for example, both sides of FIG. 7 and the central side of FIG. In addition, a region where the convex portion of the concave-convex portion 36 is permanently joined is represented by hatching in the lower diagram of FIG.

  By permanent joining at the convex portions of the plurality of concave and convex portions 36, the overall strength can be ensured in the second fluid flow path R2. Moreover, in 2nd fluid flow path R2, the space | interval of adjacent plate 20a and 10b can be correctly maintained by making several uneven | corrugated | grooved parts 36 mutually contact with the convex part.

  As shown in FIGS. 6, 7, and 8, the heights (depths) of the plurality of uneven portions 36 are made lower (shallow) than the height of the first partition portion 35 (35 a and 35 b). That is, the interval between the two plates constituting the first fluid flow path R <b> 1 can be made sufficiently wide in the region other than the first partition portion 35. Further, the interval between the two plates constituting the second fluid flow path R <b> 2 can be sufficiently widened in the region of the first partition portion 35.

  Note that, as shown in FIGS. 7 and 8, the adjacent plates 2 are permanently joined to each other at the peripheral edge portion. For example, the plate 10a is permanently joined to the plate 20a by the brazing material 40a at the bent portions (peripheral portions) at both ends thereof. Thereby, the fluid is prevented from leaking to the outside from between the adjacent plates 2. Thus, according to this invention, it is not necessary to provide the collar part for permanent joining in a peripheral part. Therefore, the plate-type heat exchanger of the present invention can be manufactured by a simple manufacturing method as compared with a plate-type heat exchanger having a collar portion.

  As described above, in the plate heat exchanger 1, as shown in FIGS. 1B, 6, 7, and 8, the flow paths at both ends of the plurality of stacked plates 2 are the second fluid flow paths R2. It is said. In this case, as shown in FIGS. 6, 7, and 8, the plurality of uneven portions 36 are joined in the second fluid flow path R <b> 2. In other words, between the adjacent plates 2, both ridges and ridges intersect diagonally and are permanently joined to each other at the intersecting points. As a result, in the second fluid flow path R2, the adjacent plates 2 are permanently joined at a number of points, as shown in FIGS. Thereby, the both ends of plate type heat exchanger 1, and the whole intensity can be secured.

  As a result, even when a large pressure of the first fluid acts on the first fluid flow path R1, it is possible to receive pressure on the two plates 2 that are permanently joined (that is, the second fluid flow path R2).

  FIG. 9 shows the permanent joint (and the first fluid flow path R1 therebetween) between the plate 10a and the plate 20a. FIG. 10 shows the permanent joint (and the second fluid flow path R2 therebetween) between the plate 20a and the plate 10b.

  As shown in FIG. 9, around the second fluid inflow port 31, the plate 10 a and the plate 20 a are brought into close contact with each other and permanently joined. Although not shown, the second fluid outlet 32 is the same. Thereby, between the plate 10a and the plate 20a, the 2nd fluid inflow port 31 and the 2nd fluid outflow port 32 are completely isolate | separated from 1st fluid flow path R1 which the plate 10a and the plate 20a form. As a result, the second fluid is not mixed with the first fluid between the plate 10a and the plate 20a.

  Further, as shown in FIG. 10, the plate 20a and the plate 10b are brought into close contact with each other around the first fluid outlet 34 and are permanently joined. Although not shown, the first fluid inlet 33 is the same. Thereby, between the plate 20a and the plate 10b, the 1st fluid inflow port 33 and the 1st fluid outflow port 34 are completely isolate | separated from 2nd fluid flow path R2 which the plate 20a and the plate 10b form. As a result, the first fluid is not mixed with the second fluid between the plate 20a and the plate 10b.

  As shown in FIG. 1B, cover plates 3 and 4 are laminated on the outer sides of both ends of the laminated plates 2 and are permanently joined to the plate 2. No opening is provided in the rear cover plate 3. The front cover plate 4 is provided with four openings. As shown in FIGS. 1A and 1B, a nozzle (or connection) 51 is provided in the opening corresponding to the second fluid inflow port 31, and a nozzle 52 is provided in the opening corresponding to the second fluid outflow port 32. However, the nozzle 53 is attached to the opening corresponding to the first fluid inlet 33, and the nozzle 54 is attached to the opening corresponding to the first fluid outlet 34.

  Next, the flow of the fluid in the plate heat exchanger 1 of the present invention will be described.

  In the first fluid flow path R1, the flow path of the first fluid flowing through the inside of the first fluid flow path R1 flows from the first fluid inlet 33 and enters the first permanently joined partition portion 35b. Change the direction to reach the second permanently joined partition part 35a, change the direction along this, and thereby split into two equal flows, the both ends of the plates 10a and 20a (First communication part) is reached. The number of the partition parts 35a and 35b shall be counted in order from the upstream side in the first fluid flow path R1. Hereinafter, the direction of flow of the fluid is changed in the same manner, and the third partition 35b, the center of the plates 10a and 20a (second communication portion), the fourth partition 35a, the plates 10a and 20a. Both ends (first communication portion), the fifth partition portion 35b, the center of the plates 10a and 20a (second communication portion), the sixth partition portion 35a, both ends of the plates 10a and 20a (first Flows in the order of communication part). In the second communication portion, the two flows that are equally divided upstream join together. At this time, as a result of the equal lengths of the flow paths of the two flows up to that point, there is no temperature difference between them, so that the heat exchange performance is not impaired. Furthermore, the direction is changed so as to follow the terminal end portion of the heat transfer section 30 and the seventh partition section 35b, and the first fluid outlet 34 is reached and flows out therefrom.

  Accordingly, in the first fluid flow path R1 through which a fluid that may contain dirt or the like flows, the flow of the first fluid is a flow parallel to the partition portions 35a and 35b, and also at both ends of the plates 10a and 20a. Parallel flow. In addition, in the first fluid flow path R1, the plurality of concavo-convex portions 36 are formed so as not to contact the convex portions of the adjacent plates. Therefore, the first fluid flow path R1 does not have a portion where stagnation occurs and does not have a portion where a fibrous foreign matter or the like is caught. Thereby, even if dirt etc. are mixed in the 1st fluid, these can be discharged from now, without accumulating inside the 1st fluid channel R1. Further, since no stagnation occurs when the inside of the first fluid flow path R1 is washed, the inside can be washed almost completely. Further, since no stagnation occurs in the first fluid flow path R1, it is possible to prevent the first fluid from freezing even when the first fluid is cooled to near 0 ° C. or below 0 ° C. it can.

  In addition, in the first fluid flow path R1, the fluid flowing inside the first fluid flow path R1 crosses the plurality of uneven portions 36 existing in the middle of the flow path. Thereby, the said fluid produces moderate turbulent flow, without forming what is called a short path. As a result, heat exchange can be performed efficiently in the heat transfer section 30.

  On the other hand, in the second fluid flow path R2, due to the structure as described above, the flow path of the second fluid that flows inside the second fluid flow path R2 flows in from the second fluid inlet 31 and is substantially at both ends and the center of the plates 20a and 10b. Are alternately circulated to reach the second fluid outlet 32 existing on the diagonal line, and flow out of the second fluid outlet 32.

  In this flow path, the second fluid abuts on a portion where the convex portions of the plurality of concave and convex portions 36 are permanently joined to each other, and passes through the left and right branches. However, since the second fluid is a clean fluid as described above, there is no problem even if it hits the portion of the permanent joint.

  As described above, in the plate heat exchanger of the present invention, the first fluid flows while forming two line-symmetrical meandering flows between the plates, while the second fluid does not meander between the plates. Flowing. At this time, the flow of the first fluid and the second fluid is basically a flow that intersects diagonally (oblique AC), and there is a portion where the flow is partially orthogonal. That is, there is no portion where the flow of the first fluid and the second fluid becomes a parallel flow.

  In contrast, in an evaporator for a refrigeration apparatus and a plate heat exchanger for a condenser (hereinafter referred to as a plate heat exchanger for a condenser), for example, both the first fluid and the second fluid pass between the plates. There is a type that flows while meandering, and in which the flow of the first fluid and the second fluid is a parallel flow. However, since the plate type heat exchanger of this type is greatly reduced in the efficiency of heat exchange, in the plate type heat exchanger for home use, bath use, etc. in which the plate type heat exchanger of the present invention is used, For practical reasons, it cannot be adopted.

  The relationship of each element in the heat exchanger is represented by Q = K · ΔT · A. Here, Q is the amount of exchange heat, K is the heat passage rate, ΔT is the temperature difference between the first fluid and the second fluid, and A is the heat transfer area. The highly efficient heat exchanger is reduced in size by reducing the heat transfer area A while ensuring the value of the exchange heat quantity Q.

  FIG. 11 is an explanatory diagram of temperature conditions for heat exchange of the plate. In particular, FIG. 11 (A) is an explanatory diagram of temperature conditions when the first fluid and the second fluid are in counterflow, and FIG. B) is an explanatory diagram of temperature conditions when the first fluid and the second fluid are in parallel flow.

  For example, in the case where the second fluid is the high temperature side and the first fluid is the low temperature side and the first fluid and the second fluid are in the counterflow (hereinafter referred to as counterflow), as shown in FIG. It is. Here, T1: second fluid inlet temperature, T2: second fluid outlet temperature, T3: first fluid outlet temperature, T4: first fluid inlet temperature. In this case, the operation (use) under the temperature condition of T3> T2 is possible, and it is often used under such conditions.

  On the other hand, in the case where the second fluid is the high temperature side and the first fluid is the low temperature side and the first fluid and the second fluid are in parallel flow (hereinafter referred to as parallel flow), as shown in FIG. It is. That is, the operation under the temperature condition of T3> T2 is impossible. Therefore, in the case of parallel flow, the efficiency of heat exchange is greatly reduced.

  Further, even when the operation is performed under the condition of T3 <T2, in the case of the counter flow, the temperature difference ΔT between the first fluid and the second fluid is ΔT = ((T1-T3) − (T2-T4)) / It is represented by (LN (T1-T3) / (T2-T4)). On the other hand, in the case of parallel flow, the temperature difference ΔT between the first fluid and the second fluid is ΔT = ((T1−T4) − (T2−T3)) / (LN (T1−T4) / (T2−T3)). It is represented by As can be seen from these comparisons, in the case of parallel flow, the temperature difference ΔT between the first fluid and the second fluid becomes small, and the efficiency of heat exchange decreases.

  In addition to the above, in a plate heat exchanger for a condenser, the heat exchange medium is intended for a refrigerant and is premised on a change in latent heat. This is due to the following reason. That is, for example, when the first fluid side is a refrigerant, the difference between the first fluid inlet temperature T4 and the first fluid outlet temperature T3 is small, and the difference between the temperature difference ΔT between the first fluid and the second fluid in the counter flow and the parallel flow is also small. Become. For this reason, the decrease in efficiency of heat exchange is not significant.

  However, in a plate heat exchanger that performs heat exchange between water and water, such as a plate heat exchanger for home use and a bath that uses the plate heat exchanger of the present invention, sensible heat change is not observed. Assumption. For this reason, the inlet temperature and the outlet temperature of both the first fluid and the second fluid vary greatly. Therefore, in the case of performing heat exchange between water and water, if there is a parallel flow over almost the entire region of the plate 2, even if only partly, as described above, the first fluid and the second fluid are exchanged. Since the temperature difference ΔT becomes small, the heat exchange efficiency decreases as a result.

  On the other hand, in the plate heat exchanger of the present invention, as described above, there is no portion where the flow of the first fluid and the second fluid becomes a parallel flow. Therefore, the temperature difference ΔT between the first fluid and the second fluid can have an effect close to the counter flow. As a result, the temperature difference ΔT between the first fluid and the second fluid remains large, and as a result, the efficiency of heat exchange does not decrease.

  When the width of the plate is small, the length of the first partition 35a extending from the center of the plate to both ends and the length of the second partition 35b extending from the ends of the plate to the center are very short. There may be.

(Second Embodiment)
FIG. 12 is a partial cross-sectional view taken along the line BB in another embodiment of the plate corresponding to FIG. 5, and FIG. 13 is a partial cross-sectional view taken along the line CC of the plate. Note that a partial cross-sectional view taken along the line AA of the plate corresponding to FIG. 5 is omitted.

  As shown in FIGS. 12 and 13, the first partition part 35a and the second partition part 35b are formed so as to bulge and contact the first fluid flow path R1 at the same position. In addition, for example, as shown in FIGS. 12 and 13, the first partition part 35 a of the plate 10 a is connected to the second partition part 35 b of the adjacent plate 20 a and the brazing material in the first fluid flow path R <b> 1. 40a is permanently joined to each other.

  The projections and depressions 36 of the plate 20a are permanently joined at the projections by the brazing material 40b and the projections of the projections and depressions 36 of the adjacent plate 10b that are in contact with each other in the second fluid flow path R2. The uneven part 36 and its permanent joint appear prominently, for example, on both sides of FIG. 12 and the central side of FIG.

  The concavo-convex portion 36 of the plate 20a is permanently joined to the convex portion by the brazing material 40a and the convex portion of the concavo-convex portion 36 of the adjacent plate 10a brought into contact with each other in the first fluid flow path R1. . The uneven part 36 and its permanent joint appear prominently, for example, on both sides of FIG. 12 and the central side of FIG.

  As shown in FIGS. 12 and 13, the height of the plurality of uneven portions 36 is equal to the height of the first partition portion 35 a and the second partition portion 35 b. That is, the adjacent plates 2 are permanently joined at a number of points, as shown in FIGS. Thereby, the whole intensity | strength of the plate type heat exchanger 1 is securable.

  As shown in FIGS. 12 and 13, adjacent plates 2 are permanently joined to each other by brazing material 40 a or 40 b at the periphery. Thereby, the fluid is prevented from leaking to the outside from between the adjacent plates 2.

(Third embodiment)
In another example of the plate structure in the plate heat exchanger 1 of the present invention, the plurality of partition portions 35 are provided in the same manner as in the example of FIG. 1, and a plurality of recessed portions ( You may make it form a depression part or several convex part (protrusion part). The concave portion or the convex portion (so-called dimple shape) is, for example, conical or hemispherical. That is, the shape of the concavo-convex portion 36 is not limited to a linear shape, and may be various shapes such as a conical shape and a hemispherical shape. Even with such an uneven portion 36, the fluid generates an appropriate turbulent flow without forming a so-called short path. As a result, heat exchange can be performed efficiently in the heat transfer section 30.

(Fourth embodiment)
FIG. 14 is a perspective view showing still another example of the plate structure in the plate heat exchanger 1 of the present invention. FIG. 14 is an enlarged perspective view of the plate 2 (20a), and corresponds to FIG.

  14, the width of the second partition portion 35b is formed so as to be wider at the one end and the other end (both ends) side of the plate 20a than at the center side of the plate 20a (this point is shown in FIGS. 4 and 5). It is the same in).

  FIG. 14 shows only the plate 20a. However, as described above, the plates 10a and 10b and the plates 20a and 20b have the same shape that satisfies a predetermined relationship. Accordingly, in the other plates 20b, 10a, and 10b, the widths of the first and second partition portions 35a and 35b are the same as those of the plate 20a.

  The first fluid changes its direction by 180 ° at one end and the other end of the second partition portion 35b. For this reason, the flow of the first fluid tends to stagnate at one end and the other end of the second partition portion 35b. Therefore, the width of the root of the second partition portion 35b (for example, the side in contact with one end or the other end of the plate 20a) is the width of the tip portion (for example, the side not in contact with one end or the other end of the plate 20a, the root It is formed to be wider than the width of the opposite side. Thereby, it can be set as the structure where a 1st fluid does not flow into the said part, it can eliminate that the flow of a 1st fluid stagnates, and, thereby, the volume of an impurity can be suppressed.

  In particular, the flow of the first fluid is more likely to stagnate in the portion facing the first fluid inlet 33 and the portion facing the first fluid outlet 34. Therefore, in particular, in FIG. 14, the width of the root of the second partition portion 35 b facing the first fluid inlet 33 and the first fluid outlet 34 is larger than the width of the root of the other second partition portion 35 b. Is also formed to be wide. Thereby, it is possible to eliminate the stagnation of the flow of the first fluid in the vicinity of the inlet and the outlet of the first fluid flow path R1.

  In FIG. 14, the width of the base of the second partition portion 35 b facing each of the first fluid inlet 33 and the first fluid outlet 34 is equal to the root of the other second partition 35 b. Although wider than the width, the roots of all the second partition portions 35b may have the same structure as shown in FIG.

(Fifth embodiment)
15 is a plan view showing an example of a plate structure in the plate heat exchanger 1 of the present invention, and corresponds to an enlarged perspective view of the plate shown in FIG. In particular, FIG. 15A is a diagram showing the interval between the partition portions 35 and the length of the communication portion, and FIG. 15B is a diagram illustrating the flow of the first fluid in the plate corresponding to FIG. It is explanatory drawing.

  Here, in FIGS. 15A and 15B, the upstream side is the first fluid inlet 33 side when viewed from the longitudinal direction of the plates 10a and 20a, and the downstream side is the longitudinal direction of the plates 10a and 20a. It is assumed that the first fluid outlet 34 side is seen from the direction. The same applies to FIGS. 16 and 17 described later. Hereinafter, the first partition portion 35a is referred to as a partition portion 35a, and the second partition portion 35b is referred to as a partition portion 35b.

  As shown in FIG. 15A, the plurality of partition portions 35a extend from the center of the plate 10a toward the opposite ends of the plate 10a to the heat transfer portion of the plate 10a (and 20a). The partition part 35a partitions the upstream side and the downstream side of the first fluid flow path R1 at the center of the plate 10a, and communicates the partition at the first communication part S provided at both ends of the plate 10a. The length of the 1st communication part S is made equal to the space | interval m of the adjacent partition part 35a and the partition part 35b.

  In addition, the space | interval m of the adjacent partition part 35a and the partition part 35b is a dimension in the longitudinal direction of the plate 10a, as shown in FIG. Moreover, the length of the 1st communication part S and the length of the other communication part mentioned later are the dimensions in the transversal direction of the plate 10a, as shown in FIG. The same applies to FIGS. 16 and 17.

  As shown in FIG. 15A, the plurality of partition portions 35b extend from both ends of the plate 10a toward the center of the plate 10a. The partition part 35b partitions the upstream side and the downstream side of the first fluid flow path R1 at both ends of the plate 10a, and communicates the partition at the second communication part t provided at the center of the plate 10a. The length of the 2nd communication part t is made into twice the space | interval m of the adjacent partition part 35a and the partition part 35b.

  Hereinafter, the operation of the fluid in the first fluid flow path R1 of the plates 10a and 20a shown in FIG. 15A will be described with reference to FIG.

  The first fluid flows in from the first fluid inlet 33 on the upstream side, and changes the flow direction along the partition portion 35 b (first) facing the first fluid inlet 33. The fluid further reaches the both ends of the plates 10a and 20a by changing the flow direction along the second partition portion 35a that is spaced m from the first partition portion 35b. In the fluid, the first meandering flow changes the flow direction along the first communication portion S on one end side, and the second meandering flow is along the first communication portion S on the other end side. Change the direction of flow. Therefore, the fluid has at least two meandering flows in the first fluid flow path R1. In addition, an order with the 1st partition part 35b, the 2nd partition part 35a, etc. from an upstream is shown, and it is the same also about the other partition parts 35a and 35b. The same applies to FIGS. 16 and 17 described later.

  Next, the fluid changes the flow direction along the third partition part 35b that is spaced m from the second partition part 35a, reaches the center of the plates 10a and 20a, and reaches the second communication part t. Change the direction of flow along. Similarly, the flow of the fluid is changed in the direction of the flow in the same way between the ends and the center of the plates 10a and 20a, and the seventh portion facing the end portion of the heat transfer section 30 and the first fluid outlet 34 is further changed. The direction is changed along the partition portion 35b, and the first fluid outlet 34 on the downstream side is reached and flows out from here.

  According to the structure of the plate of this example, as shown in FIG. 15B, since two or more meandering flows can be formed in the first fluid flow path R1, the cross-sectional area of the flow path can be reduced. it can. Moreover, since the length of the 2nd communication part t is twice the space | interval m of the adjacent partition part 35a and the partition part 35b, the increase in the pressure loss by the flow velocity becoming too large in the 1st communication part S Can be prevented. Furthermore, since the 1st communication part S exists in both ends, the performance fall by the flow velocity becoming too small in the 2nd communication part t can be prevented.

(Sixth embodiment)
FIG. 16 is a plan view showing another example of the plate structure in the plate heat exchanger 1 of the present invention. In particular, FIG. 16A is a diagram showing the interval between the partition portions 35 and the length of the communication portion, and FIG. 16B is a diagram illustrating the flow of the first fluid in the plate corresponding to FIG. It is explanatory drawing.

  As shown in FIG. 16 (A), the plurality of partition portions 35a further include central communication portions U and W for communicating the upstream and downstream sections of the first fluid flow path R1 at the center of the plate 10a. Formed as follows. In the partition part 35a, the length of the 1st communication part S is equal to the space | interval m of the adjacent partition part 35a and the partition part 35b.

  In the partition part 35a located on the most upstream side and the most downstream side of the first fluid flow path R1 in the heat transfer part of the plate 10a (and 20a), the length of the central communication part U is equal to that of the adjacent partition part 35a. It is equal to or smaller than the distance m from the portion 35b. On the other hand, in the other partition part 35a of the plate 10a, the length of the center communication part W is set to twice the distance m between the adjacent partition part 35a and the partition part 35b.

  As shown in FIG. 16A, the plurality of partition parts 35b further divide the second communication part V into the center of the plate 10a and the upstream and downstream sides of the first fluid flow path R1. 35b 'is formed. In the partition part 35b, the lengths of the two second communication parts V are each twice the distance m between the adjacent partition part 35a and the partition part 35b.

  Hereinafter, the operation of the fluid in the first fluid flow path R1 of the plates 10a and 20a shown in FIG. 16A will be described with reference to FIG.

  The first fluid flows in from the first fluid inlet 33 on the upstream side, and changes the direction of the flow along the first partition portion 35 b facing the first fluid inlet 33. The fluid further changes the flow direction along the second partition portion 35a which is spaced m from the first partition portion 35b, reaches the center of the plates 10a and 20a, and the first meandering flow of the fluid Changes the direction of flow along the central communication portion U. Further, the second and third meandering flows of the fluid change the flow direction along the second partition portion 35a and reach both ends of the plates 10a and 20a, respectively, along the first communication portion S. Change the direction of flow. Therefore, the fluid has at least three meandering flows in the first fluid flow path R1.

  Next, the first to third meandering flows of the fluid change the flow direction along the third partition portion 35b and the central partition portion 35b ′, respectively, and reach the center of the plates 10a and 20a. The flow direction is changed along the two communicating portions V. In the same manner, the direction of the flow is changed in order between both ends and the center of the plates 10a and 20a, and the terminal portion 35b facing the terminal portion of the heat transfer section 30 and the first fluid outlet 34 is further changed. The direction is changed so that the first fluid outlet 34 on the downstream side is reached and flows out from here.

  In addition, as shown to FIG. 16 (A), it is the center communication part W in the 4th and 6th partition part 35a, and is the center communication part U in the 2nd and 8th partition part 35a. In the example of FIGS. 16A and 16B, the length of the central communication portion U is assumed to be smaller than the length of the central communication portion W.

  As described above, according to this example, as shown in FIG. 16B, three or more meandering flows can be formed in the first fluid flow path R1. By configuring a plurality of meandering flows in the plate in this way, the length (path) of each meandering flow can be shortened, that is, an appropriate length. As a result, it is possible to prevent excessive pressure loss without reducing the flow velocity. In addition, according to the present invention, since a short path is not generated, performance is not deteriorated.

(Seventh embodiment)
FIG. 17 is a plan view showing still another example of the plate structure in the plate heat exchanger 1 of the present invention. In particular, FIG. 17A is a diagram illustrating the interval between the partition portions 35 and the length of the communication portion, and FIG. 17B is a diagram illustrating the flow of the first fluid in the plate corresponding to FIG. It is explanatory drawing.

  In the heat transfer section of the plate 10a (and 20a), intervals m # 1 to m # 6 between adjacent partition sections 35a and partition sections 35b are respectively the first fluid flow paths as shown in FIG. It is formed differently on the upstream side and downstream side of R1. Specifically, for example, the size relationship is (interval) m # 1 <m # 2 <m # 3 <m # 4 <m # 5 <m # 6.

  Further, the lengths of the first communication portions S # 1 to S # 3 are different between the upstream side and the downstream side of the first fluid flow path R1, respectively, as shown in FIG. As shown in FIG. 17A, the lengths of the communication portions t # 1 and t # 2 are formed so as to be different on the upstream side and the downstream side of the first fluid flow path R1, respectively. Specifically, for example, the size relationship is S # 1 (length) <S # 2 <S # 3 and t # 1 (length) <t # 2.

  Hereinafter, the operation of the fluid in the first fluid flow path R1 of the plates 10a and 20a shown in FIG. 17A will be described with reference to FIG.

  The first fluid flows in from the first fluid inlet 33 on the upstream side, and changes the direction of the flow along the first partition portion 35 b facing the first fluid inlet 33. The fluid further changes the flow direction along the second partition portion 35a that is separated from the first partition portion 35b by the distance m # 1, reaches the both ends of the plates 10a and 20a, and reaches the first communication portion S. Change the direction of flow along # 1.

  Next, the fluid changes the flow direction along the third partition part 35b spaced apart from the second partition part 35a by the distance m # 2, reaches the center of the plates 10a and 20a, and reaches the second communication part. Change the direction of flow along t # 1. Hereinafter, similarly, the direction of the flow is changed in order between the both ends and the center of the plates 10a and 20a (between m # 3 to m # 6), and the end portion of the heat transfer unit 30 and the first fluid outlet are further changed. The direction is changed along the seventh partition 35b facing 34, and reaches the first fluid outlet 34 on the downstream side, and flows out from here.

  Assume that the plate having the structure shown in FIG. 17A as described above is used in an evaporator for a vapor compression refrigeration cycle, for example. When the first fluid is used as a refrigerant in the evaporator, the refrigerant flows in from the first fluid inlet 33 on the upstream side, and the vaporization of the refrigerant proceeds, that is, the first partition portion 35a and the second portion become more downstream. The cross-sectional area can be widened by widening the distance from the partition portion 35b. Thereby, it becomes possible to always obtain an appropriate flow rate, and it is possible to reduce the pressure loss without deteriorating the heat transfer performance. The fluid inlet passage (first fluid inlet 33) is not limited to the lower side shown in FIG.

  In addition, the number of central communication parts and central partition parts is not limited to one, and a plurality of central communication parts and a plurality of central partition parts may be provided.

  For example, in FIG. 16, one central communication portion U and W provided in each partition portion 35a is provided, but a plurality of central communication portions U and W may be provided. One or a plurality of central communication parts U and W are provided so as to maintain right and left objectivity with respect to the longitudinal center line of the plate 10a. Therefore, the number of central communication parts U and W is an odd number.

  In addition, one central partition portion 35b 'provided in each partition portion 35b is provided, but the number thereof may be plural. The one or more central partition portions 35b 'are provided so as to maintain the right and left object with respect to the longitudinal center line of the plate 10a. Therefore, the number of central partition portions 35b 'is an odd number.

  Moreover, you may provide the 1 or several center communication part W also about the partition part 35a of the plate 10a of the Example shown in FIG. Even in this case, as described above, it is provided so as to keep the right and left objects with respect to the center line in the longitudinal direction of the plate 10a. Accordingly, the number of central communication portions W is an odd number. Further, the length of the central communication portion W provided in each partition portion 35a in this case is provided from the upstream side to the downstream side, similarly to the relationship with the lengths of the second communication portions t # 1 and t # 2. The longer the relationship, the longer it may be.

DESCRIPTION OF SYMBOLS 1 Plate type heat exchanger 2 Plate 10a, 20a, 10b, 20b Plate 30 Heat transfer part 31 2nd fluid inflow port 32 2nd fluid outflow port 33 1st fluid inflow port 34 1st fluid outflow port 35a 1st partition part 35b 2nd partition part 36 Concave-convex part 40a, 40b Brazing material

Claims (12)

A plurality of plates are stacked, and the adjacent plates are permanently joined at their peripheral portions, and a first fluid flow path through which the first fluid flows and a second fluid flow through which the second fluid flows between the adjacent plates. In a plate-type heat exchanger in which paths are alternately formed and the first fluid and the second fluid exchange heat through the heat transfer section of the plate between them,
One or both of the heat transfer portions of the plate facing each other across the first fluid flow path extend from the center of the plate toward both ends of the plate, and upstream of the first fluid flow path at the center of the plate. A first partition portion that is formed so as to partition the side and the downstream side, and to communicate the partition at the first communication portion provided at both ends of the plate;
A second partition portion formed alternately with the first partition portion on the heat transfer portion of the plate provided with the first partition portion, from both ends of the plate toward the center of the plate Extending to partition the upstream side and the downstream side of the first fluid flow path at both ends of the plate, and to connect the partition at a second communication portion provided at the center of the plate. A second partition part,
The first partition portion and the second partition portion are each formed by causing the plate to bulge into the first fluid flow path,
The plate-type heat exchanger, wherein the first partition portion and the second partition portion are each permanently joined to a plate facing each other across the first fluid flow path. The first partition portion is further formed to include a central communication portion that communicates the upstream and downstream sections of the first fluid flow path at the center of the plate,
The second partition part is further formed in the second communication part so as to include a central partition part that divides the upstream side and the downstream side of the first fluid flow path in the center of the plate. The plate heat exchanger according to claim 1, wherein In the first partition portion located on the most upstream side and the most downstream side of the first fluid flow path in the heat transfer portion of the plate, the length of the central communication portion is adjacent to the first partition portion. The plate-type heat exchanger according to claim 2, wherein the plate-type heat exchanger is equal to or smaller than an interval between the first partition portion and the second partition portion. The length of the first communication portion is equal to the interval between the adjacent first partition portion and the second partition portion, and the length of the second communication portion is adjacent to the first communication portion. It is twice the space | interval of a partition part and a 2nd partition part. The plate type heat exchanger of Claim 1 characterized by the above-mentioned. 2. The plate heat exchanger according to claim 1, wherein a width of the second partition portion is formed to be wide at both end sides of the plate. The interval between the first partition portion and the second partition portion in the heat transfer portion of the plate is different between the upstream side and the downstream side of the first fluid flow path. 4. The plate heat exchanger according to any one of 3 above. A plurality of concavo-convex portions formed in regions other than the first partition portion and the second partition portion in the heat transfer portion of the plate, which are in contact with the convex portions of the plate adjacent to each other in the second fluid flow path. A plurality of concavo-convex portions formed so that the plurality of concavo-convex portions are respectively in the convex portions thereof and the convex portions of the adjacent plates brought into contact with each other in the second fluid channel. The plate heat exchanger according to any one of claims 1 to 6, wherein the plate heat exchanger is permanently joined. The plate-type heat exchanger according to claim 7, wherein heights of the plurality of uneven portions are equal to heights of the first partition portion and the second partition portion. The plurality of concavo-convex portions are further formed so as to come into contact with the convex portions of the plates adjacent to each other in the first fluid flow path, and the plurality of concavo-convex portions are each in the convex portions, the first The plate-type heat exchanger according to claim 8, wherein the projections of the adjacent plates brought into contact with each other in the fluid flow path are permanently joined to each other. The plate-type heat exchanger according to claim 7, wherein heights of the plurality of uneven portions are lower than heights of the first partition portion and the second partition portion. 11. The plate heat exchanger according to claim 8, wherein the plurality of concave and convex portions are formed so as not to contact a convex portion of the adjacent plate in the first fluid flow path. The first and second fluid flow paths formed alternately by the plurality of stacked plates, the flow paths at both ends thereof are configured by the second fluid flow paths. Item 12. The plate heat exchanger according to any one of items 11 to 11.

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