JP6432613B2 - Water heat exchanger - Google Patents

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, considering the increase in pressure loss, clogging of the flow path, etc., there is a limit to reducing the cross-sectional area of the first flow path and the second flow path. Therefore, it is necessary to devise the shape of the flow path.

  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 exchanges heat between the first fluid and the second fluid, the high-performance and compact design is achieved by devising the shape of the flow path. is there.

The water heat exchanger according to the first and second aspects includes a first layer in which a plurality of first flow paths through which water as a first fluid flows and a second flow path through which refrigerant as a second fluid flows. And the second layer formed in a plurality of rows are stacked, and performs 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. And here, the first flow path has a meandering shape when the first layer is viewed along the stacking direction, and / or the second flow path is first along the stacking direction. When the two layers are viewed, it has a meandering shape.

  Here, as described above, the first flow path and the second flow path have a meandering shape when the first layer and the second layer are viewed along the stacking direction. Compared with the case where the second flow path has a straight shape, the flow path length per unit volume of the water heat exchanger can be increased. And since the heat-transfer promotion effect can be acquired by the meandering shape of such a 1st flow path and a 2nd flow path, compared with the case where the 1st flow path and the 2nd flow path have a straight shape. Thus, the heat transfer coefficient in the first flow path and the second flow path can be improved. As described above, the performance and compactness of the water heat exchanger can be achieved here.

In the water heat exchanger according to the first aspect, when the first fluid is heated by the second fluid, the first flow path is a flow in the vicinity of the first fluid outlet located near the outlet of the first fluid. The first fluids that are adjacent to each other in the arrangement direction of the first fluid channels join together so that the number of channels is less than the number of fluid channels in the upstream portion of the vicinity of the first fluid outlet. The total of the cross-sectional area of the first flow path in the vicinity of the outlet is formed to be larger than the total of the cross-sectional area of the flow path in the portion on the upstream side of the vicinity of the first fluid outlet.

  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.

In the water heat exchanger according to the second aspect, when the first fluid is cooled by the second fluid, the second flow path is a flow in the vicinity of the second fluid outlet located near the outlet of the second fluid. When the second flow paths adjacent in the arrangement direction of the second flow paths merge so that the number of paths is smaller than the number of flow paths in the upstream portion of the vicinity of the second fluid outlet, the second fluid The total of the cross-sectional area of the second flow path in the vicinity of the outlet is formed to be larger than the total of the cross-sectional area of the flow path in the portion upstream 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 channel length per unit volume of the water heat exchanger can be increased, and the heat transfer coefficient in the first channel and the second channel is improved. Therefore, high performance and compactness of the water heat exchanger can be achieved.

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 (corresponding to Drawing 2) showing the 1st 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 2 of the present invention. It is a figure which shows the external appearance of the water heat exchanger concerning the modification 3 of this 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 4 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 4 of the present invention. It is a figure (corresponding to Drawing 2) showing the 1st channel of the water heat exchanger concerning modification 5 of the present invention. It is a figure (corresponding to Drawing 2) showing the 1st 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 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 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, 3 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 in FIG. ing. Thus, the 1st flow path 11 and the 2nd flow path 20 are arrange | positioned so that a cross flow may be made here.

  Here, the first flow path 11 has a meandering shape when the first layer 10 is viewed along the stacking direction. Specifically, the first flow path 11 is meandering linearly (that is, squared) in the arrangement direction of the first flow paths 11 (here, the left and right direction in FIG. 2). It extends in a direction (here, the vertical direction) intersecting the arrangement direction. It is preferable that the first flow path 11 meanders three or more times from one end of the first layer 10 to the other end. In addition, the second flow path 21 has a meandering shape when the second layer 20 is viewed along the stacking direction. Specifically, the second flow path 21 is meandering linearly (that is, squarely) in the arrangement direction of the second flow paths 21 (here, the vertical direction in FIG. 3), while the second flow path 21 It extends in a direction intersecting the arrangement direction (here, the horizontal direction). It is preferable that the second flow path 21 meanders three or more times from one end of the second layer 20 to the other end.

  In addition, here, the heat exchanging unit 3 having the laminated structure of the first layer 10 and the second layer 20 includes the first plate member 12 in which the groove forming the first flow path 11 is formed on one side, and the second 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.

  In such a water heat exchanger 1, as described above, the first flow path 11 and the second flow path 21 have a meandering shape when the first layer 10 and the second layer 20 are viewed along the stacking direction. Therefore, compared with the case where the 1st flow path 11 and the 2nd flow path 21 have a straight shape, the flow path length per unit volume of the water heat exchanger 1 can be enlarged. In addition, since the heat transfer promoting effect can be obtained by the meandering shape of the first flow path 11 and the second flow path 21, the first flow path 11 and the second flow path 21 have a straight shape. Compared with the case where it exists, the heat transfer rate in the 1st flow path 11 and the 2nd flow path 21 can be improved. Thus, the high performance and compactness of the water heat exchanger 1 can be achieved here.

(2) Modification 1
In the water heat exchanger 1 of the above embodiment, as shown in FIGS. 2 and 3, the first and second flow paths 11 and 21 have a shape meandering linearly (that is, angularly). However, the present invention is not limited to this.

  For example, as shown in FIGS. 5 and 6, the first and second flow paths 11 and 21 may have a meandering shape in a curved manner (that is, rounded without being angular).

  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, both the first and second flow paths 11 and 21 have a meandering shape, but only the first flow path 11 or the second flow path 21 is provided. May have a meandering shape.

  For example, the second flow path 21 may have a meandering shape as shown in FIGS. 3 and 6, and the first flow path 11 may have a straight shape as shown in FIG. On the contrary, the first flow path 11 has a meandering shape as shown in FIGS. 2 and 5, and the second flow path 21 has a straight shape as shown in FIG. Also good.

  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 according to the embodiment and the first and second modifications, 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. 9 and 10, as shown in FIGS. 9 and 10, from one end of the second layer 20 (the lower end of the second layer 20 in FIG. 10) to the other end (the upper end of the second layer 20 in FIG. 10) 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 the present modification, it is possible to obtain the same functions and effects as in the above embodiment and Modifications 1 and 2.

(5) Modification 4
In the water heat exchanger 1 according to the embodiment and the first and second modifications, 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. 11, 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. 11). 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 the configuration shown in FIG. 11, 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. However, the present invention is not limited to this. For example, as shown in FIG. 12, connection channels 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 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. 11, and the second header 9 can have only a space corresponding to the space 9a in FIG.

  Also in the configuration of the present modification, it is possible to obtain the same functions and effects as in the above embodiment and Modifications 1 and 2.

(6) Modification 5
In the water heat exchanger 1 according to the embodiment and the first to fourth modifications, when water as the first fluid is heated by the second fluid, a scale is deposited in the first channel 11, and the first channel 11 There is a risk of clogging.

  Therefore, here, in order to suppress clogging of the portion near the outlet of the first flow path 11 due to such scale deposition, for example, as shown in FIG. The flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a located in the first fluid outlet is formed so as to be larger than the flow passage cross-sectional area S11b in the portion 11b upstream of the first fluid outlet vicinity portion 11a. Here, 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 upstream of the first fluid outlet vicinity portion 11a. Therefore, 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, unlike the configuration of the first flow path 11 shown in FIG. 13, the number of flow paths in the first fluid outlet vicinity portion 11a is larger than the number of flow paths in the portion upstream of the first fluid outlet vicinity portion 11a. Alternatively, the first flow paths 11 may be merged so as to reduce the number. For example, as shown in FIG. 14, 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 one, and then after the merge. 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, the flow path cross-sectional area S11a in the first fluid outlet vicinity part 11a after the merge is made larger than the sum of the flow path cross-sectional areas S11b in the portion 11b upstream of the first fluid outlet vicinity part 11a before the merge. be able to.

  In such a water heat exchanger 1, as described above, the flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a of the first flow passage 11 is larger than the upstream portion 11b. 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 11 to the first fluid outlet vicinity portion 11a, the scale that deposits when the first fluid is heated is in the vicinity of the first fluid outlet. It is possible to prevent clogging of the portion 11a. As described above, the first flow in the water heat exchanger 1 can be obtained not only in this embodiment and the same effects as those of the first to fourth modifications but also with a minimum decrease in the heat transfer coefficient. Clogging of the path 11 can be suppressed.

(7) Modification 6
In the water heat exchanger 1 according to the embodiment and the first to fifth modifications, when the first fluid is cooled by the refrigerant as the second fluid, the gas component flowing through the second flow path 21 as the second fluid evaporates. May increase, and the pressure loss of the second flow path 21 may increase.

  Therefore, here, in order to suppress the increase in the pressure loss of the second flow path 21 due to the evaporation of the second fluid, for example, as shown in FIG. The flow passage cross-sectional area S21a in the second fluid outlet vicinity portion 21a located in the vicinity is formed to be larger than the flow passage cross-sectional area S21b in the portion 21b upstream of the second fluid outlet vicinity portion 21a. Here, the channel width W21a of the second channel 21 in the second fluid outlet vicinity portion 21a is formed to be larger than the channel width W21b in the portion 21b upstream of the second fluid outlet vicinity portion 21a. Therefore, 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). Moreover, you may arrange | position so that the 1st flow path 11 and the 2nd flow path 21 may make orthogonal opposed flow (or orthogonal parallel flow).

  Also in the configuration in which the second flow path 21 as in the above-described modification 4 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. Similarly to the configuration shown in FIG. 15, a configuration in which the flow path width W21a of the second flow path 21 in the second fluid outlet vicinity 21a can be increased. In this case, for example, as shown in FIG. 16, the channel group 21A located in the vicinity of the second fluid outlet is a second fluid outlet vicinity part 21a, and the channel groups 21B and 21C are the second fluid outlet vicinity part. As the portion 21b on the upstream side of 21a, the channel width W21a of the second channel 21 constituting the channel group 21A constituting the channel group 21A is set to the second channel 21 constituting the channel groups 21B and 21C. What is necessary is just to form so that it may become larger than flow-path width W21b.

  Further, unlike the configuration of the second flow path 21 shown in FIG. 15, the number of flow paths in the second fluid outlet vicinity portion 21a is larger than the number of flow paths in the portion upstream of the second fluid outlet vicinity portion 21a. Alternatively, the second flow path 21 may be merged so as to reduce the number. For example, as shown in FIG. 17, 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 21a so as to become one. 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.

  In contrast to the configuration in which the second channel 21 shown in FIG. 17 is merged at the second fluid outlet vicinity portion 21a to make the channel sectional area S21a larger than the total of the channel 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 4 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.

  In such a water heat exchanger 1, as described above, because the second channel 21 has a larger channel cross-sectional area S21a in the second fluid outlet vicinity portion 21a than the upstream portion 21b, The second fluid containing a large amount of gas components that increase with evaporation while limiting the decrease in the heat transfer coefficient due to the decrease in the flow rate of the second fluid in the second flow path 21 to only the second fluid outlet vicinity 21a. It can flow smoothly through the outlet vicinity 21a. As described above, the second flow in the water heat exchanger 1 can be obtained not only in this embodiment and the same effects as those of the first to fifth modifications but also with a minimum decrease in the heat transfer coefficient. An increase in pressure loss in the passage 21 can be suppressed.

  Further, as in the configuration shown in FIG. 18, in the configuration in which the number of flow paths N21a in the second fluid outlet vicinity portion 21a is increased to the number of flow paths N21a in the upstream portion 21b, the second number in the water heat exchanger 1 is increased. In addition to suppressing an increase in pressure loss in the flow path 21, 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, in the configuration shown in FIG. 18, 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 and 21C, but also the channel groups 21A, 21B, Since the number of flow paths is reduced in the order of 21C, that is, near the vicinity of the inlet of the second fluid, it effectively contributes to the distribution performance of the second fluid in the second flow path 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 (2)

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,
The first flow path, when viewed the first layer along the stacking direction, have a meandering shape,
And / or
Said second flow path, when viewed the second layer along the stacking direction, have a meandering shape,
In the case where the first fluid is heated by the second fluid, the number of channels in the first fluid outlet vicinity (11a) where the first channel is positioned in the vicinity of the outlet of the first fluid is the first fluid. The first fluids adjacent to each other in the arrangement direction of the first fluid channels are joined together so that the number of fluid channels in the portion (11b) on the upstream side from the vicinity of the outlet is reduced. The total of the cross-sectional area of the first flow path in the vicinity of the outlet is formed to be larger than the total of the cross-sectional area of the flow path in the portion on the upstream side of the vicinity of the first fluid outlet.
Water heat exchanger (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,
The first flow path, when viewed the first layer along the stacking direction, have a meandering shape,
And / or
Said second flow path, when viewed the second layer along the stacking direction, have a meandering shape,
In the case where the first fluid is cooled by the second fluid , the number of channels in the second fluid outlet vicinity (21a) where the second channel is positioned in the vicinity of the outlet of the second fluid is the second fluid. The second fluids adjacent to each other in the arrangement direction of the second flow channels are joined together so that the number of flow channels in the portion (21b) on the upstream side of the vicinity of the outlet is reduced. The total of the cross-sectional area of the second flow path in the vicinity of the outlet is formed to be larger than the total of the cross-sectional area of the flow path in the portion on the upstream side of the vicinity of the second fluid outlet.
Water heat exchanger (1).

Images