JP2018112382A - Water heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress an increase in pressure loss and clogging of a flow passage by devising a flow passage shape of a water heat exchanger that is constituted by stacking a first layer where a first flow passage where water as the first fluid flows is formed in a plurality of rows and a second layer where a second flow passage where a refrigerant as the second fluid flows is formed in a plurality of rows and that exchanges heat between the first fluid and the second fluid.SOLUTION: A first flow passage (11) is so formed that when a first fluid is heated with a second fluid, the flow passage cross-sectional area thereof is larger at a first fluid exit vicinity part (11a) located nearby an exit of the first fluid than at a part (11b) upstream therefrom. Further, a second flow passage (21) is so formed that when the first fluid is cooled with the second fluid, the flow passage cross-sectional area thereof is larger at a second fluid exit vicinity part (21a) located nearby an exit of the second fluid than at a part (21b) upstream therefrom.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a water heat exchanger, in particular, a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a plurality of second flow paths through which refrigerant as a second fluid flows. It is related with the water heat exchanger which is comprised by laminating | stacking the made 2nd layer, and performs heat exchange with a 1st fluid and a 2nd fluid.

  2. Description of the Related Art Conventionally, in a heat pump type air conditioner or heat pump type hot water heater, a water heat exchanger that performs heat exchange between water as a first fluid and a refrigerant (such as a chlorofluorocarbon refrigerant, a natural refrigerant, or a brine) as a second fluid has been provided. It is used. As such a water heat exchanger, as shown in Patent Document 1 (Japanese Patent Laid-Open No. 2010-117102), a first layer in which a plurality of first flow paths through which a first fluid flows is formed, and a second fluid There is a configuration in which a second layer in which a plurality of second flow paths are formed is stacked.

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

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

  An object of the present invention is to provide a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a second layer in which a plurality of second flow paths through which a refrigerant as a second fluid flows are formed. In a hydrothermal exchanger that performs heat exchange between the first fluid and the second fluid, an increase in pressure loss and clogging of the channel are suppressed by devising the channel shape. There is.

  The water heat exchanger according to the first aspect includes a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a plurality of second flow paths through which refrigerant as a second fluid flows. The formed second layer is laminated to perform heat exchange between the first fluid and the second fluid. The first flow path has one end from the other end along the direction intersecting the arrangement direction of the first flow paths when the first layer is viewed along the stacking direction of the first and second layers. It extends to the part. The second flow path extends from one end of the second layer to the other end along the direction intersecting the arrangement direction of the second flow paths when the second layer is viewed along the stacking direction. In this case, when the first fluid is heated by the second fluid, the flow path cross-sectional area in the vicinity of the first fluid outlet where the first flow path is located in the vicinity of the first fluid outlet is in the vicinity of the first fluid outlet. It is formed so as to be larger than the cross-sectional area of the flow path in the portion upstream of the portion.

  Here, as described above, since the flow passage cross-sectional area in the vicinity of the first fluid outlet is larger than the upstream portion of the first flow passage, the flow velocity of the first fluid in the first flow passage is reduced. It is possible to prevent the scale that deposits when the first fluid is heated from clogging in the vicinity of the first fluid outlet, while limiting the decrease in the heat transfer coefficient due to the above. Thus, the clogging of the first flow path in the water heat exchanger can be suppressed while minimizing the decrease in the heat transfer coefficient.

  The water heat exchanger according to the second aspect is the water heat exchanger according to the first aspect, wherein the first flow path is upstream of the first fluid outlet vicinity part in the first fluid outlet vicinity part. It merges so that it may become fewer than the number of the flow paths in the side part.

  Here, as described above, the flow path breakage in the vicinity of the first fluid outlet is achieved by merging the first flow paths so that the number of flow paths in the vicinity of the first fluid outlet is smaller than the upstream portion. The area can be made larger than the upstream portion.

  The water heat exchanger according to the third aspect includes a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a plurality of second flow paths through which refrigerant as a second fluid flows. The formed second layer is laminated to perform heat exchange between the first fluid and the second fluid. The first flow path has one end from the other end along the direction intersecting the arrangement direction of the first flow paths when the first layer is viewed along the stacking direction of the first and second layers. It extends to the part. The second flow path extends from one end of the second layer to the other end along the direction intersecting the arrangement direction of the second flow paths when the second layer is viewed along the stacking direction. In this case, when the first fluid is cooled by the second fluid, the flow passage cross-sectional area in the vicinity of the second fluid outlet where the second flow passage is located in the vicinity of the second fluid outlet is in the vicinity of the second fluid outlet. It is formed so as to be larger than the cross-sectional area of the flow path in the portion upstream of the portion.

  Here, as described above, since the flow passage cross-sectional area in the vicinity of the second fluid outlet is larger than the upstream portion of the second flow passage, the flow velocity of the second fluid in the second flow passage is reduced. The second fluid containing a large amount of gas components that increase with evaporation can be smoothly flowed to the vicinity of the second fluid outlet, while the decrease in the heat transfer coefficient due to the above is limited only 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 a decrease in the heat transfer coefficient.

  The water heat exchanger according to a fourth aspect is the water heat exchanger according to the third aspect, wherein the second flow path is upstream of the second fluid outlet vicinity part in the second fluid outlet vicinity part. It merges so that it may become fewer than the number of the flow paths in the side part.

  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 part, the cross-sectional area of the flow path in the vicinity of the second fluid outlet is changed to the upstream side. It can be larger than the part.

  A water heat exchanger according to a fifth aspect is the water heat exchanger according to the third aspect, wherein the second flow path is upstream of the second fluid outlet vicinity in the second fluid outlet vicinity. It branches so that it may become more than the number of the flow paths in the side part.

  Here, as described above, by branching so that the number of channels in the vicinity of the second fluid outlet is larger than the upstream portion, the cross-sectional area of the channel in the vicinity of the second fluid outlet is changed to the upstream side. It can be larger than the part. In addition, this reduces the number of flow paths in the vicinity of the inlet of the second fluid here, so that the distribution performance of the second fluid in the second flow path can be kept good.

  In the water heat exchanger according to the sixth aspect, when the first fluid is cooled by the second fluid in the water heat exchanger according to the first or second aspect, the second flow path is formed of the second fluid. The channel cross-sectional area in the vicinity of the second fluid outlet located in the vicinity of the outlet is formed to be larger than the channel cross-sectional area in the upstream portion of the vicinity of the second fluid outlet.

  Here, as described above, since the flow passage cross-sectional area in the vicinity of the second fluid outlet is larger than the upstream portion of the second flow passage, the flow velocity of the second fluid in the second flow passage is reduced. The second fluid containing a large amount of gas components that increase with evaporation can be smoothly flowed to the vicinity of the second fluid outlet, while the decrease in the heat transfer coefficient due to the above is limited only 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 a decrease in the heat transfer coefficient.

  As described above, according to the present invention, the first fluid is heated while limiting the decrease in the heat transfer coefficient due to the decrease in the flow velocity of the first fluid in the first flow path to only the vicinity of the first fluid outlet. Since the scale that precipitates when the operation is performed can be prevented from clogging in the vicinity of the first fluid outlet, the clogging of the first flow path in the water heat exchanger can be suppressed while minimizing the decrease in the heat transfer coefficient. it can. In addition, according to the present invention, the reduction in the heat transfer coefficient due to the decrease in the flow velocity of the second fluid in the second flow path is limited only to the vicinity of the second fluid outlet, and the second gas containing many gas components that increase with evaporation. Since the two fluids can flow smoothly in the vicinity of the second fluid outlet, an increase in the pressure loss of the second flow path in the water heat exchanger can be suppressed while minimizing the decrease in the heat transfer coefficient.

It is a figure which shows the external appearance of the water heat exchanger concerning one Embodiment of this invention. It is a figure which shows the 1st flow path of the water heat exchanger concerning one Embodiment of this invention. It is a figure which shows the 2nd flow path of the water heat exchanger concerning one Embodiment of this invention. It is a perspective view which shows the lamination | stacking state of the 1st flow path and 2nd flow path of the water heat exchanger concerning one Embodiment of this invention. It is a figure (corresponding to Drawing 2) showing the 1st channel of the water heat exchanger concerning modification 1 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 1 of the present invention. It is a figure which shows the external appearance of the water heat exchanger concerning the modification 2 of this invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 2 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 3 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 3 of the present invention. It is a figure (corresponding to Drawing 2) showing the 1st channel of the water heat exchanger concerning modification 4 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 5 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 5 of the present invention.

  Hereinafter, an embodiment of a water heat exchanger concerning the present invention and its modification are described based on a drawing. In addition, the specific structure of the water heat exchanger concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of 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 performs heat exchange between water as a first fluid and refrigerant as a second fluid in a heat pump air conditioner, a heat pump water heater, or the like. In the following description, “top”, “bottom”, “left”, “right”, “vertical”, “horizontal” with reference to the front surface of the water heat exchanger 1 shown in FIGS. However, these expressions are expressions for convenience of explanation, and do not mean the actual arrangement of the water heat exchanger 1 and its constituent parts.

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

  The heat exchange unit 3 includes a first layer 10 in which a plurality of first flow paths 11 through which a first fluid flows are formed, a second layer 20 in which a plurality of second flow paths 21 through which a second fluid flows are formed, Are laminated. Here, the direction in which the first layer 10 and the second layer 20 are stacked (here, the direction from the front side to the back side in FIGS. 1 to 3) is defined as the stacking direction. In addition, the direction in which the plurality of first flow paths 11 are arranged (here, the left-right direction 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 arranged (here, FIG. 3). (The vertical direction of the paper surface) is the arrangement direction of the second flow paths 21. And when the 1st flow path 11 sees the 1st layer 10 along the lamination direction of the 1st and 2nd layers 10 and 20, the direction (here, it intersects with the arrangement direction of the 1st flow path 11) 2 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 vertical direction and vertical direction of FIG. ing. Further, the second flow path 21 is a direction that intersects with the arrangement direction of the second flow paths 21 when the second layer 20 is viewed along the stacking direction of the first and second layers 10 and 20 (here, 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 horizontal direction in FIG. It extends. Thus, the 1st flow path 11 and the 2nd flow path 20 are arrange | positioned so that a cross flow may be made here.

  And here, the heat exchange part 3 which has the laminated structure of the 1st layer 10 and the 2nd layer 20 is the 1st board | plate material 12 in which the groove | channel which makes the 1st flow path 11 was formed in the single side | surface, and the 2nd flow path 21. And the second plate material 22 having grooves formed on one side thereof are alternately laminated. The 1st and 2nd board | plate materials 12 and 22 are formed with the metal raw 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. And after laminating | stacking a predetermined number of 1st and 2nd board | plate materials 12 and 22 by which such groove processing was made | formed, between 1st and 2nd board | plate materials 12 and 22 is joined using joining processes, such as a diffusion joining, for example. Thereby, the heat exchange part 3 which has the laminated structure of the 1st layer 10 and the 2nd layer 20 is obtained. In addition, here, although the groove | channel which makes the flow paths 11 and 21 is formed in the single side | surface of both the 1st and 2nd board | plate materials 12 and 22, it is not limited to this, The 1st and 2nd board | plate materials 12 are not limited to this. , 22 may be formed with grooves 11, 21 on both surfaces, or grooves 11, 21 may be formed on both surfaces of the first and second plates 12, 22. May be.

  Here, the first inlet / outlet pipes 4 a and 4 b are provided at the upper part and the lower part of the casing 2. In the casing 2, a first header portion 6 in which a space for joining the upper end portions of the first flow path 11 is formed in the upper portion and a space for joining the lower end portions of the first flow passage 11 are formed in the lower portion thereof. The first header portion 7 is provided. The first inlet / outlet pipe 4 a communicates with the upper end of the first flow path 11 via the first header section 6, and the first inlet / outlet pipe 4 b passes through the first header section 7 to the first flow path. 11 communicates with the lower end portion. The 2nd entrance / exit pipe | tube 5a, 5b is provided in the left part and the right part of the casing 2 here. In the casing 2, a second header portion 8 in which a space for joining the left end portions of the second flow path 21 is formed at the left portion thereof, and a space for joining the right end portions of the second flow passage 21 at the right portion thereof. And a second header portion 9 formed with a. The second inlet / outlet pipe 5 a communicates with the left end of the second flow path 21 via the second header portion 8, and the second inlet / outlet pipe 5 b passes through the second header section 9 to the second flow path. 21 communicates with the right end portion.

  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 serves as the inlet of the first fluid, and the first inlet / outlet pipe 4a serves 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. 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 moves through the second flow path 21 from the right to the left. It will function as a heat exchanger that flows and cools. 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, 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 an inlet for the second fluid, and the second inlet / outlet pipe 5b can be used as an outlet for the second fluid. In this case, in the water heat exchanger 1, the first fluid flows in the first flow path 11 from the bottom to the top and is cooled, and the second fluid moves in the second flow path 21 from the left to the right. It functions as a heat exchanger that flows and heats.

  And here, when water as the first fluid is heated by the second fluid, the channel cross-sectional area S11a in the first fluid outlet vicinity portion 11a located in the vicinity of the outlet of the first fluid with respect to the first channel 11 However, it forms so that it may become larger than the flow-path cross-sectional area S11b in the part 11b upstream from the 1st fluid exit vicinity part 11a. Specifically, the channel width W11a of the first channel 11 in the first fluid outlet vicinity portion 11a is formed to be larger than the channel width W11b in the portion 11b upstream of the first fluid outlet vicinity portion 11a. By doing so, the channel cross-sectional area S11a is made larger than the channel cross-sectional area S11b. Further, the first fluid outlet vicinity portion 11a refers to the end portion on the outlet side (here, the first inlet / outlet pipe 4a side) from the inlet side (here, the end part on the first inlet / outlet pipe 4b side) of the first flow path 11. The portion having a flow length of 20 to 50% closer to the outlet side among the flow lengths up to).

  Further, here, when the first fluid is cooled by the refrigerant as the second fluid, the channel cross-sectional area S21a in the second fluid outlet vicinity portion 21a located in the vicinity of the outlet of the second fluid with respect to the second channel 21. However, it is formed so as to be larger than the channel cross-sectional area S21b in the upstream portion 21b of the second fluid outlet vicinity portion 21a. Specifically, the flow passage width W21a of the second flow passage 21 in the second fluid outlet vicinity portion 21a is formed to be larger than the flow passage width W21b in the portion 21b upstream of the second fluid outlet vicinity portion 21a. By doing so, the channel cross-sectional area S21a is made larger than the channel cross-sectional area S21b. Further, the second fluid outlet vicinity portion 21a refers to the end portion on the outlet side (here, the second inlet / outlet tube 5b side) from the inlet side (here, the end portion on the second inlet / outlet tube 5a side) of the second flow path 21. The portion having a flow length of 20 to 50% closer to the outlet side among the flow lengths up to).

  In such a water heat exchanger 1, as described above, when water as the first fluid is heated by the second fluid, the channel cross-sectional area in the first fluid outlet vicinity portion 11a with respect to the first channel 11 is described. Since S11a is made larger than the portion 11b on the upstream side, the reduction in the heat transfer coefficient due to the decrease in the flow velocity of the first fluid in the first flow path 11 is limited only to the first fluid outlet vicinity portion 11a. The scale that precipitates when the fluid is heated can be made difficult to clog the first fluid outlet vicinity portion 11a. As described above, the clogging of the first flow path 11 in the water heat exchanger 1 can be suppressed while minimizing the decrease in the heat transfer coefficient.

  Further, in the water heat exchanger 1 as described above, when the first fluid is cooled by the refrigerant as the second fluid as described above, the flow passage in the second fluid outlet vicinity portion 21a with respect to the second flow passage 21. Since the cross-sectional area S21a is larger than the upstream portion 21b, the decrease in the heat transfer coefficient due to the decrease in the flow velocity of the second fluid in the second flow path 21 is limited only to the second fluid outlet vicinity portion 21a, The second fluid containing a lot of gas components that increase with evaporation can flow smoothly to the second fluid outlet vicinity 21a. 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 a decrease in the heat transfer coefficient.

(2) Modification 1
In the water heat exchanger 1 of the above-described embodiment, when water as the first fluid is heated by the second fluid, the channel cross-sectional area S11a in the first fluid outlet vicinity portion 11a is set upstream of the first channel 11. It is 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 passage cross-sectional area S21a in the second fluid outlet vicinity portion 21a is set for the second flow passage 21. It is larger than the upstream portion 21b. However, the present invention is not limited to this, and a configuration in which the cross-sectional area in the vicinity of the fluid outlet is made larger than the upstream portion only in the first flow path 11 or the second flow path 21 may be applied. Good.

  For example, when the first fluid is cooled by the refrigerant as the second fluid, as shown in FIG. 3, for the second flow channel 21, the flow channel cross-sectional area S21a in the second fluid outlet vicinity portion 21a is set to the upstream side. The first channel 11 has a channel cross-sectional area (here, channel width) that does not change from the inlet side to the outlet side of the first channel 11 as shown in FIG. A configuration may be applied.

  Further, for example, when water as the first fluid is heated by the second fluid, the flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a is set as the first flow passage 11 as shown in FIG. As shown in FIG. 6, the second channel 21 has a channel cross-sectional area (here, channel width) that extends from the inlet side to the outlet side of the second channel 21. A configuration that does not change may be applied.

  Also in the configuration of the present modification, it is possible to obtain the same operational effects as in the above embodiment.

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

  For example, the second flow path that extends 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 horizontal direction. 7 and 8, as shown in FIGS. 7 and 8, 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 counter flow (or parallel flow). In this case, the second inlet / outlet pipes 5 a and 5 b and the second headers 8 and 9 are provided at the lower part and the upper part of the casing 2. 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 from the top. It will function as a heat exchanger that flows downward and is cooled. 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.

  Also 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 embodiment and the first modification, the first flow path 11 and the second flow path 21 are arranged to form a cross flow, but the present invention is not limited to this.

  For example, the second channel 21 is divided into a plurality of channel groups, and these channel groups are connected in series so that the first channel 11 and the second channel 21 are orthogonally opposed ( 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 paths 21 (here, the vertical direction in FIG. 9). doing. Then, by providing a partition member on the second header 9, the space in the second header 9 and the space 9a communicating with the right end portion of the second channel 21 constituting the second inlet / outlet pipe 5b and the channel group 21A, And a space 9b communicating with the right end of the second flow path 21 constituting the flow path groups 21B and 21C. In addition, by providing a partition member in the second header 8, the space in the second header 8 and the space 8a communicating with the left end portion of the second flow path 21 constituting the second inlet / outlet pipe 5a and the flow path group 21C And a space 8b communicating with the left end of the second flow path 21 constituting the flow path groups 21A and 21B. Thereby, 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 ( (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 will function as a heat exchanger that flows from top to bottom while being folded back to the left and right in the order of the groups 21A, 21B, and 21C and that is cooled. 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 and heats from the bottom to the top while being folded left and right in the order of the flow path groups 21C, 21B, and 21A. In this case, the flow path group 21A located in the vicinity of the second fluid outlet is the second fluid outlet vicinity part 21a, and the flow path groups 21B and 21C are upstream of the second fluid outlet vicinity part 21a. 21b, the channel width W21a of the second channel 21 constituting the channel group 21A constituting the channel group 21A is larger than the channel width W21b of the second channel 21 constituting the channel groups 21B and 21C. It is formed to become. Thus, 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 flows in the portion 21b on the upstream side of the second fluid outlet vicinity portion 21a. It can be formed 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 the spaces 8a, 8b, 9a, and 9b so that the flow path groups 21A, 21B, and 21C are connected in series. However, the present invention is not limited to this. For example, as shown in FIG. 10, connection channels 29 a and 29 b having the same functions as the spaces 8 b and 9 b may be formed at the left end and the right end of the second channel 21. That is, the connection flow path 29a that communicates between the left ends of the second flow paths 21 constituting the flow path groups 21A and 21B and the right end of the second flow path 21 that constitutes the flow path groups 21B and 21C are communicated. The connection flow path 29b to be formed is formed in the second layer 20. Here, the groove | channel which makes the connection flow paths 29a and 29b in the 2nd board | plate material 22 can be formed. In this case, the second header 8 can have only a space corresponding to the space 8a in FIG. 9, and the second header 9 can have only a space corresponding to the space 9a in FIG.

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

(5) Modification 4
In the water heat exchanger 1 of the said embodiment and the modifications 1-3, when heating the water as a 1st fluid with a 2nd fluid, about the 1st flow path 11, it is located in the exit vicinity of the 1st fluid. The channel width W11a of the first channel 11 in the first fluid outlet vicinity portion 11a is formed to be larger than the channel width W11b in the portion 11b on the upstream side of the first fluid outlet vicinity portion 11a. 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 higher than the first fluid outlet vicinity portion 11a. Is larger than the flow path cross-sectional area S11b in order to suppress clogging in the vicinity of the outlet of the first flow path 11 due to scale deposition.

  However, when water as the first fluid is heated by the second fluid, the flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a is upstream of the first fluid outlet vicinity portion 11a. The configuration for forming the passage portion 11b 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 of the first flow path 11 is larger than that in the first fluid outlet vicinity portion 11a. You may make it make the 1st flow path 11 merge so that it may become fewer than the number of flow paths in the upstream part. For example, as shown in FIG. 11, two first flow paths 11 adjacent to each other in the arrangement direction of the first flow paths 11 are merged at the first fluid outlet vicinity portion 11a to form a single line. The flow path width W11a in the first fluid outlet vicinity part 11a may be formed to be larger than the sum of the flow path widths W11b in the upstream part 11b of the first fluid outlet vicinity part 11a before joining. . Thereby, 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 after the merging is the first fluid before the merging. It can be made larger than the sum total of the channel cross-sectional areas S11b in the portion 11b on the upstream side of the outlet vicinity portion 11a.

(6) Modification 5
In the water heat exchanger 1 according to the above embodiment and the first to fourth modifications, when the first fluid is cooled by the refrigerant as the second fluid, the second channel 21 is located near the outlet of the second fluid. The channel width W21a of the second channel 21 in the two-fluid outlet vicinity portion 21a is formed to be larger than the channel width W21b in the upstream portion 21b 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 passage cross-sectional area S21a in the second fluid outlet vicinity portion 21a is higher than the second fluid outlet vicinity portion 21a. In order to suppress an increase in pressure loss in the second flow path 21 due to an increase in the gas component flowing through the second flow path 21 as the second fluid evaporates. Yes.

  However, when the first fluid is cooled by the refrigerant as the second fluid, the flow passage cross-sectional area S21a in the second fluid outlet vicinity portion 21a is upstream of the second fluid outlet vicinity portion 21a. The configuration for forming the passage portion 21b to be larger than the flow passage 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 part 21a of the second flow path 21 is larger than that in the second fluid outlet vicinity part 21a. You may make it make the 2nd flow path 21 merge so that it may become fewer than the number of flow paths in the upstream part. For example, as shown in FIG. 12, the two second flow paths 21 adjacent in the arrangement direction of the second flow paths 21 are merged at the second fluid outlet vicinity portion 21 a to become one, and thus after the merge The channel width W21a in the second fluid outlet vicinity portion 21a may be formed to be larger than the total of the channel width W21b in the upstream portion 21b of the second fluid outlet vicinity portion 21a before joining. . Thereby, the flow path cross-sectional area S21a in the second fluid outlet vicinity part 21a after the merge is made larger than the total of the flow path cross-sectional areas S21b in the portion 21b upstream of the second fluid outlet vicinity part 21a before the merge. be able to.

  Also, the second flow path 21 shown in FIG. 12 is merged at the second fluid outlet vicinity portion 21a to reverse the configuration in which the flow path cross-sectional area S21a is larger than the total of the flow path cross-sectional areas S21b. 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 upstream of the second fluid outlet vicinity portion 21a, the total of the channel cross-sectional areas S21a is calculated. You may make it larger than the sum total of S21b. For example, in the configuration in which the second flow path 21 as in Modification 3 is divided into a plurality of flow path groups 21A, 21B, and 21C and these flow path groups 21A, 21B, and 21C are connected in series, FIG. As shown, the flow path group 21A located near the outlet of the second fluid is the second fluid outlet vicinity part 21a, and the flow path groups 21B and 21C are the upstream part 21b of the second fluid outlet vicinity part 21a. The number N21a of the second flow paths 21 constituting the flow path group 21A may be made larger than the number N21b of the flow paths 21B and 21C. Here, the channel widths W21a, W21b (channel cross-sectional areas S21a, S21b) of the second channels 21 are the same, and the channel cross-sectional area S21a in the channel group 21A can be changed by changing the number of channels. The total of the channel cross-sectional areas S21b in the channel groups 21B and 21C is changed. As described above, in the configuration in which the number of channels N21a in the second fluid outlet vicinity portion 21a is increased to the number of channels N21a in the upstream portion 21b, the pressure loss of the second channel 21 in the water heat exchanger 1 increases. In addition to reducing the number of flow paths in the vicinity of the inlet of the second fluid, the distribution performance of the second fluid in the second flow path 21 can be kept good. In particular, not only the number of channels N21a in the channel group 21A is larger than the number of channels N21b in the upstream channel groups 21B, 21C, but also in the order of the channel groups 21A, 21B, 21C, that is, If the number of flow paths is reduced as approaching the vicinity of the inlet of the two fluids, it effectively contributes to the distribution performance of the second fluid in the second flow paths 21.

  The present invention includes a first layer in which a plurality of first flow paths through which water as a first fluid flows, a second layer in which a plurality of second flow paths through which a refrigerant as a second fluid flows, Are laminated, and can be widely applied to a water heat exchanger that performs heat exchange between the first fluid and the second fluid.

DESCRIPTION OF SYMBOLS 1 Water heat exchanger 10 1st layer 11 1st flow path 11a 1st fluid exit vicinity part 11b The part upstream from the 1st fluid exit vicinity part 20 2nd layer 21 2nd flow path 21a 2nd fluid exit vicinity part 21b A portion upstream from the vicinity of the second fluid outlet

JP 2010-117102 A

Claims (6)

A first layer (10) in which a plurality of first flow paths (11) through which water as a first fluid flows is formed, and a plurality of second flow paths (21) through which a refrigerant as a second fluid flows are formed. In the water heat exchanger that is configured by stacking the second layer (20), and performs heat exchange between the first fluid and the second fluid,
When the first flow path is viewed in the first layer along the stacking direction of the first and second layers, the first flow path is formed along the direction intersecting the arrangement direction of the first flow paths. Extending from one end to the other,
When the second flow path is viewed from the second layer along the stacking direction, from one end of the second layer to the other end along the direction intersecting the arrangement direction of the second flow paths. Extended,
When the first fluid is heated by the second fluid, the flow path cross-sectional area in the first fluid outlet vicinity portion (11a) where the first flow path is positioned in the vicinity of the outlet of the first fluid is the first flow path. Formed so as to be larger than the cross-sectional area of the flow path in the portion (11b) on the upstream side of the vicinity of the fluid outlet,
Water heat exchanger (1). The first flow paths merge so that the number of flow paths in the vicinity of the first fluid outlet is smaller than the number of flow paths in the portion on the upstream side of the first fluid outlet vicinity.
The water heat exchanger according to claim 1. A first layer (10) in which a plurality of first flow paths (11) through which water as a first fluid flows is formed, and a plurality of second flow paths (21) through which a refrigerant as a second fluid flows are formed. In the water heat exchanger that is configured by stacking the second layer (20), and performs heat exchange between the first fluid and the second fluid,
When the first flow path is viewed in the first layer along the stacking direction of the first and second layers, the first flow path is formed along the direction intersecting the arrangement direction of the first flow paths. Extending from one end to the other,
When the second flow path is viewed from the second layer along the stacking direction, from one end of the second layer to the other end along the direction intersecting the arrangement direction of the second flow paths. Extended,
In the case where the first fluid is cooled by the second fluid, the flow path cross-sectional area in the second fluid outlet vicinity part (21a) where the second flow path is located in the vicinity of the outlet of the second fluid is the second It is formed so as to be larger than the cross-sectional area of the flow path in the portion (21b) upstream from the vicinity of the fluid outlet.
Water heat exchanger (1). The second flow path is merged 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 upstream of the second fluid outlet vicinity.
The water heat exchanger according to claim 3. The second flow path is branched such that the number of flow paths in the vicinity of the second fluid outlet is larger than the number of flow paths in the portion upstream of the second fluid outlet vicinity.
The water heat exchanger according to claim 3. In the case where the first fluid is cooled by the second fluid, the flow path cross-sectional area in the second fluid outlet vicinity part (21a) where the second flow path is located in the vicinity of the outlet of the second fluid is the second It is formed so as to be larger than the cross-sectional area of the flow path in the portion (21b) upstream from the vicinity of the fluid outlet.
The water heat exchanger according to claim 1 or 2.

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