JP5025783B2 - Evaporator and refrigeration system provided with the evaporator - Google Patents

Description

  The present invention relates to an evaporator for exchanging heat between a single component refrigerant, a refrigerant such as an azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, a non-azeotropic refrigerant mixture, and a heat exchange fluid such as water, and the evaporation The present invention relates to a refrigeration system equipped with a container.

  Conventionally, there are various types of evaporators employed in refrigeration systems (refrigeration cycles), and as one of them, as shown in FIG. 10, a plurality of heat transfer plates 1 '..., 2' ... are stacked. The first flow path R1 ′ for flowing the refrigerant CM ′ in the liquid state or the gas-liquid mixed state and the second flow path R2 ′ for flowing the heat exchange fluid W ′ are each heat transfer plates 1 ′, 2 ′,. Those formed alternately on the boundary are well known (for example, see Patent Document 1).

  Such an evaporator A ′ is a so-called plate heat exchanger, and is formed by connecting openings H1 ′, H2 ′, H3 ′, and H4 ′ formed at both ends of each heat transfer plate 1 ′ and 2 ′. The refrigerant inflow path 31a ′ and the refrigerant outflow path 31b ′ for allowing the refrigerant CM ′ to flow into and out of the first flow path R1 ′ are formed at both ends of the heat transfer plates 1 ′ and 2 ′, and the second flow path R2 ′. A heat exchange fluid inflow passage 32a ′ and a heat exchange fluid outflow passage 32b ′ through which the heat exchange fluid W ′ flows in and out are formed at both ends of the heat transfer plates 1 ′ and 2 ′.

  In such an evaporator A ′, the flow direction of the refrigerant CM ′ flowing through the first flow path R1 ′ and the flow direction of the heat exchange fluid W ′ flowing through the second flow path R2 ′ are opposite to each other (a counter flow). ), The refrigerant inflow path 31a ′, the refrigerant outflow path 31b ′, the heat exchange fluid inflow path 32a ′, and the heat exchange fluid outflow path 32b ′ are arranged.

  Thus, the evaporator A ′ configured as described above causes the heat exchange fluid W ′ to flow through the second flow path R2 ′ while flowing the refrigerant CM ′ in the liquid state or the gas-liquid mixed state through the first flow path R1 ′. Thus, the refrigerant CM ′ and the heat exchange fluid W ′ exchange heat, and the refrigerant CM ′ in the first flow path R1 ′ evaporates and the heat exchange fluid W ′ in the second flow path R2 ′ cools. It has come to be.

  By the way, the refrigeration system provided with the evaporator A ′ having the above configuration generally condenses the refrigerant CM ′ discharged from the refrigerant outflow passage 31b ′ of the evaporator A ′ by the compressor and then condenses it by the condenser. It is configured to be supplied again to the evaporator A ′, but if the refrigerant CM ′ discharged from the evaporator A ′ (refrigerant CM ′ supplied to the compressor) contains liquid, the compressor will be damaged. There is a possibility that the refrigerant CM ′ is completely evaporated during the heat exchange between the refrigerant CM ′ and the heat exchange fluid W ′ in the evaporator A ′ (while the refrigerant CM ′ flows through the first flow path R1 ′). And the refrigerant CM ′ completely gasified is discharged from the evaporator A ′.

Japanese Patent No. 4554025

  However, if the refrigerant CM ′ is completely evaporated in the first flow path R1 ′, and the gasified refrigerant CM ′ is discharged from the evaporator A ′, the refrigerant CM ′ flows in the downstream area of the first flow path R1 ′. There is a problem that the cooling effect on the heat exchange fluid W ′ in the refrigerant (substantially completely gasified refrigerant) CM ′ is reduced and the heat exchange efficiency is lowered.

  More specifically, when the heat transfer plates 1 ′ and 2 ′ are wetted by the refrigerant CM ′, the heat transfer plates 1 ′ and 2 ′ and the heat exchange fluid W ′ are caused by the latent heat of vaporization accompanying the evaporation of the refrigerant CM ′. However, since the refrigerant CM ′ that is almost completely gasified has almost no latent heat of vaporization, the heat transfer plates 1 ′ and 2 ′ and the heat exchange fluid W ′ cannot be efficiently cooled. .

  Therefore, the conventional refrigeration system (evaporator A ′) is almost used for cooling the heat exchange fluid W ′ in which the refrigerant CM ′ flowing in the downstream area in the first flow path R1 ′ flows in the second flow path R2 ′. There is a problem that heat exchange efficiency is reduced without contributing.

  Accordingly, in view of such circumstances, the present invention provides an evaporator that can efficiently cool a heat exchange fluid and that can discharge a completely gasified refrigerant, and a refrigeration system including the evaporator. The issue is to provide.

  In the evaporator according to the present invention, the first flow path for circulating the refrigerant and the second flow path for circulating the heat exchange fluid are alternately formed with each of the plurality of stacked heat transfer plates as a boundary. The refrigerant inflow path and the refrigerant outflow path for allowing the refrigerant to flow in and out of the one flow path are formed at an interval in one direction so as to pass through the region where the first flow path is formed, and In the evaporator formed in such a manner that the heat exchange fluid inflow passage and the heat exchange fluid outflow passage through which the heat exchange fluid flows in and out through the region where the second flow path is formed are spaced apart in the one direction. A partition extending in the other direction orthogonal to the one direction is provided between one surface of the opposing heat transfer plates, and on one side of the one direction between the surfaces of the heat transfer plate with the partition as a boundary. One of the heat transfer plates is formed while the second flow path is formed. On the other side of the one direction between the two surfaces, a third flow path is formed for flowing a heated fluid having a temperature higher than that of the heat exchange fluid, while a first flow path is formed between the other surfaces of the heat transfer plates facing each other. And a heating fluid inflow path for allowing the heating fluid to flow into and out of the third flow path and a heating fluid outflow path through the region where the third flow path is formed, It is formed so that it may pass through the area | region in which a 2nd flow path is formed, and it is formed so that a refrigerant | coolant outflow path may pass through the area | region in which a 3rd flow path is formed.

  According to the evaporator having the above configuration, the refrigerant inflow path is formed (arranged) so as to pass through the area where the second flow path is formed, and the refrigerant outflow path is passed through the area where the third flow path is formed. The first flow path formed between the other surfaces of the heat transfer plate is formed to face the second flow path and the third flow path with the heat transfer plate interposed therebetween. become.

  Therefore, the refrigerant that has flowed into the first flow path from the refrigerant flow path exchanges heat with the heat exchange fluid in the entire second flow path, and also exchanges heat with the heating fluid that flows through the third flow path.

  That is, the evaporator having the above-described configuration causes the second flow path of the heat transfer plate to flow through the gas-liquid mixed state refrigerant that sufficiently contains the liquid component in the entire region corresponding to the second flow path in the first flow path. Since many corresponding regions are wetted with the refrigerant, the refrigerant in the first flow path and the heat exchange fluid in the entire second flow path exchange heat. In other words, the heat exchange fluid in the entire second flow path is cooled by the latent heat of vaporization accompanying the evaporation of the refrigerant attached to many areas corresponding to the second flow path of the heat transfer plate. Therefore, the evaporator configured as described above can efficiently cool the entire heat exchange fluid flowing through the second flow path without forming a region where it is difficult for the refrigerant and the heat exchange fluid to exchange heat. it can.

  Then, as described above, when the refrigerant in the gas-liquid mixed state sufficiently containing the liquid component is circulated in the entire region corresponding to the second channel in the first channel, the refrigerant circulated in the first channel is The gas-liquid mixed state containing the liquid component also enters the area corresponding to the third flow path from the area corresponding to the flow path, but the heated fluid having a temperature higher than the heat exchange fluid is circulated through the third flow path. The refrigerant flowing through the first flow path and the heated fluid flowing through the third flow path exchange heat so that the refrigerant in the first flow path rapidly evaporates and is completely gasified. It will be discharged from the outflow channel. Therefore, when the evaporator having the above-described configuration is employed in a refrigeration system, the heat exchange fluid can be efficiently cooled, and damage to the compressor provided in the subsequent stage can be prevented.

  As one aspect of the present invention, each heat transfer plate is formed with partitioning ridges extending in the other direction orthogonal to the one direction on one surface facing each other, and the partitioning portion of the heat transfer plates facing each other. It may be formed by welding in a state where the partitioning ridges are in surface contact with each other. In this way, since a wide partition portion is formed between the second flow path and the third flow path, the heat exchange fluid flowing in the second flow path flows in the third flow path. It is prevented from being affected by the heat of the heated fluid having a high temperature.

  As another aspect of the present invention, the refrigerant inflow path, the refrigerant outflow path, the heat exchange fluid inflow path, and the heat exchange fluid outflow path are aligned in the one direction at a central portion in the other direction of the heat transfer plate. May be arranged. In this way, the flow of the refrigerant in the first flow path and the flow of the heat exchange fluid in the second flow path can be made uniform.

  As another aspect of the present invention, any one of the heat exchange fluid outflow passage or the heat exchange fluid inflow passage disposed on the third flow path side has an elliptical shape in which a cross-sectional shape has a long axis in the one direction. May be formed. If it does in this way, a refrigerant can be circulated smoothly in the 1st channel. That is, if any one of the heat exchange fluid outflow path or the heat exchange fluid inflow path exists in a region where the refrigerant having evaporated by heat exchange with the heat exchange fluid in the second flow path flows. Prevents the flow of refrigerant and increases pressure loss. However, the cross-sectional shape of either the heat exchange fluid outflow passage or the heat exchange fluid inflow passage arranged on the third flow path side is formed in an elliptical shape having a major axis in one direction (longitudinal direction of the refrigerant). Then, since the minor axis is positioned in the other direction, the range that hinders the circulation of the refrigerant is narrowed. As a result, the refrigerant can be smoothly circulated without increasing the pressure loss.

  The refrigeration system according to the present invention includes an evaporator for exchanging heat between the refrigerant and the heat exchange fluid, a compressor for pressurizing the refrigerant discharged from the evaporator, and a condensation for condensing the refrigerant compressed by the compressor. A refrigeration system configured to supply the refrigerant condensed in the condenser to the evaporator, wherein the evaporator is constituted by any of the evaporators described above, and the refrigerant is supplied to the first flow path. In a state of being circulated, the heat exchange fluid is circulated through the second flow path, and the heating fluid having a temperature higher than that of the heat exchange fluid is circulated through the third flow path. According to the refrigeration system, since any one of the evaporators is used, the same operations and effects as the evaporator can be achieved.

  As described above, according to the evaporator of the present invention, the heat exchange fluid can be efficiently cooled, and the excellent effect that the completely gasified refrigerant can be discharged can be obtained.

  Further, according to the refrigeration system of the present invention, since the evaporator is provided, the heat exchange fluid can be efficiently cooled, and the excellent effect that the completely gasified refrigerant can be discharged. Can play.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic perspective view of the evaporator which concerns on one Embodiment of this invention, Comprising: (a) says the schematic perspective view seen from the front side of the evaporator, (b) saw from the back side of the evaporator. A schematic perspective view is shown. The schematic disassembled perspective view of the state which abbreviate | omitted the heat-transfer plate in the intermediate position of the evaporator which concerns on the same embodiment is shown. It is explanatory drawing of one heat-transfer plate employ | adopted as the evaporator which concerns on the embodiment, Comprising: (a) shows the front view seen from the one surface side of the heat-transfer part, (b) The rear view seen from the other surface side of the heat part is shown. It is explanatory drawing of the other heat-transfer plate employ | adopted as the evaporator which concerns on the embodiment, Comprising: (a) shows the front view seen from the other surface side of the heat-transfer part, (b) shows heat-transfer. The rear view seen from the one surface side of a thermal part is shown. (A) shows the partial expanded sectional view of the partition part vicinity of the evaporator which concerns on the embodiment, (b) is the elements on larger scale of the junction part of the heat exchanger plates which comprise the evaporator which concerns on the embodiment. Annular projections provided around the openings (first opening, second opening, third opening, fourth opening, fifth opening, sixth opening) (first annular protruding parts, second annular The schematic of the part which joined convex parts, 3rd annular convex parts, 4th annular convex parts, 6th annular convex parts) is shown. It is the figure which added the flow of the refrigerant | coolant, the heat exchange fluid, and the heating fluid to the longitudinal cross-sectional view of the evaporator which concerns on the embodiment, Comprising: (a) is the 1st flow path in a 1st path | pass area | region and a 2nd path | pass area | region. (B) shows a cross-sectional view in the second flow path in the first path region, and (c) shows a cross-sectional view in the second flow path in the second pass region. . The schematic system diagram of the refrigerating system (air conditioner) which employ | adopted the evaporator which concerns on the embodiment is shown. The whole perspective view of the condenser employ | adopted as the refrigeration system shown in FIG. 7 is shown. FIG. 9 is a longitudinal sectional view of the condenser shown in FIG. 8, wherein (a) is a longitudinal sectional view of a portion where the cooling water inflow passage and the cooling water outflow passage communicate with each other through the cooling water passage; b) shows a longitudinal sectional view of a portion where the refrigerant inflow passage and the refrigerant outflow passage communicate with each other through the refrigerant flow passage. The schematic exploded perspective view of the conventional evaporator employ | adopted as a refrigerating system is shown.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

  The evaporator which concerns on this embodiment is for implement | achieving a refrigerating cycle, and is employ | adopted as one structure of the refrigerating system mounted in an air conditioner, a refrigerator, etc.

  Such an evaporator is a so-called plate heat exchanger, and includes a plurality of stacked heat transfer plates 1, 2,... As shown in FIGS. Each of the heat transfer plates 1 and 2 is formed by press-molding a metal plate (a plate made of a stainless alloy in the present embodiment). As shown in FIGS. In the embodiment, the heat transfer portions 10 and 20 have a rectangular shape in plan view, and annular portions 11 and 21 extending from the outer periphery of the heat transfer portions 10 and 20 in a direction intersecting the heat transfer portions 10 and 20. The heat transfer portions 10 and 20 face each other in a state where the annular portions 11 and 21 of the adjacent heat transfer plates 1 and 2 are fitted to each other (see FIG. 2).

  In the present embodiment, each of the heat transfer plates 1 and 2 is arranged such that the heat transfer portions 10 and 20 are divided into two regions in one direction as shown in FIGS. 3 (a) and 4 (b). On one surface of the heat parts 10 and 20, partitioning ridges 100 and 200 extending in the other direction orthogonal to one direction are formed. In addition, in FIGS. 3-6, the part (The partition protrusion 100,200 and the 1st thru | or 6th annular convex part mentioned later) protruded from the heat-transfer parts 10 and 20 is hatched.

  In the present embodiment, the heat transfer plates 1 and 2 are arranged on one surface of the heat transfer portions 10 and 20 facing each other in a stacked state (hereinafter referred to as the longitudinal direction of the heat transfer plates 1 and 2). , Extending in the short direction). Since each of the heat transfer plates 1 and 2 is formed by press-molding a metal plate as described above, the other surface (the back surface of one surface) of the heat transfer portions 10 and 20 has a partition. Corrugations (grooves) extending in the lateral direction are formed in correspondence with the projecting ridges 100 and 200 (see FIGS. 3B and 4A).

  Thereby, the heat-transfer parts 10 and 20 of each heat-transfer plate 1 and 2 are two area | region A1 in a longitudinal direction bordering on the protruding protrusions 100 and 200 (and the recessed line formed in the back surface side). It is partitioned into A2.

  As shown in FIG. 5A, the partitioning ridges 100 and 200 according to the present embodiment have a flat top, and the partitioning ridges 100 and 200 of the adjacent heat transfer plates 1 and 2 are formed. The tops (planes) are in surface contact with each other. The partitioning ridges 100 and 200 divide between one surface of the heat transfer plates 1 and 2 into two flow paths (second flow path R2 and third flow path R3 to be described later) through which fluids having different temperatures flow. This is for forming the partition portion 30. Therefore, the length in the longitudinal direction of the top portions (planes) of the partitioning ridges 100, 200 is such that each of the fluids flowing through the second flow path R2 and the third flow path R3 is not easily affected by the heat of the other party ( It is preferable to form the wide partition portion 30 by setting the width as wide as possible. For example, the heat transfer plates 1 and 2 are made of austenitic stainless alloy (thermal conductivity 16 W / mk), When brazing the strips 100 and 200 (planar tops) with copper (thermal conductivity 370 W / mk), the width (heat transfer plates 1 and 2) of the tops (planes) of the partitioning projections 100 and 200 The length in the longitudinal direction) may be 1 mm or more.

  Returning to FIG. 3A and FIG. 4B, the partitioning ridges 100 and 200 are biased toward one end side in the longitudinal direction (one direction) of the heat transfer plates 1 and 2 (heat transfer portions 10 and 20). It is provided at the position. That is, the partitioning ridges 100 and 200 are provided on one end side of the center of the heat transfer units 10 and 20 in the longitudinal direction. Thereby, the heat-transfer parts 10 and 20 are the other end side rather than the area | region (henceforth 1st area | region) A1 of the one end side of a longitudinal direction among the two area | regions divided by the protruding protrusions 100 and 200 for partitioning. A region (hereinafter referred to as a second region) A2 is widened. The length in the longitudinal direction of the second region A2 is the flow path length necessary for circulating the heat exchange fluid W such as water (the flow path length necessary for heat exchange between the refrigerant CM and the heat exchange fluid W). ) Set above.

  As described above, the evaporator A according to this embodiment includes the annular portion 11 that extends from the outer periphery of the heat transfer portions 10 and 20 in the direction in which the heat transfer plates 1 and 2 intersect the heat transfer portions 10 and 20. , 21, of the heat transfer plates 1 and 2 adjacent to each other, one of the heat transfer plates 1 has a partitioning ridge 100 on the extending side of the annular portion 11 as shown in FIG. The other heat transfer plate 2 is formed such that the partitioning ridge 200 protrudes in the same direction as the annular portion 21 as shown in FIG. 4B. . That is, as shown in FIGS. 3 and 4, the evaporator A according to the present embodiment includes partitioning ridges 100 and 200 and openings (described below) (first opening H1, second opening H2, third opening H3, fourth). Annular projections (first annular projections 101, 201, second annular projections 102, 202, third annular projections 103, 203, fourth annular projection) around the opening H4, the fifth opening H5, and the sixth opening H6) Part 104, 204, fifth annular convex part 105, 205, sixth annular convex part 106, 206) are formed by alternately stacking two kinds of heat transfer plates 1, 2 having different projecting directions. (See FIG. 2).

  Each of the heat transfer plates 1 and 2 has a plurality of openings formed in the heat transfer portions 10 and 20. More specifically, each of the heat transfer plates 1 and 2 is provided with one large-diameter opening in the first region A1 and two smaller-diameter openings than the large-diameter opening. . Each of the heat transfer plates 1 and 2 is provided with three large-diameter openings in the second region A2 at intervals in the longitudinal direction of the heat transfer portions 10 and 20.

  The large-diameter openings provided in the first area A1 and the second area A2 are arranged on the heat transfer plates 1 and 2 (heat transfer plates 1 and 2 (heat transfer sections 10 and 20) on the center in the short direction of the heat transfer plates 1 and 2 (heat transfer sections 10 and 20). They are arranged in a row in the longitudinal direction of the heat parts 10, 20). In the following description, four openings (large-diameter openings provided in the first area A1 and the second area A2) aligned in a line in the longitudinal direction of the heat transfer plates 1 and 2 are defined as the heat transfer sections 10 and 20. The first opening H1, the second opening H2, the third opening H3, and the fourth opening H4 are sequentially called from one end side to the other end side, and the small-diameter opening in the first region A1 is the fifth opening H5 and the fourth opening H4. Let it be a six-opening H6.

  Said 1st opening H1 is arrange | positioned in the position biased to the one end side of the longitudinal direction of the heat-transfer parts 10 and 20 in 1st area | region A1. Of the second opening H2, the third opening H3, and the fourth opening H4 in the second region A2, the second opening H2 is disposed on one end side in the longitudinal direction of the heat transfer sections 10 and 20 in the second region A2. The third opening H3 and the fourth opening H4 are arranged on the other end side in the longitudinal direction of the heat transfer parts 10 and 20 in the second region A2.

  The fifth opening H5 and the sixth opening H6 are arranged on both sides of the first opening H1 in the first region A1. In the present embodiment, the fifth opening H5 and the sixth opening H6 are arranged in a line in the short direction of the heat transfer units 10 and 20.

  The first opening H1, the third opening H3, the fourth opening H4, the fifth opening H5, and the sixth opening H6 are each formed in a substantially circular shape, while the second opening H2 is the heat transfer plate 1. , 2 are formed in an elliptical shape with a major axis set in the longitudinal direction.

  In the heat transfer portions 10 and 20 of the heat transfer plates 1 and 2, the first opening H1, the second opening H2, the third opening H3, the fourth opening H4, the fifth opening H5, and the sixth opening H6 are independent. Thus, annular convex portions 101, 102, 103, 104, 105, 106, 201, 202, 203, 204, 205, 206 are formed. In the following description, each annular protrusion 101, 102, 103, 104, 105, 106, 201, 202, 203, 204, 205, 206 is associated with each of the first opening H1 to the sixth opening H6. Annular projections 101, 201, second annular projections 102, 202, third annular projections 103, 203, fourth annular projections 104, 204, fifth annular projections 105, 205, sixth annular projection 106, 206.

  As shown in FIG. 3A and FIG. 4B, each of the heat transfer plates 1 and 2 includes the first annular protrusions 101 and 201 and the third annular protrusions 103 and 203 as one of the heat transfer parts 10 and 20. 4 (surface on which partitioning ridges 100 and 200 are formed), and as shown in FIGS. 3B and 4A, the second annular protrusions 102 and 202, the fourth annular protrusion 104, 204, fifth annular protrusions 105, 205 and sixth annular protrusions 106, 206 are provided on the other surface of the heat transfer parts 10, 20.

  As shown in FIGS. 3 and 4, in the present embodiment, the first opening H1, the third opening H3, the fourth opening H4, the fifth opening H5, and the sixth opening H6 are each formed in a substantially circular shape. Therefore, the first annular convex portions 101 and 201, the third annular convex portions 103 and 203, the fourth annular convex portions 104 and 204, the fifth annular convex portions 105 and 205, and the sixth annular convex portions 106 and 206, respectively. Are formed in an annular shape corresponding to the corresponding openings H1, H2, H3, H4. On the other hand, since the 2nd cyclic | annular convex parts 102 and 202 have the 2nd opening H2 formed in the elliptical shape, they have comprised the elliptical cyclic | annular form by which the long axis was set to the longitudinal direction of the heat exchanger plates 1 and 2. .

  Then, as shown in FIG. 5 (b), the heat transfer plates 1 and 2 are stacked in a stacked state on the one surface side of the adjacent heat transfer plates 1 and 2 facing each other. The first annular projections 101 and 201 and the third annular projections 103 and 203 are in contact with each other over the entire circumference, and the corresponding annular projections (second annular projections) are also provided on the other surface facing each other. Portions 102 and 202, fourth annular convex portions 104 and 204, fifth annular convex portions 105 and 205, and sixth annular convex portions 106 and 206) are in contact with each other over the entire circumference. . As a result, the heat transfer plates 1 and 2 have corresponding openings (first openings H1..., Second openings H2..., Third openings H3..., Fourth openings H4. ..., the sixth openings H6 ...) are connected to each other.

  Further, as shown in FIGS. 3 (a) and 4 (b), one surface of each heat transfer plate 1, 2 is along a part of the other end side in the longitudinal direction of the outer periphery of the second opening H2. Guide convex portions 107 and 207 are formed. The guide convex portions 107 and 207 are formed in an arc shape in plan view outside the second annular convex portions 102 and 202, and the opening center of the second opening H2 (the center of curvature of the second annular convex portions 102 and 202). ) And two imaginary lines connecting the two ends are formed in a range where the angle θ is 60 ° to 120 ° (preferably 80 ° to 90 °).

  As shown in FIGS. 3B and 4A, the other surface of each of the heat transfer plates 1 and 2 is a guide that partially surrounds at least one end in the longitudinal direction of the third opening H3. Protrusion portions 108 and 208 are provided. The guide convex portions 108 and 208 according to the present embodiment are formed in an arc shape in which the center of curvature is set at a position offset toward the other end side in the longitudinal direction with respect to the opening center of the third opening H3. Both ends in the direction are formed so as to open at the other end side in the longitudinal direction with a space from the periphery of the fourth opening H4 (fourth annular convex portions 104, 204).

  In this embodiment, a pair of side guide convex portions 109 and 209 extending from both ends of the guide convex portions 108 and 208 to both sides of the fourth opening H4 is formed. The pair of side guide convex portions 109 and 209 are formed so as not to reach the other end in the longitudinal direction of the heat transfer portions 10 and 20, and the distance between them increases toward the other end in the longitudinal direction. It is formed to do.

  Each of the heat transfer plates 1 and 2 has a plurality of recesses and protrusions (not shown) alternately formed in the first region A1 and the second region A2 of the heat transfer parts 10 and 20. In the state where each heat transfer plate 1 and 2 is laminated, the protrusions of the heat transfer portions 10 and 20 of the adjacent heat transfer plates 1 and 2 intersect each other, and between the laminated heat transfer plates 1 and 2. A space through which fluid can flow is formed. That is, in the evaporator A, a space in which fluid can flow is formed between the opposing ridges by the ridges of the adjacent heat transfer plates 1 and 2 crossing each other.

  In the evaporator A according to this embodiment, the adjacent heat transfer plates 1 and 2 are permanently joined by brazing. That is, as shown in FIG. 5, the evaporator A according to the present embodiment has a contact portion between adjacent heat transfer plates 1 and 2 (partition ridges 100 and 200, annular portions 11 and 21, first annular projections). Parts 101, 201, second annular convex parts 102, 202, third annular convex parts 103, 203, fourth annular convex parts 104, 204, fifth annular convex parts 105, 205, sixth annular convex part The portions 106 and 206, the guide convex portions 107 and 207, the guide convex portions 108 and 208, the side guide convex portions 109 and 209, and the contact points where the ridges contact) are brazed, and the opening H1 , H2, H3, H4, H5 and H6 and the outer periphery of the heat transfer parts 10 and 20 are sealed.

  Thereby, the evaporator A, as shown in FIG. 2 and FIG. 6, distributes the heat exchange fluid W through the first flow path R1 through which the refrigerant CM flows through each of the heat transfer plates 1 and 2. Two flow paths R2 are alternately formed.

  In the evaporator A according to the present embodiment, the partition projections 100 and 200 on one surface of the adjacent heat transfer units 10 and 20 are connected (brazed), whereby the heat transfer units 10 and 20 are connected. A partition portion 30 that divides one of the two surfaces into two in the longitudinal direction (one direction) is formed so as to extend in the short direction (the other direction orthogonal to the one direction). Then, as shown in FIG. 6 (a), the evaporator A extends over the entire length in the longitudinal direction between the other surfaces of the heat transfer sections 10 and 20 (all together with the first region A1 and the second region A2). The first flow path R1 is formed (in a region corresponding to the region), and as shown in FIGS. 6B and 6C, between the one surface of the heat transfer units 10 and 20 with the partition 30 as a boundary. A second flow path R2 for circulating the heat exchange fluid W is formed on the other end side in the longitudinal direction (region corresponding to the second region A2), and one end side in the longitudinal direction (region corresponding to the first region A1). A third flow path R3 is formed through which the heated fluid WM having a temperature higher than that of the heat exchange fluid W is circulated.

  Further, as shown in FIG. 6, the evaporator A according to the present embodiment has the first opening H1 of each of the heat transfer plates 1 and 2 connected and the third opening H3 connected to each of the first flow paths R1. A refrigerant inflow path 31a and a refrigerant outflow path 31b through which the refrigerant CM flows in and out are formed, and the second openings H2 of the heat transfer plates 1 and 2 are connected and the fourth opening H4 is connected, so that the second flow path R2 is connected. Thus, a heat exchange fluid inflow passage 32a and a heat exchange fluid outflow passage 32b through which the heat exchange fluid W flows in and out are formed.

  That is, in the evaporator A according to the present embodiment, the refrigerant inflow path 31a and the refrigerant outflow path 31b pass through the region where the first flow path R1 is formed, corresponding to the arrangement of the first opening H1 and the third opening H3. Are formed at intervals in the longitudinal direction of the heat transfer sections 10 and 20, and the heat exchange fluid inflow passage 32a and the heat exchange fluid outflow passage are provided corresponding to the arrangement of the second opening H2 and the third opening H3. 32b is formed at a predetermined interval in the longitudinal direction of the heat transfer sections 10 and 20 so as to pass through the region where the second flow path R2 is formed.

  As described above, the first opening H1, the second opening H2, the third opening H3, and the fourth opening H4 are aligned in the longitudinal direction at the center in the short direction of the heat transfer sections 10 and 20, and thus the refrigerant. The inflow path 31a, the refrigerant outflow path 31b, the heat exchange fluid inflow path 32a, and the heat exchange fluid outflow path 32b are also arranged in a line in the longitudinal direction at the center in the short direction of the heat transfer units 10 and 20. .

  In the present embodiment, a single component refrigerant, an azeotropic mixed refrigerant, or a pseudo azeotropic mixed refrigerant is employed as the refrigerant CM. Accordingly, in the evaporator A according to the present embodiment, the flow direction of the refrigerant CM flowing in the first flow path R1 and the heat exchange fluid W flowing in the second flow path R2 are the same direction (refrigerant CM). And the heat exchange fluid W are in parallel flow), the third opening H3 is connected to form the refrigerant inflow passage 31a, and the first opening H1 is connected to form the refrigerant outflow passage 31b. In the evaporator A, the fourth opening H4 of each of the heat transfer plates 1 and 2 is connected to form a heat exchange fluid inflow passage 32a, and the second opening H2 is connected to form a heat exchange fluid outflow passage 32b. Is formed.

  In the evaporator A according to this embodiment, the heating fluid inflow passage 33a and the heating fluid outflow passage 33b are formed by connecting the fifth openings H5 of the heat transfer plates 1 and 2 and the sixth opening H6. Yes. In the present embodiment, the fifth opening H5 and the sixth opening H6 are provided so as to form a line in the short direction of the heat transfer sections 10 and 20, and thus the heating fluid inflow path 33a and the heating fluid outflow path 33b. Are also arranged on both sides of the refrigerant outflow path 31b in a row in the short direction of the heat transfer sections 10 and 20.

  As shown in FIGS. 1 and 2, the evaporator A according to the present embodiment includes a plurality of laminated heat transfer plates 1 and 2 sandwiched between two frame plates 3 and 4. Then, as shown in FIG. 2, the first opening H1 and the third opening H3 corresponding to the refrigerant inflow path 31a and the refrigerant outflow path 31b are formed in one frame plate 3, and one small-diameter opening (heating) is formed. A fifth opening H5 that is a fluid outflow path 33b) is provided, and the other frame plate 4 has a second opening H2 and a second opening corresponding to the heat exchange fluid inflow path 32a and the heat exchange fluid outflow path 32b. A fourth opening H4 is formed, and a fifth opening H5 that is one small-diameter opening (an opening that becomes the heating fluid inflow passage 33a) is provided. Thus, the evaporator A according to the present embodiment is configured to allow the refrigerant CM to flow in and out from one frame plate 3 side, and to be configured to flow out the heat exchange fluid W from the other frame plate 4 side. Yes. Further, the evaporator A is configured to allow the heating fluid WM to flow from the other frame plate 4 side and to discharge the heating fluid WM from the one frame plate 3 side.

  In the present embodiment, the single heat transfer plate 2 located at a predetermined position (a position where the predetermined number of sheets are located) from one frame plate 3 is provided with only the sixth opening H6 as a small-diameter opening, and the heating fluid inflow The path 33a and the heated fluid outflow path 33b are reversed at a midway position. That is, the evaporator A according to this embodiment has a predetermined position (a predetermined number of sheets) from one frame plate 3 and the one frame plate 3 as shown in FIGS. 2, 6 (b) and 6 (c). The sixth opening H6 is connected to form the heating fluid inflow passage 33a and the fifth opening H5 is connected to the heating fluid outflow passage 33b. In the space between the other frame plate 4 and the heat transfer plate 2 at the predetermined position (second pass region Pa2), the fifth opening H5 is connected to form a heating fluid inflow passage 33a. The six fluid openings H6 are connected to form a heated fluid outflow passage 33b. Thereby, the evaporator A according to the present embodiment allows the heating fluid inflow passage 33a in the first pass region Pa1 and the heating fluid outflow in the second pass region Pa2 through the sixth opening H6 of the heat transfer plate 2 at a predetermined position. The path 33b is in a continuous state.

  In the evaporator A according to the present embodiment, the second opening H2 is formed in an elliptical shape in which the long axis is set in the longitudinal direction, and therefore the heat exchange fluid outflow passage 32b disposed on the third flow path R3 side. Is formed in an elliptical shape having a long axis in the longitudinal direction of the heat transfer plates 1 and 2. And since the 2nd cyclic | annular convex parts 102 and 202 surrounding the 2nd opening H2 have comprised the elliptical cyclic | annular form by which the long axis was set to the longitudinal direction, the sealing part (2nd 2nd) which exists in 1st flow path R1. The portion where the annular convex portions 102 and 202 are sealed is formed so that the short direction is narrower than the longitudinal direction of the heat transfer portions 10 and 20.

  In the evaporator A according to the present embodiment, as described above, the guide convex portions 107 and 207 of the heat transfer portions 10 and 20 facing each other are connected to each other, so that FIG. 6B and FIG. As shown in FIG. 2, a fluid guide portion 34 is formed between the one surface of the heat transfer plates 1 and 2 to partially surround the periphery of the heat exchange fluid outflow passage 32b on the other end side in the longitudinal direction.

  Further, in the evaporator A, the guide projections 108 and 208 are connected to each other, so that the refrigerant inflow passage 31a is provided between the other surfaces of the heat transfer plates 1 and 2 as shown in FIG. The guide part 35 which partially surrounds at least one end side in the longitudinal direction of the heat transfer plates 1 and 2 is formed.

  In the present embodiment, a pair of side guide convex portions 109 and 209 extending from both ends of the guide convex portions 108 and 208 are provided on the other surface of each of the heat transfer plates 1 and 2 so as to face each other. The side guide convex portions 109 and 209 on the other surface of the heat transfer portions 10 and 20 are connected (brazed), so that the guide is interposed between the other surfaces of the heat transfer plates 1 and 2. A pair of side guide portions 36a and 36b extending from both ends of the portion 35 to both sides of the heat exchange fluid inflow passage 32a are formed.

  The evaporator A according to the present embodiment is as described above, and is adopted as one configuration of the refrigeration system FS mounted on an air conditioner, a refrigerator, or the like as shown in FIG. Here, the case where it is employed in a refrigeration system FS mounted on an air conditioner will be described as an example.

  The refrigeration system FS includes the evaporator A, a compressor B that pressurizes the refrigerant CM discharged from the evaporator A, and a condenser C that condenses the refrigerant CM compressed by the compressor B. Yes.

  In the evaporator A, the refrigerant outflow path 31b is connected to the primary side of the compressor B through a pipe P. The evaporator A is connected via a pipe P to an indoor unit in which the heat exchange fluid inflow passage 32a and the heat exchange fluid outflow passage 32b are separately arranged indoors.

  That is, in the evaporator A, each of the heat exchange fluid inflow path 32a and the heat exchange fluid outflow path 32b is connected to the indoor unit, and the second flow path R2, the heat exchange fluid inflow path 32a, the heat exchange is performed. A circulation flow path for the heat exchange fluid W (water in this embodiment) is formed by the fluid outflow path 32b, the pipe P, and the indoor unit. Thereby, the air conditioner (refrigeration system FS) according to the present embodiment supplies water (cold water) W heat-exchanged by the evaporator A to the indoor unit, and water exchanged heat (water whose temperature has increased) by the indoor unit. W is returned to the evaporator A.

  The compressor B employs a general reciprocating type or screw type, and the secondary side is connected to the condenser C via a pipe P.

  Although various types of heat exchangers can be adopted as the condenser C, a plate heat exchanger is adopted in the present embodiment.

  Unlike the evaporator A, the condenser C of the refrigeration system FS according to the present embodiment employs a general plate heat exchanger. That is, in the condenser C according to this embodiment, a plurality of heat transfer plates 5 and 6 are stacked as shown in FIG. 8, and the cooling water CW is circulated as shown in FIGS. 9 (a) and 9 (b). Each of the heat transfer plates includes a cooling water flow path R4 to be circulated and a refrigerant flow path R5 through which the refrigerant CM (the refrigerant CM pressurized by the compressor B) subjected to heat exchange with the cooling water CW flows. 5 and 6 are alternately formed as boundaries, and openings formed at the four corners of each of the heat transfer plates 5 and 6 are connected to cool the cooling water flow path R4 at both ends of the heat transfer plates 5 and 6. A cooling water inflow path 50a and a cooling water outflow path 50b through which water CW flows in and out are formed, and a refrigerant inflow path 51a and a refrigerant outflow path 51b through which the refrigerant CM flows in and out of the refrigerant flow path R5. Is formed. Thereby, the condenser C condenses the refrigerant CM by heat exchange between the cooling water CW flowing through the cooling water flow path R4 and the refrigerant CM flowing through the refrigerant flow path R5.

  Returning to FIG. 7, in the condenser C, each of the cooling water inflow passage 50a and the cooling water outflow passage 50b is connected to a cooling device (for example, a cooling tower) by a pipe P. The cooling water inflow passage 50a, the cooling water A circulation passage for the cooling water CW is formed by the outflow passage 50b, the pipe P, and the cooling device. Thereby, in the refrigeration system FS according to the present embodiment, the cooling water CW cooled by the cooling device is supplied to the cooling water inflow passage 50a, and the cooling water CW is supplied to the refrigerant flow passage in the cooling water flow passage R4. After being used for heat exchange with the refrigerant CM in R5, the refrigerant is discharged from the cooling water outflow passage 50b toward the cooling device. In the condenser C, the refrigerant inflow path 51a is connected to the compressor B via a pipe P, and the refrigerant outflow path 51b is directly or indirectly connected to the refrigerant inflow path 31a of the evaporator A. Connected through.

  In the refrigeration system FS according to the present embodiment, the refrigerant outflow path 51b of the condenser C and the heating fluid inflow path 33a of the evaporator A are connected by a pipe P, and the heating fluid outflow path 33b of the evaporator A and the evaporation The refrigerant inflow passage 31a of the vessel A is connected to the intermediate position by a pipe P provided with the expansion valve V.

  Note that the refrigeration system FS according to the present embodiment can be an air conditioning / heating machine by providing a four-way valve on the flow path of the refrigerant CM to reverse the flow of the refrigerant CM. In this case, the evaporator A and the condenser C are interchanged. That is, the plate heat exchanger that functions as the evaporator A during cooling functions as the condenser C during heating, and the plate heat exchanger that functions as the condenser C during heating functions as the evaporator A during cooling. Therefore, it goes without saying that when the air conditioner is used, it is preferable to employ a plate-type heat exchanger similar to the evaporator A configured as described above as the condenser C.

  The refrigeration system FS (air conditioner) according to the present embodiment is as described above. Next, the operation of the air conditioner having the above configuration (the refrigeration system FS including the evaporator A having the above configuration) will be described.

  First, the cooling device (cleaning tower) is driven to circulate the cooling water CW in the circulation channel. At the same time, the compressor B of the refrigeration system FS is operated to pressurize the refrigerant CM and send it to the downstream side (condenser C side) to circulate the refrigerant CM in the circulation path in the refrigeration system FS and To circulate the water W, which is the heat exchange fluid, in the circulation path.

  Then, in the evaporator A, the refrigerant CM flowing in the first flow path R1 and the water W flowing in the second flow path R2 exchange heat, and the water W that has passed through the second flow path R2 is cooled. It is sent to an indoor unit (not shown), and the indoor air and water W are heat-exchanged by the indoor unit, and the air whose temperature has decreased is blown into the room as cold air. Then, the water W whose temperature has increased due to the heat exchange with the air returns to the evaporator A again and is cooled by exchanging heat with the refrigerant CM flowing in the first flow path R1.

  When the water W is cooled in this manner, the refrigerant CM in the first flow path R1 evaporates as it flows downstream due to heat exchange with the water W flowing in the second flow path R2, and contains a large amount of gas components. It becomes a liquid mixed state. In the evaporator A, the refrigeration system FS according to the present embodiment is in a gas-liquid mixed state in which the refrigerant CM is sufficiently contained in a state where the refrigerant CM passes through the entire region corresponding to the second flow path R2 in the first flow path R1. The refrigerant CM is set to circulate so that the entire water W flowing in the second flow path R2 can be cooled. That is, when the refrigerant CM is in a gas-liquid mixed state that sufficiently contains a liquid component in a state of passing through a region corresponding to the second flow path R2 in the first flow path R1, the second flow paths of the heat transfer units 10 and 20 are used. Since the region corresponding to R2 is in a wet state, the refrigerant CM flowing through the first flow path R1 actively takes the heat of the heat exchange fluid W over the entire area of the second flow path R2, and the heat exchange fluid W Is efficiently cooled.

  As described above, when the refrigerant CM in the gas-liquid mixed state sufficiently containing the liquid component is circulated in the region corresponding to the second flow path R2 in the first flow path R1, the refrigerant CM flowing in the first flow path R1 is the second flow. The gas-liquid mixed state is also obtained when entering the region corresponding to the third flow path R3 from the region corresponding to the path R2, but the heating fluid WM having a temperature higher than that of the heat exchange fluid W is applied to the third flow path R3. By making it circulate, the refrigerant CM in the most downstream area of the first flow path R1 is rapidly moved by heat transfer between the refrigerant CM flowing through the first flow path R1 and the heating fluid WM flowing through the third flow path R3. As a result of evaporation, the completely gasified refrigerant CM is discharged from the refrigerant outflow path 31b (see FIG. 6).

  The refrigerant CM discharged from the refrigerant outflow path 31b is compressed by the compressor B, supplied to the condenser C, condensed, and returned to the evaporator A.

  In the refrigeration system FS according to the present embodiment, the high-temperature refrigerant CM discharged from the condenser C is circulated through the third flow path R3 of the evaporator A as the heating fluid WM, and then decompressed by the expansion valve V. After the temperature of the refrigerant CM is lowered, the refrigerant CM is supplied again to the refrigerant inflow passage 31a.

  For example, a single component refrigerant is used as the refrigerant CM, and as shown in FIG. 7, 5 ° C. refrigerant CM is supplied to the refrigerant inflow passage 31a, and 12 ° C. water W returning from the indoor unit is cooled to 7 ° C. Assuming that the water is supplied toward the indoor unit, the refrigerant CM supplied at 5 ° C. flows through the first flow path R1 while being exchanged with the water W. As the refrigerant CM flows through the first flow path R1, the pressure drops due to flow resistance, and evaporation proceeds while the temperature decreases. The refrigerant CM finally completes evaporation at 4 ° C., and is supplied to the compressor B from the refrigerant outflow passage 31b in an overheated state at 8 ° C. When 32 ° C. cooling water is supplied to the condenser C from the cooling device, the refrigerant CM compressed by the compressor B is condensed by heat exchange with the cooling water CW and evaporated in a state of 40 ° C. To the third flow path R3 of the container A. The cooling water CW supplied to the condenser C is discharged in a state where the temperature has increased to 37 ° C. by heat exchange with the refrigerant CM.

  And the refrigerant | coolant CM from the condenser C is supplied to the refrigerant | coolant inflow path 31a of the evaporator A, distribute | circulates the 3rd flow path R3, and heat-exchanges with the refrigerant | coolant CM distribute | circulated in the most downstream in 1st flow path R1. It will be. Then, the refrigerant CM in the most downstream area of the first flow path R1 is completely evaporated at 4 ° C. and discharged from the refrigerant outflow path 31b in an overheated state at 8 ° C., whereas the refrigerant that has passed through the third flow path R3. The CM is discharged from the heated fluid outflow passage 33b in a state where the temperature is lowered to 30 ° C. And the refrigerant | coolant CM discharged | emitted from 3rd flow path R3 will be supplied to the refrigerant | coolant inflow path 31a again, after temperature fall to 5 degreeC by pressure reduction by passing through the expansion valve V. FIG.

  Therefore, in the air conditioner (refrigeration system FS) according to the present embodiment, the water W is cooled only by the refrigerant CM circulating in the circulation path, and the refrigerant CM in the first flow path R1 is completely evaporated and gasified. It will be. Therefore, the air conditioner (refrigeration system FS) operates smoothly without damaging the compressor B because the refrigerant CM reaching the compressor B does not contain liquid.

  As described above, the evaporator A according to the present embodiment extends in the short direction perpendicular to the longitudinal direction of the heat transfer plates 1 and 2 between the surfaces of the heat transfer plates 1 and 2 facing each other. A partition portion 30 is provided, and the second flow path R2 is formed on one side in the longitudinal direction of the heat transfer plates 1 and 2 between one surface of the heat transfer plates 1 and 2 with the partition portion 30 as a boundary. At the same time, a third flow path R3 is formed on the other side in the longitudinal direction of the heat transfer plates 1 and 2 between the one surfaces of the heat transfer plates 1 and 2 for circulating the heating fluid WM having a higher temperature than the heat exchange fluid W. On the other hand, a first flow path R1 is formed between the other surfaces of the heat transfer plates 1 and 2 facing each other, and a heating fluid inflow path 33a and a heating fluid outflow flow the heating fluid WM into and out of the third flow path R3. The path 33b passes through the region where the third flow path R3 is formed. The refrigerant inflow path 31a is formed so as to pass through the area where the second flow path R2 is formed, and the refrigerant outflow path 31b is formed in the area where the third flow path R3 is formed. Since it forms so that it may pass, the heat exchange fluid W can be cooled efficiently, and it can produce the outstanding effect that the completely gasified refrigerant CM can be discharged. Therefore, when the evaporator A is employed in the refrigeration system FS, the heat exchange fluid W can be cooled with high efficiency, and damage to the compressor B provided in the subsequent stage can be prevented.

  Further, the partition portion 30 is formed by being welded in a state where the partition projections 100 and 200 discharged from the heat transfer plates 1 and 2 facing each other toward the other side are in surface contact with each other. A wide partition 30 is formed between the flow path R2 and the third flow path R3 to prevent the heat exchange fluid W from being affected by the heat fluid WM having a higher temperature than the heat exchange fluid W. can do.

  Further, the refrigerant inflow passage 31a, the refrigerant outflow passage 31b, the heat exchange fluid inflow passage 32a, and the heat exchange fluid outflow passage 32b are arranged at the center of the heat transfer plates 1 and 2 in the other direction. Since they are aligned in the longitudinal direction of 1 and 2, the flow of the refrigerant CM in the first flow path R1 and the flow of the heat exchange fluid W in the second flow path R2 can be made uniform.

  In particular, since the heating fluid inflow passage 33a and the heating fluid outflow passage 33b are disposed on both sides of the heat transfer plates 1 and 2 in the short direction with respect to the refrigerant outflow passage 31b, the heating fluid inflow passage 33a is heated. The heating fluid WM flowing toward the fluid outflow path 33b passes around the refrigerant outflow path 31b, and the refrigerant CM discharged from the first flow path R1 can be reliably evaporated.

  The cross-sectional shape of the heat exchange fluid outflow passage 32b arranged on the third flow path R3 side is formed in an elliptical shape having a long axis in the longitudinal direction of the heat transfer plates 1 and 2 (the flow direction of the refrigerant CM). Therefore, the refrigerant CM can be smoothly circulated in the first flow path R1. That is, if the heat exchange fluid outflow passage 32b exists in a region where the refrigerant CM that has evaporated due to heat exchange with the heat exchange fluid W in the second flow path R2 flows, the flow of the refrigerant CM is hindered and the pressure is reduced. Although the loss increases, as described above, if the cross-sectional shape of the heat exchange fluid outflow passage 32b is formed in an elliptical shape having a long axis in the longitudinal direction of the heat transfer plates 1 and 2 (longitudinal direction of the refrigerant CM), Since the short axis is positioned in the short direction of the heat plates 1 and 2, the range that hinders the circulation of the refrigerant CM is narrowed. As a result, the refrigerant CM can be smoothly circulated without increasing the pressure loss.

  The heat exchange fluid outflow passage 32b is disposed on the third flow path R3 side with respect to the heat exchange fluid inflow passage 32a, and the heat exchange plate 1 and 2 are disposed between one surface of the heat exchange plates 1 and 2. Since a fluid guide portion 34 is provided that partially surrounds the periphery of the fluid outflow path 32b on the other end side (upstream side in the flow direction of the heat exchange fluid W) of the heat transfer plates 1 and 2, heat exchange is performed. The heat exchange fluid W flowing from the fluid inflow passage 32a collides with the fluid guide portion 34, is divided on both sides of the fluid guide portion 34, and then flows into the heat exchange fluid outflow passage 32b. Accordingly, since the heat exchange fluid W flowing from the heat exchange fluid inflow passage 32a side in the second flow passage R1 does not directly flow out of the heat exchange fluid outflow passage 32b, the refrigerant in the first flow passage R1. The opportunity for heat exchange between the CM and the heat exchange fluid W in the second flow path R2 can be increased, and the heat exchange fluid W can be efficiently cooled.

  Between the other surfaces of the heat transfer plates 1 and 2, at least the other end side of the refrigerant inflow passage 31a in the longitudinal direction of the heat transfer plates 1 and 2 (the downstream side in the flow direction of the refrigerant CM in the first flow path R1). ) Is partially provided so that the refrigerant CM flowing into the first flow path R1 from the refrigerant inflow path 31a does not flow directly toward the refrigerant outflow path 31b, and the heat exchange fluid W Can increase the chance of heat exchange. That is, the refrigerant CM that has flowed into the first flow path R1 from the refrigerant inflow path 31a once flows along the guide portion 35 toward the opposite side of the refrigerant outflow path 31b and then flows toward the refrigerant outflow path 31b. Thereby, since the distribution path of refrigerant | coolant CM can be lengthened, the opportunity of heat exchange with the to-be-heat-exchanged fluid W can be increased.

  In particular, the evaporator A according to this embodiment includes a pair of side guide portions 36a extending from both ends of the guide portion 35 to both sides of the heat exchange fluid inflow passage 32a between the other surfaces of the heat transfer plates 1 and 2. Since 36b is provided, the refrigerant CM that has flowed into the first flow path R1 from the refrigerant inflow path 31a flows toward the opposite side of the refrigerant outflow path 31b along the guide part 35 and the side guide parts 36a and 36b. Thus, the refrigerant flows to the refrigerant outflow path 31b side. Therefore, since the flow path of the refrigerant CM can be made longer than when only the guide part 35 is provided, the chance of heat exchange with the heat exchange fluid W can be further increased. Further, by providing the side guide portions 36a and 36b, the refrigerant CM flowing into the first flow path R1 from the refrigerant inflow path 31a cools the periphery of the heat exchange fluid inflow path 32a, so that more efficient cooling can be achieved. It becomes possible.

  The refrigeration system FS according to the present embodiment includes an evaporator that exchanges heat between the refrigerant CM and the heat exchange fluid W, a compressor B that pressurizes the refrigerant CM discharged from the evaporator, and the compressor B A refrigeration system FS configured to supply the refrigerant CM condensed in the condenser C to the evaporator. The refrigeration system FS is configured to supply the refrigerant CM condensed in the condenser C to the evaporator. In order to allow the heating fluid WM to flow through the third flow path R3 while flowing the heat exchange fluid W through the second flow path R2 in a state where the refrigerant A is configured in the evaporator A and the refrigerant CM is passed through the first flow path R1, the evaporation The same operations and effects as the device A can be achieved.

  In addition, this invention is not limited to the said embodiment, Of course, it can change suitably in the range which does not deviate from the summary of this invention.

  For example, in the above embodiment, when the pressure is constant, it is assumed that the refrigerant CM (single component refrigerant, azeotropic refrigerant mixture, or pseudo azeotropic refrigerant mixture) that hardly increases in temperature even with the progress of evaporation is employed. In addition, the fourth opening H4 on the other end side in the longitudinal direction of the second region A2 constitutes the heat exchange fluid inflow passage 32a, while the second opening H2 on the one end side in the longitudinal direction of the second region A2 The heat exchange fluid outflow passage 32b is configured to cause the refrigerant CM flowing in the first flow path R1 and the heat exchange fluid W (water) flowing in the second flow path R2 to flow in the same direction (in parallel flow). However, the present invention is not limited to this. Even when the pressure is constant, when the refrigerant CM (non-azeotropic refrigerant mixture) that rises in temperature due to the progress of evaporation is employed, the longitudinal direction of the second region A2 Heat exchange fluid outflow path 3 at the fourth opening H4 on the other end side On the other hand, the second opening H2 on one end side in the longitudinal direction of the second region A2 constitutes the heat exchange fluid inflow passage 32a, and the refrigerant CM and the second passage R2 circulate in the first passage R1. The heat exchange fluid W (water) that circulates in (1) may be circulated in the opposite direction (turned to the opposite flow).

  In the above embodiment, the heating fluid inflow passage 33a and the heating fluid outflow passage 33b (the fifth opening H5 and the sixth opening H6) are arranged in a row in the short direction of the heat transfer plates 1 and 2, For example, the heating fluid inflow path 33a and the heating fluid outflow path 33b (the fifth opening H5 and the sixth opening H6) are aligned in a line in the longitudinal direction of the heat transfer plates 1 and 2. It may be arranged at a diagonal position of the first region A1. That is, the arrangement of the heating fluid inflow path 33a and the heating fluid outflow path 33b can be appropriately changed as long as the heating fluid WM having a temperature higher than that of the heat exchange fluid W can be filled in the third flow path R3.

  In the above embodiment, the refrigerant inflow passage 31a, the refrigerant outflow passage 31b, the heat exchange fluid inflow passage 32a, and the heat exchange fluid outflow passage 32b are aligned in the longitudinal direction at the center of the heat transfer plates 1 and 2 in the short direction. However, the present invention is not limited to this, and these channels may be disposed at appropriate positions. However, it goes without saying that it is preferable to use the same method as in the above embodiment in consideration of the flow of the refrigerant CM, the heat exchange fluid W, and the like.

  In the above embodiment, the heat transfer plates 1 and 2 (heat transfer portions 10 and 20) are formed in a rectangular shape in plan view so that the refrigerant CM and the heat exchange fluid W are circulated in the longitudinal direction. For example, the heat transfer plates 1 and 2 (heat transfer portions 10 and 20) are formed in a rectangular shape in plan view, and the partition 30 that partitions one surface of the heat transfer plates 1 and 2 is provided. It may be formed so as to extend in the longitudinal direction, and the refrigerant CM and the heat exchange fluid W may be circulated in the short direction of the heat transfer plates 1 and 2. Of course, the heat transfer plates 1 and 2 (heat transfer portions 10 and 20) may be formed in a square shape in plan view. Even in this case, the first flow path R1 is formed so as to overlap both the second flow path R2 and the third flow path R3, and the refrigerant outflow path 31b is provided in a region corresponding to the third flow path R3. Thus, the same operations and effects as the above embodiment can be achieved.

  Although not mentioned in the above embodiment, for example, a guide for guiding the refrigerant CM flowing from the refrigerant inflow path 31a side to the refrigerant outflow path 31b around the refrigerant outflow path 31b, or a heat exchange fluid A guide for guiding the heat exchange fluid W flowing from the heat exchange fluid inflow passage 32a side to the heat exchange fluid outflow passage 32b is provided around the outflow passage 32b, or the heating fluid is provided around the heat fluid outflow passage 33b. A guide for guiding the heating fluid WM flowing from the inflow path 33a side to the heating fluid outflow path 33b may be provided. Such a guide may be formed of a ridge along the flow direction of the target fluid. If it does in this way, it can discharge smoothly, without disturbing the flow of the fluid which circulates in each channel.

  In the above embodiment, the heat exchange fluid outflow passage 32b is partially surrounded on the premise that the heat exchange fluid W is circulated from the other end side in the longitudinal direction of the heat transfer plates 1 and 2 toward the one end side. Although the fluid guide part 34 is provided on the other end side in the longitudinal direction of the heat transfer plates 1 and 2, the present invention is not limited thereto. For example, the fluid guide part 34 is not provided and the heat exchange fluid inflow path 32 a side is provided. The heat exchange fluid W flowing from the heat exchange fluid may be directly discharged from the heat exchange fluid outflow passage 32b.

  Moreover, in the said embodiment, the guide part 35 which partially surrounds the refrigerant | coolant inflow path 31a (3rd opening H3) from the one end side of a longitudinal direction is provided, and the refrigerant | coolant CM which flowed in from the refrigerant | coolant inflow path 31a is made into the heat-transfer plate 1, 2 is guided toward the other end side in the longitudinal direction and then circulated toward the refrigerant outflow passage 31b on the one end side in the longitudinal direction. However, the present invention is not limited to this. Without providing, the refrigerant CM flowing in from the refrigerant inflow path 31a may be directly circulated toward the refrigerant outflow path 31b.

  Further, in the above embodiment, the refrigerant inflow path 31a extends from both ends of the guide portion 35 surrounding the refrigerant inflow path 31a on the premise that the refrigerant inflow path 31a is disposed closer to one end in the longitudinal direction than the heat exchange fluid inflow path 32a. Although the pair of side guide portions 36a and 36b are provided, the present invention is not limited to this. For example, only the guide portion 35 may be provided, or the guide portion 35 and the side guide portions 36a and 36b are provided. Alternatively, the refrigerant CM that has flowed into the first flow path R1 from the refrigerant inflow path 31a may flow directly toward the refrigerant outflow path 31b. However, in order to increase the amount of heat exchange between the refrigerant CM and the heat exchange fluid W, it is preferable to provide the guide portion 35, and it is more preferable to provide a pair of side guide portions 36 a and 36 b together with the guide portion 35. Needless to say.

  In the above embodiment, the cross-sectional shape of the heat exchange fluid outflow passage 32b is formed in an elliptical shape in which the long axis is set in the longitudinal direction (the flow direction of the refrigerant CM), but is not limited to this. The cross-sectional shape of the heat exchange fluid outflow passage 32b may be a perfect circle. Further, the cross-sectional shapes of the refrigerant inflow path 31a, the refrigerant outflow path 31b, the heat exchange fluid inflow path 32a, the heat exchange outflow path, the heating fluid inflow path 33a, and the heating fluid outflow path 33b are rounded. For example, these cross-sectional shapes may be formed in a non-circular shape. However, considering the flow of the fluid in each flow path, it is preferable to set the cross-sectional shape to a rounded shape, and in particular, the heat exchange fluid inflow path 32a penetrating the middle position of the first flow path R1. Alternatively, it goes without saying that the cross-sectional shape of the heat exchange outflow passage is preferably an elliptical shape having a major axis set in the flow direction of the refrigerant CM.

  In the above embodiment, the plurality of stacked heat transfer plates 1 and 2 are brazed to seal the periphery of the opening and the outer periphery of the heat transfer portions 10 and 20, but the present invention is not limited to this. Instead, for example, an annular gasket may be disposed around the opening or around the outer periphery of the heat transfer portions 10 and 20 so that the gasket is sandwiched between the adjacent heat transfer plates 1 and 2. Even in this manner, the first flow path R1, the second flow path R2, and the third flow path R3 as well as the refrigerant inflow path 31a, the refrigerant outflow path 31b, and the like can be formed between the heat transfer plates 1 and 2. Therefore, the same operation and effect as the above embodiment can be achieved. In this type of evaporator A, the gasket may be deteriorated depending on the type and properties of the refrigerant CM. Therefore, when the material of the gasket is appropriately selected or there is no appropriate gasket, the same as in the above embodiment. Needless to say, you need to adopt something.

  In the above embodiment, the refrigerant CM having a high temperature passing through the condenser C is circulated through the third flow path R3 as the heating fluid WM. However, the refrigerant CM passing through the evaporator A is transferred to the third flow path R3. For example, the third flow path R3 is connected to another path and the high temperature water or the above is used as the heating fluid to flow to the third flow path R3. Of course, it is possible to make it.

  1, 2 ... Heat transfer plate, 3, 4 ... Frame plate, 10, 20 ... Heat transfer part, 11, 21 ... Ring part, 30 ... Partition part, 31a ... Refrigerant inflow path, 31b ... Refrigerant outflow path, 32a ... Covered Heat exchange fluid inflow passage, 32b ... Heat exchange fluid outflow passage, 33a ... Heating fluid inflow passage, 33b ... Heating fluid outflow passage, 34 ... Fluid guide portion, 35 ... Guide portion, 36a, 36b ... Side guide portion, 100, 200 ... partitioning projections, 101, 201 ... first annular projection, 102, 202 ... second annular projection, 103, 203 ... third annular projection, 104, 204 ... fourth annular projection, 105, 205 ... Fifth annular projection, 106,206 ... Sixth annular projection, 107,207 ... Guide projection, 108,208 ... Guide projection, 109,209 ... Side guide projection, A ... Evaporator, A1 ... first region, A2 ... second region, B ... compressed , C ... condenser, CM ... refrigerant, FS ... refrigeration system, H1 ... first opening, H1 -... first opening, H2 ... second opening, H3 ... third opening, H4 ... fourth opening, H5 ... fifth Opening, H6 ... sixth opening, P ... piping, Pa1 ... first pass region, Pa2 ... second pass region, R1 ... first flow channel, R2 ... second flow channel, R3 ... third flow channel, V ... expansion valve , W: Heat exchange fluid, WM: Heated fluid, θ: Angle

Claims (5)

  A first flow path through which the refrigerant flows and a second flow path through which the heat exchange fluid flows are alternately formed across each of the stacked heat transfer plates, and the refrigerant flows out of each first flow path. The refrigerant inflow path and the refrigerant outflow path to be introduced are formed at intervals in one direction so as to pass through the region where the first flow path is formed, and the heat exchange fluid is flowed into and out of the second flow path. In the evaporator formed at intervals in the one direction so that the heat exchange fluid inflow path and the heat exchange fluid outflow path pass through the region where the second flow path is formed, one of the heat transfer plates facing each other A partition portion extending in the other direction orthogonal to the one direction is provided between the surfaces, and the second flow path is formed on one side of the one direction between one surface of the heat transfer plate with the partition portion as a boundary. And the distance between one side of the heat transfer plate A third flow path for flowing a heated fluid having a temperature higher than that of the heat exchange fluid is formed on the other side, and a first flow path is formed between the other surfaces of the heat transfer plates facing each other, A heating fluid inflow path and a heating fluid outflow path for allowing the heating fluid to flow in and out of the three flow paths are formed so as to pass through a region where the third flow path is formed, and the refrigerant inflow path is formed as a second flow path. An evaporator characterized in that it is formed so as to pass through a region where the refrigerant is discharged and the refrigerant outflow passage is formed so as to pass through a region where the third flow path is formed.   Each heat transfer plate is formed with partitioning ridges extending in the other direction orthogonal to the one direction on one surface facing each other, and the partitioning portion is formed by the partitioning ridges of the heat transfer plates facing each other. The evaporator according to claim 1, wherein the evaporator is formed by welding in a contact state.   The refrigerant inflow path, the refrigerant outflow path, the heat exchange fluid inflow path, and the heat exchange fluid outflow path are aligned in the one direction at the center of the other direction of the heat transfer plate. Item 3. The evaporator according to Item 1 or 2.   2. The heat exchange fluid outflow passage or the heat exchange fluid inflow passage arranged on the third flow path side is formed in an elliptical shape with a cross-sectional shape having a long axis in the one direction. 4. The evaporator according to any one of items 1 to 3.   An evaporator for exchanging heat between the refrigerant and the heat exchange fluid, a compressor for pressurizing the refrigerant discharged from the evaporator, and a condenser for condensing the refrigerant compressed by the compressor, the condenser In the refrigeration system configured to supply the refrigerant condensed in step 1 to the evaporator, the evaporator is configured by the evaporator according to any one of claims 1 to 4, and the refrigerant is provided in the first flow path. Refrigeration characterized in that a heated fluid having a temperature higher than that of the heat exchange fluid is circulated through the third channel while the heat exchange fluid is circulated through the second channel. system.

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