JP6897635B2 - Water heat exchanger - Google Patents

Description

In the present invention, a water heat exchanger, particularly, a first layer in which a first layer through which water as a first fluid flows is formed in a plurality of rows, and a second flow path in which a refrigerant as a second fluid flows are formed in a plurality of rows. The present invention relates to a water heat exchanger that is formed by laminating the second layer and the second layer, and exchanges heat between the first fluid and the second fluid.

Conventionally, in heat pump type air conditioners, heat pump type water heaters, etc., water heat exchangers that exchange heat between water as the first fluid and refrigerant as the second fluid (fluorocarbon refrigerant, natural refrigerant, brine, etc.) have been used. It is used. As such a water heat exchanger, as shown in Patent Document 1 (Japanese Unexamined Patent Publication No. 2010-117102), a first layer in which a plurality of rows of first flow paths through which the first fluid flows are formed, and a second fluid are used. Some are configured by stacking a second layer in which a plurality of rows of flowing second flow paths are formed.

In the above-mentioned conventional water heat exchanger, high performance and compactness can be achieved by reducing the flow path cross-sectional area of the first flow path and the second flow path.

However, if the flow path cross-sectional area of the first flow path or the second flow path is made too small, there is a concern that the pressure loss may increase or the flow path may be clogged. For this reason, it is necessary to devise a flow path shape that can suppress an increase in pressure loss and clogging of the flow path.

An object of the present invention is a first layer in which a plurality of rows of first flow paths through which water flows as a first fluid are formed, and a second layer in which a plurality of rows of second flow paths through which a refrigerant as a second fluid flows are formed. In a water heat exchanger that exchanges heat between the first fluid and the second fluid, by devising the shape of the flow path, it is possible to suppress an increase in pressure loss and clogging of the flow path. There is.

In the water heat exchanger according to the first aspect, the first plate material and the second plate material are alternately laminated in the stacking direction, so that the first flow path through which water as the first fluid flows is viewed along the stacking direction. A laminated structure having a first layer formed in a plurality of rows at the time and a second layer formed in a plurality of rows when the second flow path through which the refrigerant as the second fluid flows is viewed along the stacking direction. It is configured to exchange heat between the first fluid and the second fluid. When the first layer is viewed along the stacking direction, the first flow path extends from one end to the other end of the first layer along a direction intersecting the arrangement direction of the first flow path. The second flow path extends from one end to the other end of the second layer along the direction intersecting the arrangement direction of the second flow path when the second layer is viewed along the stacking direction. Here, when the first fluid is cooled by the second fluid, the cross-sectional area of the flow path in the vicinity of the second fluid outlet located near the outlet of the second fluid is near the outlet of the second fluid. It is formed so as to be larger than the cross-sectional area of the flow path in the portion on the upstream side of the portion.

Here, as described above, for the second flow path, the flow path cross-sectional area in the vicinity of the second fluid outlet is larger than that on the upstream side, so that the flow velocity of the second fluid in the second flow path decreases. The decrease in heat transfer coefficient due to the above can be limited to the vicinity of the second fluid outlet, and the second fluid containing a large amount of gas components increasing with evaporation can be smoothly flowed to the vicinity of the second fluid outlet. As described above, here, it is possible to suppress an increase in the pressure loss of the second flow path in the water heat exchanger while minimizing the decrease in the heat transfer coefficient.

In the water heat exchanger according to the second aspect, in the water heat exchanger according to the first aspect, the number of flow paths in the second flow path in the vicinity of the second fluid outlet is upstream of that in the vicinity of the second fluid outlet. It merges so that it is less than the number of flow paths in the side portion.

Here, as described above, by merging so that the number of flow paths in the vicinity of the second fluid outlet is smaller than that in the upstream portion, the cross-sectional area of the flow paths in the vicinity of the second fluid outlet is on the upstream side. Can be larger than the part of.

In the water heat exchanger according to the third aspect, in the water heat exchanger according to the first aspect, the number of flow paths in the second flow path in the vicinity of the second fluid outlet is upstream of that in the vicinity of the second fluid outlet. It branches so that it is larger than the number of flow paths in the side portion.

Here, as described above, the cross-sectional area of the flow path in the vicinity of the second fluid outlet is increased to the upstream side by branching so that the number of flow paths in the vicinity of the second fluid outlet is larger than that in the upstream portion. Can be larger than the part of. Moreover, since the number of flow paths in the vicinity of the inlet of the second fluid is reduced here, the distribution performance of the second fluid in the second flow path can be kept good.

As described above, according to the present invention, the first fluid is heated while limiting the decrease in heat transfer coefficient due to the decrease in the flow velocity of the first fluid in the first flow path to only the portion near the outlet of the first fluid. Since it is possible to prevent the scale deposited at the time of being clogged in the vicinity of the first fluid outlet, it is possible to suppress the clogging of the first flow path in the water heat exchanger while minimizing the decrease in the heat transfer coefficient. it can. Further, according to the present invention, the decrease in heat transfer coefficient due to the decrease in the flow velocity of the second fluid in the second flow path is limited to the vicinity of the outlet of the second fluid, and a large amount of gas component increases with evaporation. Since the two fluids can flow smoothly to the vicinity of the outlet of the second fluid, it is possible to suppress an increase in the pressure loss of the second flow path in the water heat exchanger while minimizing the decrease in the heat transfer coefficient.

It is a figure which shows the appearance of the water heat exchanger which concerns on one Embodiment of this invention. It is a figure which shows the 1st flow path of the water heat exchanger which concerns on one Embodiment of this invention. It is a figure which shows the 2nd flow path of the water heat exchanger which concerns on one Embodiment of this invention. It is a perspective view which shows the laminated state of the 1st channel and the 2nd channel of the water heat exchanger which concerns on one Embodiment of this invention. It is a figure (corresponding to FIG. 2) which shows the 1st flow path of the water heat exchanger which concerns on the modification 1 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 1 of this invention. It is a figure which shows the appearance of the water heat exchanger which concerns on the modification 2 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 2 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 3 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 3 of this invention. It is a figure (corresponding to FIG. 2) which shows the 1st flow path of the water heat exchanger which concerns on the modification 4 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 5 of this invention. It is a figure (corresponding to FIG. 3) which shows the 2nd flow path of the water heat exchanger which concerns on the modification 5 of this invention.

Hereinafter, embodiments of the water heat exchanger according to the present invention and examples of modifications thereof will be described with reference to the drawings. The specific configuration of the water heat exchanger according to the present invention is not limited to the following embodiments and modifications thereof, and can be changed without departing from the gist of the invention.

(1) Configuration and Features FIGS. 1 to 4 are views showing a water heat exchanger 1 according to an embodiment of the present invention.

The water heat exchanger 1 is a heat exchanger that exchanges heat between water as a first fluid and a refrigerant as a second fluid in a heat pump type air conditioner, a heat pump type water heater, or the like. In the following description, "top", "bottom", "left", "right", "vertical", and "horizontal" are used with reference to the front surface of the water heat exchanger 1 shown in FIGS. , Etc., but these expressions are for convenience of explanation and do not mean the actual arrangement of the water heat exchanger 1 and its components.

The water heat exchanger 1 mainly includes a casing 2 provided with a heat exchange unit 3 for exchanging heat between the first fluid and the second fluid, first inlet / outlet pipes 4a and 4b serving as inlets / outlets for the first fluid, and the like. It has second inlet / outlet pipes 5a and 5b that serve as inlet / outlet for the second fluid.

The heat exchange unit 3 includes a first layer 10 in which a plurality of rows of first flow paths 11 through which the first fluid flows are formed, and a second layer 20 in which a plurality of rows of second flow paths 21 through which the second fluid flows are formed. Is configured by stacking. Here, the direction in which the first layer 10 and the second layer 20 are laminated (here, the direction from the front side of the paper surface to the back side of the paper surface in FIGS. 1 to 3) is defined as the stacking direction. Further, the direction in which the plurality of first flow paths 11 are lined up (here, the left-right direction on the paper surface in FIG. 2) is the arrangement direction of the first flow paths 11, and the direction in which the plurality of second flow paths 21 are lined up (here, FIG. 3). The vertical direction of the paper surface) is the arrangement direction of the second flow path 21. Then, when the first layer 10 is viewed along the stacking direction of the first and second layers 10 and 20, the first flow path 11 intersects the arrangement direction of the first flow path 11 (here, in this case). Extends from one end of the first layer 10 (upper end of the first layer 10 in FIG. 2) to the other end (lower end of the first layer 10 in FIG. 2) along the paper surface vertical direction and vertical direction of FIG. ing. Further, the second flow path 21 intersects the arrangement direction of the second flow path 21 when the second layer 20 is viewed along the stacking direction of the first and second layers 10, 20 (here, the second flow path 21). From one end of the second layer 20 (the left end of the second layer 20 in FIG. 3-) to the other end (the right end of the second layer 20 in FIG. 3) along the paper surface left-right direction and lateral direction of FIG. It is extending. As described above, here, the first flow path 11 and the second flow path 20 are arranged so as to form an orthogonal flow.

Here, the heat exchange unit 3 having a laminated structure of the first layer 10 and the second layer 20 has a first plate material 12 having a groove forming the first flow path 11 formed on one surface and a second flow path 21. The second plate member 22 having grooves formed on one side thereof are alternately laminated. The first and second plate members 12 and 22 are made of a metal material. The grooves forming the first flow path 11 and the second flow path 21 are formed, for example, by subjecting the first and second plate members 12 and 22 to machining or etching. Then, after laminating a predetermined number of the first and second plate materials 12 and 22 having been grooved in this way, the first and second plate materials 12 and 22 are joined by using a joining process such as diffusion joining. As a result, the heat exchange unit 3 having a laminated structure of the first layer 10 and the second layer 20 is obtained. Here, grooves forming the flow paths 11 and 21 are formed on one side of both the first and second plate members 12 and 22, but the present invention is not limited to this, and the first and second plate materials 12 are not limited thereto. , 22 may be formed on both sides of the flow paths 11 and 21, or grooves forming the flow paths 11 and 21 may be formed on both sides of both the first and second plate members 12 and 22. It may have been done.

The first entrance / exit pipes 4a and 4b are provided here at the upper part and the lower part of the casing 2. The casing 2 has a first header portion 6 in which a space for merging between the upper ends of the first flow path 11 is formed in the upper portion thereof, and a space in the lower portion thereof for merging between the lower ends of the first flow path 11. The first header portion 7 and the like are provided. The first inlet / outlet pipe 4a communicates with the upper end portion of the first flow path 11 via the first header portion 6, and the first inlet / outlet pipe 4b communicates with the first flow path via the first header portion 7. It communicates with the lower end of 11. The second inlet / outlet pipes 5a and 5b are provided here on the left and right portions of the casing 2. The casing 2 has a second header portion 8 in which a space for merging between the left ends of the second flow path 21 is formed on the left portion thereof, and a space for merging between the right ends of the second flow path 21 on the right portion thereof. A second header portion 9 and a second header portion 9 are provided. The second inlet / outlet pipe 5a communicates with the left end portion of the second flow path 21 via the second header portion 8, and the second inlet / outlet pipe 5b communicates with the second flow path via the second header portion 9. It communicates with the right end of 21.

In the water heat exchanger 1 having such a configuration, for example, when the first fluid is heated by the second fluid, the first inlet / outlet pipe 4b is used as the inlet of the first fluid, and the first inlet / outlet pipe 4a is used as the first fluid. The second inlet / outlet pipe 5b can be used as the inlet of the second fluid, and the second inlet / outlet pipe 5a can be used as the outlet of the second fluid. Then, in this case, in the water heat exchanger 1, the first fluid flows through the first flow path 11 from the bottom to the top and is heated, and the second fluid flows through the second flow path 21 from right to left. It will function as a heat exchanger that flows and cools. Further, in the water heat exchanger 1, for example, when the first fluid is cooled by the second fluid, the first inlet / outlet pipe 4b is used as the inlet of the first fluid, and the first inlet / outlet pipe 4a is used as the outlet of the first fluid. The second inlet / outlet pipe 5a can be used as the inlet of the second fluid, and the second inlet / outlet pipe 5b can be used as the outlet of the second fluid. Then, in this case, in the water heat exchanger 1, the first fluid flows through the first flow path 11 from bottom to top and is cooled, and the second fluid flows through the second flow path 21 from left to right. It will function as a heat exchanger that is heated as it flows.

Here, when water as the first fluid is heated by the second fluid, the flow path cross-sectional area S11a of the first flow path 11 in the first fluid outlet vicinity portion 11a located near the outlet of the first fluid Is formed so as to be larger than the flow path cross-sectional area S11b in the portion 11b on the upstream side of the first fluid outlet vicinity portion 11a. Specifically, the flow path width W11a of the first flow path 11 in the first fluid outlet vicinity portion 11a is formed to be larger than the flow path width W11b in the portion 11b on the upstream side of the first fluid outlet vicinity portion 11a. By doing so, the flow path cross-sectional area S11a is made larger than the flow path cross-sectional area S11b. Further, the first fluid outlet vicinity portion 11a is from the inlet side (here, the end on the first inlet / outlet pipe 4b side) to the outlet side (here, the end on the first inlet / outlet pipe 4a side) of the first flow path 11. ), Which has a flow path length of 20 to 50% closer to the outlet side.

Further, here, when the first fluid is cooled by the refrigerant as the second fluid, the flow path cross-sectional area S21a of the second flow path 21 in the second fluid outlet vicinity portion 21a located near the outlet of the second fluid Is formed so as to be larger than the flow path cross-sectional area S21b in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. Specifically, the flow path width W21a of the second flow path 21 in the second fluid outlet vicinity portion 21a is formed to be larger than the flow path width W21b in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. By doing so, the flow path cross-sectional area S21a is made larger than the flow path cross-sectional area S21b. Further, the second fluid outlet vicinity portion 21a is from the inlet side (here, the end on the second inlet / outlet pipe 5a side) to the outlet side (here, the end on the second inlet / outlet pipe 5b side) of the second flow path 21. ), Which has a flow path length of 20 to 50% closer to the outlet side.

In such a water heat exchanger 1, as described above, when water as the first fluid is heated by the second fluid, the flow path cross-sectional area of the first flow path 11 in the vicinity of the first fluid outlet 11a Since S11a is made larger than the portion 11b on the upstream side thereof, the decrease in heat transfer coefficient due to the decrease in the flow velocity of the first fluid in the first flow path 11 is limited to only the portion near the first fluid outlet 11a, and the first It is possible to prevent the scale deposited when the fluid is heated from being clogged in the vicinity of the first fluid outlet 11a. As described above, here, it is possible to suppress the clogging of the first flow path 11 in the water heat exchanger 1 while minimizing the decrease in the heat transfer coefficient.

Further, in such a water heat exchanger 1, when the first fluid is cooled by the refrigerant as the second fluid as described above, the second flow path 21 is a flow path in the vicinity of the second fluid outlet 21a. Since the cross-sectional area S21a is larger than the portion 21b on the upstream side thereof, the decrease in heat transfer rate due to the decrease in the flow velocity of the second fluid in the second flow path 21 is limited to only the portion 21a in the vicinity of the second fluid outlet. The second fluid containing a large amount of gas components that increase with evaporation can be smoothly flowed to the portion 21a near the outlet of the second fluid. As described above, here, it is possible to suppress an increase in the pressure loss of the second flow path 21 in the water heat exchanger 1 while minimizing the decrease in the heat transfer coefficient.

(2) Modification 1
In the water heat exchanger 1 of the above embodiment, when water as the first fluid is heated by the second fluid, the flow path cross-sectional area S11a in the vicinity of the first fluid outlet 11a is upstream of the first flow path 11. It is made larger than the side portion 11b. Moreover, in the water heat exchanger 1 of the above embodiment, when the first fluid is cooled by the refrigerant as the second fluid, the flow path cross-sectional area S21a in the second fluid outlet vicinity portion 21a is set for the second flow path 21. It is made larger than the upstream portion 21b. However, the present invention is not limited to this, and even if a configuration is applied only to the first flow path 11 or the second flow path 21 so that the flow path cross-sectional area in the vicinity of the fluid outlet is larger than that on the upstream side. Good.

For example, when the first fluid is cooled by the refrigerant as the second fluid, the second flow path 21 has the flow path cross-sectional area S21a in the vicinity of the second fluid outlet 21a on the upstream side as shown in FIG. As shown in FIG. 5, the cross-sectional area of the flow path (here, the flow path width) of the first flow path 11 does not change from the inlet side to the exit side of the first flow path 11. The configuration may be applied.

Further, for example, when water as the first fluid is heated by the second fluid, the first flow path 11 has a flow path cross-sectional area S11a in the vicinity of the first fluid outlet 11a as shown in FIG. The second flow path 21 is made larger than the upstream portion 11b, and as shown in FIG. 6, the flow path cross-sectional area (here, the flow path width) extends from the inlet side to the exit side of the second flow path 21. An unchanged configuration may be applied.

Even in the configuration of this modification, the same effect as that of the above embodiment can be obtained.

(3) Modification example 2
In the water heat exchanger 1 of the above embodiment and the first modification, the first flow path 11 and the second flow path 21 are arranged so as to form a orthogonal flow, but the present invention is not limited to this.

For example, a second flow path extending from one end of the second layer 20 (the left end of the second layer 20 in FIG. 3) to the other end (the right end of the second layer 20 in FIG. 3) along the lateral direction. As shown in FIGS. 7 and 8, 21 is drawn from one end of the second layer 20 (the lower end of the second layer 20 in FIG. 8) to the other end (the upper end of the second layer 20 in FIG. 8) along the vertical direction. The first flow path 11 and the second flow path 21 may be arranged so as to form a countercurrent (or parallel flow) so as to extend to the part). In this case, the second inlet / outlet pipes 5a and 5b and the second headers 8 and 9 are provided at the lower and upper parts of the casing 2. In this configuration, when the first fluid is heated by the second fluid, the first fluid flows from the bottom to the top of the first flow path 11 and is heated, and the second fluid flows through the second flow path 21 from the top. It will function as a heat exchanger that flows downward and is cooled. Further, in this configuration, when the first fluid is cooled by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow path 21. It will function as a heat exchanger that flows from bottom to top and is heated.

Even in the configuration of this modification, the same effects as those of the above-described embodiment and modification 1 can be obtained.

(4) Modification 3
In the water heat exchanger 1 of the above embodiment and the first modification, the first flow path 11 and the second flow path 21 are arranged so as to form a orthogonal flow, but the present invention is not limited to this.

For example, the second flow path 21 is divided into a plurality of flow path groups, and these flow path groups are connected in series so that the first flow path 11 and the second flow path 21 are orthogonal countercurrents ( Alternatively, they may be arranged so as to form an orthogonal parallel flow). Specifically, in the configuration shown in FIG. 9, the second flow path 21 is divided into three flow path groups 21A, 21B, and 21C in the arrangement direction of the second flow path 21 (here, the vertical direction on the paper surface of FIG. 9). doing. Then, by providing a partition member in the second header 9, the space in the second header 9 communicates with the space 9a communicating with the second inlet / outlet pipe 5b and the right end of the second flow path 21 constituting the flow path group 21A. , The space 9b communicating with the right end of the second flow path 21 constituting the flow path groups 21B and 21C. Further, by providing a partition member in the second header 8, the space in the second header 8 communicates with the space 8a communicating with the second inlet / outlet pipe 5a and the left end of the second flow path 21 constituting the flow path group 21C. , The space 8b communicating with the left end of the second flow path 21 constituting the flow path groups 21A and 21B. As a result, the flow path groups 21A, 21B, and 21C of the second flow path 21 are connected in series via the second headers 8 and 9, and the first flow path 11 and the second flow path 21 are orthogonally opposed to each other. Or orthogonal parallel flow). In this configuration, when the first fluid is heated by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is heated, and the second fluid flows through the second flow path 21. It functions as a heat exchanger that flows from top to bottom and is cooled while folding back to the left and right in the order of groups 21A, 21B, and 21C. Further, in this configuration, when the first fluid is cooled by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow path 21. It functions as a heat exchanger that flows from the bottom to the top while being folded back to the left and right in the order of the flow path groups 21C, 21B, and 21A and is heated. In this case, the flow path group 21A located near the outlet of the second fluid is defined as the second fluid outlet vicinity portion 21a, and the flow path groups 21B and 21C are the portions upstream of the second fluid outlet vicinity portion 21a. As 21b, the flow path width W21a of the second flow path 21 constituting the flow path group 21A constituting the flow path group 21A is larger than the flow path width W21b of the second flow path 21 constituting the flow path groups 21B and 21C. It is formed so as to be. As a result, when the first fluid is cooled by the refrigerant as the second fluid, the flow path cross-sectional area S21a in the second fluid outlet vicinity portion 21a becomes the flow in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. It can be formed so as to be larger than the road cross-sectional area S21b.

In the configuration shown in FIG. 9, the space in the second headers 8 and 9 is divided into spaces 8a, 8b, 9a and 9b so that the flow path groups 21A, 21B and 21C are connected in series. , Not limited to this. For example, as shown in FIG. 10, connecting flow paths 29a and 29b having the same functions as the spaces 8b and 9b may be formed at the left end and the right end of the second flow path 21. That is, the connection flow path 29a that communicates between the left ends of the second flow paths 21 that form the flow paths groups 21A and 21B and the right end of the second flow paths 21 that form the flow paths groups 21B and 21C communicate with each other. The connecting flow path 29b is formed in the second layer 20. Here, a groove forming the connection flow paths 29a and 29b can be formed in the second plate member 22. In this case, the second header 8 may have only the space corresponding to the space 8a of FIG. 9, and the second header 9 may have only the space corresponding to the space 9a of FIG.

Even in the configuration of this modification, the same effects as those of the above-described embodiment and modification 1 can be obtained.

(5) Modification example 4
In the water heat exchangers 1 of the above-described embodiments and modifications 1 to 3, when water as the first fluid is heated by the second fluid, the first flow path 11 is located near the outlet of the first fluid. The flow path width W11a of the first flow path 11 in the portion 11a near the fluid outlet is formed to be larger than the flow path width W11b in the portion 11b on the upstream side of the portion 11a near the first fluid outlet. As a result, when water as the first fluid is heated by the second fluid, the flow path cross-sectional area S11a in the first fluid outlet vicinity portion 11a is the portion 11b on the upstream side of the first fluid outlet vicinity portion 11a. It is made larger than the flow path cross-sectional area S11b in the above, and clogging of the portion near the outlet of the first flow path 11 due to scale precipitation is suppressed.

However, when water as the first fluid is heated by the second fluid, the flow path cross-sectional area S11a in the first fluid outlet vicinity portion 11a is upstream of the first fluid outlet vicinity portion 11a for the first flow path 11. The configuration for forming the side portion 11b so as to be larger than the flow path cross-sectional area S11b is not limited to this.

Specifically, when water as the first fluid is heated by the second fluid, the number of flow paths in the first fluid outlet vicinity portion 11a is larger than that in the first fluid outlet vicinity portion 11a for the first flow path 11. The first flow paths 11 may be merged so as to be smaller than the number of flow paths in the upstream portion. For example, as shown in FIG. 11, two first flow paths 11 adjacent to each other in the arrangement direction of the first flow path 11 are merged at the first fluid outlet vicinity portion 11a to form one, and after merging. The flow path width W11a in the first fluid outlet vicinity portion 11a may be formed to be larger than the total of the flow path width W11b in the portion 11b on the upstream side of the first fluid outlet vicinity portion 11a before merging. .. As a result, when water as the first fluid is heated by the second fluid, with respect to the first flow path 11, the flow path cross-sectional area S11a in the vicinity of the first fluid outlet 11a after merging becomes the first fluid before merging. It can be made larger than the total of the flow path cross-sectional areas S11b in the portion 11b on the upstream side of the exit vicinity portion 11a.

(6) Modification 5
In the water heat exchangers 1 of the above-described embodiments and modifications 1 to 4, when the first fluid is cooled by the refrigerant as the second fluid, the second flow path 21 is located near the outlet of the second fluid. The flow path width W21a of the second flow path 21 in the two fluid outlet vicinity portion 21a is formed so as to be larger than the flow path width W21b in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. As a result, when the first fluid is cooled by the refrigerant as the second fluid, the flow path cross-sectional area S21a in the second fluid outlet vicinity portion 21a is the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. In order to make it larger than the flow path cross-sectional area S21b in the above, the increase in the pressure loss of the second flow path 21 due to the increase in the gas component flowing through the second flow path 21 as the second fluid evaporates is suppressed. There is.

However, when the first fluid is cooled by the refrigerant as the second fluid, the flow path cross-sectional area S21a in the second fluid outlet vicinity portion 21a is upstream of the second fluid outlet vicinity portion 21a in the second flow path 21. The configuration for forming the side portion 21b so as to be larger than the flow path cross-sectional area S21b is not limited to this.

Specifically, when the first fluid is cooled by the refrigerant as the second fluid, the number of flow paths in the second fluid outlet vicinity portion 21a is larger than that in the second fluid outlet vicinity portion 21a for the second flow path 21. The second flow path 21 may be merged so as to be smaller than the number of flow paths in the upstream portion. For example, as shown in FIG. 12, two second flow paths 21 adjacent to each other in the arrangement direction of the second flow path 21 are merged at the second fluid outlet vicinity portion 21a to form one, and after merging. The flow path width W21a in the second fluid outlet vicinity portion 21a may be formed to be larger than the total of the flow path width W21b in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a before merging. .. As a result, the flow path cross-sectional area S21a in the second fluid outlet vicinity portion 21a after merging is made larger than the total of the flow path cross-sectional areas S21b in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a before merging. be able to.

Further, contrary to the configuration in which the flow path cross-sectional area S21a is made larger than the total of the flow path cross-sectional areas S21b by merging the second flow path 21 shown in FIG. 12 at the portion near the second fluid outlet 21a, the second flow path is second. By branching the number of flow paths in the fluid outlet vicinity portion 21a so as to be larger than the number of flow paths in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a, the total of the flow path cross-sectional areas S21a is the flow path cross-sectional area. It may be larger than the total of S21b. For example, in a configuration in which the second flow path 21 as in the modification 3 is divided into a plurality of flow path groups 21A, 21B, 21C and these flow path groups 21A, 21B, 21C are connected in series, FIG. As shown in the above, the flow path group 21A located near the outlet of the second fluid is designated as the second fluid outlet vicinity portion 21a, and the flow path groups 21B and 21C are designated as the portions 21b on the upstream side of the second fluid outlet vicinity portion 21a. The number of flow paths N21a of the second flow path 21 constituting the flow path group 21A may be larger than the number of flow paths N21b in the flow path groups 21B and 21C. Here, the flow path widths W21a and W21b (flow path cross-sectional areas S21a and S21b) of each of the second flow paths 21 are the same, and by changing the number of flow paths, the flow path cross-sectional area S21a in the flow path group 21A can be obtained. The total of the flow path cross-sectional areas S21b in the flow path groups 21B and 21C is changed. As described above, in the configuration in which the number of flow paths N21a in the portion 21a near the second fluid outlet is increased and the number of flow paths N21a in the upstream portion 21b is increased, the pressure loss of the second flow path 21 in the water heat exchanger 1 is increased. The number of flow paths in the vicinity of the inlet of the second fluid is reduced, so that the distribution performance of the second fluid in the second flow path 21 can be kept good. In particular, not only the number of flow paths N21a in the flow path group 21A is larger than the number of flow paths N21b in the flow path groups 21B and 21C on the upstream side, but also the order of the flow path groups 21A, 21B and 21C, that is, the first If the number of flow paths is reduced as the two fluids approach the vicinity of the inlet, the distribution performance of the second fluid in the second flow path 21 is effectively contributed.

In the present invention, a first layer having a plurality of rows of first flow paths through which water as a first fluid flows, and a second layer having a plurality of rows of second flow paths through which a refrigerant as a second fluid flows are formed. Is configured to be laminated, and is widely applicable to a water heat exchanger that exchanges heat between a first fluid and a second fluid.

1 Water heat exchanger 10 First layer 11 First flow path 11a Near the first fluid outlet 11b Upstream side of the vicinity of the first fluid outlet 20 Second layer 21 Second flow path 21a Near the second fluid outlet 21b A part on the upstream side of the vicinity of the second fluid outlet

Japanese Unexamined Patent Publication No. 2010-117102

Claims (1)

When the first plate material (12) and the second plate material (22) are alternately laminated in the stacking direction, so that the first flow path (11) through which water as the first fluid flows is viewed along the stacking direction. The first layer (10) formed in a plurality of rows and the second flow path (21) through which the refrigerant as the second fluid flows are formed in a plurality of rows when viewed along the stacking direction. ), In a water heat exchanger that exchanges heat between the first fluid and the second fluid.
When the first layer is viewed along the stacking direction, the first flow path extends from one end to the other end of the first layer along the direction intersecting the arrangement direction of the first flow path. It is extended and
When the second layer is viewed along the stacking direction, the second flow path extends from one end to the other end of the second layer along the direction intersecting the arrangement direction of the second flow path. It is extended and
The water heat exchanger has a first header portion that communicates with the second flow path at one end portion of the second layer and a second header portion that communicates with the second flow path at the other end portion of the second layer. Has a header part and
When the first fluid is cooled by the second fluid, the cross-sectional area of the flow path in the second fluid outlet vicinity portion (21a) located near the outlet of the second fluid is the second flow path. It is formed so as to be larger than the flow path cross-sectional area in the portion (21b) on the upstream side of the vicinity of the fluid outlet.
The second flow path merges so that the number of flow paths in the vicinity of the second fluid outlet is smaller than the number of flow paths in the portion on the upstream side of the vicinity of the second fluid outlet. The flow path cross-sectional area in the vicinity of the fluid outlet is formed to be larger than the flow path cross-sectional area in the portion upstream of the second fluid outlet vicinity.
Water heat exchanger (1).

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