JP2014006003A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a heat exchange which is not enlarged, a heat exchanger in which a device performance is not reduced, and a heat exchange in which a pressure resistant strength is not reduced.SOLUTION: The heat exchanger comprises at least a heat conduction member in which at least one first fluid flow passage in which a first fluid flows, at least one second fluid flow passage row where a plurality of second fluid flow passages in which a second fluid exchanging heat with the first fluid flows are provided in a row shape, and at least one third fluid flow passage in which the second fluid flows are formed at least. The second fluid flow passage and the third fluid flow passage are provided in such a manner that the closer to the first fluid flow passage the fluid flow passage becomes, the smaller a sectional area becomes, that the closer to the first fluid flow passage the fluid flow passage becomes, the wider an interval with the closest fluid flow passage belonging to the same row of fluid flow passages provided in the row shape becomes, or that the closer to the first fluid flow passage the fluid flow passage becomes, the smaller the sectional area becomes and the wider the interval with the closest fluid flow passage belonging to the same row of fluid flow passages provided in the row shape becomes.

Description

  The present invention relates to a heat exchanger that performs heat exchange between a first fluid and a second fluid.

  As a conventional air conditioner, there is an air conditioner that heats a refrigerant with high-temperature gas. In such an air conditioner, the fuel supplied from the fuel supply device is burned by a burner to generate hot exhaust gas in the combustion chamber, and the fins are heated by the exhaust gas. The heat of the fins is transferred to the partition member, and the heat transfer member in contact with the partition member is heated. A plurality of fluid flow paths are formed in a row in the heat transfer member, and the liquid refrigerant flowing through the fluid flow paths is heated. The heated liquid refrigerant is vaporized and evaporated to a gas-liquid two-phase state in which bubbles are generated in the liquid. Since the gas-liquid two-phase refrigerant is hot, it flows into the outlet header pipe by natural circulation force, and flows into the radiator via the refrigerant outlet pipe connected to the outlet header pipe (see, for example, Patent Document 1). .)

Japanese Patent No. 2600930 (column 4, line 49-column 6, line 10, Fig. 1-4)

  When the refrigerant flow rate is increased with an increase in the capacity of the device, it is necessary to increase the cross-sectional area of each fluid flow path in order to prevent an increase in pressure loss. However, when the dimension of each fluid flow path is enlarged in a direction parallel to the row direction of the fluid flow paths, there is a problem that the heat transfer member becomes large. Further, when the dimension of each fluid flow path is enlarged in the direction perpendicular to the column direction of the fluid flow path, the distance between the surface of the fluid flow path farther from the partition wall member and the partition wall member becomes longer, and the refrigerant flows in the vicinity of the surface. However, since it is impossible to receive heat, there is a problem that the performance of the device is deteriorated. Further, when the cross-sectional area of each fluid flow path is increased, there is a problem in that the pressure resistance strength of the heat transfer member decreases.

  The present invention has been made to solve the above-described problems, and provides a heat exchanger that is not increased in size even when the refrigerant flow rate is increased. Moreover, the heat exchanger which does not cause the performance fall of an apparatus even when increasing a refrigerant | coolant flow volume is obtained. Moreover, even when the refrigerant flow rate is increased, a heat exchanger in which the pressure resistance does not decrease is obtained.

  In the heat exchanger according to the present invention, at least one first fluid channel through which a first fluid flows and a plurality of second fluid channels through which a second fluid that exchanges heat with the first fluid flows are arranged in a line. At least one second fluid flow path row provided in the at least one heat transfer member formed by at least one third fluid flow path through which the second fluid flows. A channel, the second fluid channel array, and the third fluid channel are provided in the order of the first fluid channel, the second fluid channel column, and the third fluid channel, and the second fluid channel And the third fluid channel forms at least two fluid channel rows, and is provided in a row of the first fluid channel, the second fluid channel, and the third fluid channel. The rows of fluid flow paths are provided so as not to cross each other, and the second fluid flow path rows are arranged at the center of the cross section of the first fluid flow path. The cross section of the second fluid channel and the third fluid channel are smaller as the second fluid channel and the third fluid channel are closer to the first fluid channel. Or the closer to the first fluid flow path, the wider the distance from the nearest fluid flow path belonging to the same row of the fluid flow paths provided in a row, or the first fluid flow path. The one closer to one fluid flow path is provided such that the cross-sectional area is smaller and the distance from the closest fluid flow path belonging to the same row of the fluid flow paths provided in a row is increased.

  The present invention provides a plurality of fluid flow paths through which the second fluid flows at different distances relative to the fluid flow path through which the first fluid flows, so that it is not necessary to arrange the fluid flow paths in a wide area, and the refrigerant flow rate Even when increasing the heat transfer member, the heat transfer member can be downsized. In addition, by dividing the fluid flow into a number of fluid flow paths and flowing the second fluid, the surface area of the fluid flow path through which the second fluid flows and the surface area where the second fluid comes into contact is increased, and the heat reception of the refrigerant is promoted. Even when the refrigerant flow rate is increased, it is possible to suppress degradation in the performance of the device. In addition, by dividing the fluid flow into many fluid flow paths and flowing the second fluid, the cross-sectional area of each fluid flow path is reduced, and the pressure resistance strength of the heat transfer member does not decrease even when the refrigerant flow rate is increased.

It is a perspective view of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows the example which applied the heat exchanger which concerns on Embodiment 1 of this invention to the heat pump type heating system. It is a figure which shows the example which applied the heat exchanger which concerns on Embodiment 1 of this invention to the heat pump type hot-water supply system. It is a perspective view of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 2 of this invention.

Hereinafter, the heat exchanger according to the present invention will be described with reference to the drawings.
In the following, a heat exchanger for a heating system or a hot water supply system will be described as an example, but it goes without saying that the present invention can also be applied to a heat exchanger used for other purposes. Moreover, in each figure, the same code | symbol is attached | subjected to the same member or the same part. Moreover, illustration is abbreviate | omitted suitably about the fine structure. In addition, overlapping descriptions are simplified or omitted as appropriate.

Embodiment 1 FIG.
1 shows a perspective view of a heat exchanger according to Embodiment 1. FIG.
The heat exchanger 1 includes at least a heat transfer member 2. The heat transfer member 2 is manufactured, for example, by integral extrusion molding of an aluminum material. The heat transfer member 2 includes a first fluid channel row 4 in which a plurality of first fluid channels 3 through which the first fluid flows are provided in one row, and a second fluid that exchanges heat with the first fluid. A plurality of second fluid flow paths 5 in which at least one second fluid flow path 5 is provided in at least one row, and a plurality of third fluid flow paths 7 in which a second fluid that exchanges heat with the first fluid flows are 1 The third fluid flow path row 8 provided in the row is formed. The first fluid channel row 4, the second fluid channel row 6, and the third fluid channel row 8 may not be parallel or parallel. The second fluid flow path row 6 may be one row or a plurality of rows. In the case of a plurality of rows, the second fluid flow passage rows 6 may not be parallel to or parallel to each other. However, it is not limited to three rows.) Further, the second fluid flow path 5 and the third fluid flow path 7 form a row in a direction substantially orthogonal to the column (in FIG. 1, the case where there are 10 rows is described, but the number is limited to 10 rows). Not.) In addition, the second fluid channel 5 and the third fluid channel 7 may be the same or different in the number provided for each row. The first fluid channel row 4, the second fluid channel row 6, and the third fluid channel row 8 do not cross each other, and the first fluid channel row 4, the second fluid channel row 6, The three fluid flow path rows 8 are arranged in this order. Each row may be parallel or non-parallel. Also, the rows do not cross each other.

  The first fluid and the second fluid are refrigerants such as R410, R32 and water, for example. When water is used as the first fluid or the second fluid, and the heat transfer member 2 is made of a material that is easily corroded by water such as aluminum, the first fluid channel 3, the second fluid channel 5, and the third fluid are used. A copper pipe or the like that is less likely to be corroded by water than aluminum is provided inside the flow path 7 so as to be expanded, and the first fluid and the second fluid may flow through the copper pipe.

Each of the first fluid channel 3, the second fluid channel 5, and the third fluid channel 7 is provided through the heat transfer member 2 so as not to cross each other in the longitudinal direction of the heat transfer member 2. Here, the cross-sectional shape of the first fluid flow path 3 is assumed to be a circle, and the cross-sectional shapes of the second fluid flow path 5 and the third fluid flow path 7 are assumed to be rectangular. However, other shapes may be used. In addition, when the cross-sectional shape of the 1st fluid flow path 3, the 2nd fluid flow path 5, or the 3rd fluid flow path 7 is made into a circle or a square, the manufacturing precision at the time of integrally extruding the heat-transfer member 2 etc. Can be improved. Moreover, the cross-sectional shapes of the first fluid channel 3, the second fluid channel 5, and the third fluid channel 7 may be the same or different. Further, the cross-sectional shape may be different within the column or row, and the cross-sectional shape may be different for each column or row. Further, the cross-sectional shape may be the same and the cross-sectional areas may be different from each other within the column, the row, or the column or the row, or the cross-sectional shapes may be different from each other. Further, the first fluid channel 3, the second fluid channel 5, and the third fluid channel 7 may or may not be provided with the center of the fluid channel being linear.
In addition, the horizontal hole 9 may be provided in the both ends of the heat-transfer member 2. FIG. The lateral hole 9 communicates with the second fluid channel 5 and the third fluid channel 7 and is provided perpendicular to the second fluid channel 5 and the third fluid channel 7. A tube for connecting to the piping of the system may be attached by brazing to the side hole 9 portion.

  The second fluid channel 5 and the third fluid channel 7 are set to have a cross-sectional area and an interval according to the distance from the nearest first fluid channel 3. As shown in FIG. 1, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the closest first fluid channel 3 increases. Further, the second fluid channel 5 and the third fluid channel 7 are arranged such that the distance from the nearest fluid channel belonging to the same row becomes narrower as the distance from the nearest first fluid channel 3 increases. Is provided. The second fluid channel 5 and the third fluid channel 7 preferably have a smaller cross-sectional area than the first fluid channel 3 in terms of heat exchange.

Thus, the following effects are acquired by comprising the heat exchanger 1. FIG.
When a plurality of fluid flow paths through which the second fluid flows are provided at different distances with respect to the fluid flow path through which the first fluid flows, it is not necessary to arrange the fluid flow paths in a wide area and the refrigerant flow rate is increased. However, the heat transfer member can be reduced in size. In addition, by dividing the fluid flow into a number of fluid flow paths and flowing the second fluid, the surface area of the fluid flow path through which the second fluid flows and the surface area where the second fluid comes into contact is increased, and the heat reception of the refrigerant is promoted. Even when the refrigerant flow rate is increased, it is possible to suppress degradation in the performance of the device. In addition, by dividing the fluid flow into many fluid flow paths and flowing the second fluid, the cross-sectional area of each fluid flow path is reduced, and the pressure resistance strength of the heat transfer member does not decrease even when the refrigerant flow rate is increased.

In addition, the fluid flow path through which the second fluid provided far from the fluid flow path through which the first fluid flows has a lower heat exchange amount than the fluid flow path through which the second fluid provided nearby. However, in the heat exchanger 1, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the nearest first fluid channel 3 increases. By doing so, the surface area of the fluid flow path through which the second fluid provided in the distance flows and the surface of the second fluid in contact with the surface of the fluid flow path can be increased. A decrease in the amount of heat exchange can be suppressed.
Further, as the distance from the nearest first fluid passage 3 between the second fluid passage 5 and the third fluid passage 7 increases, the distance between the nearest fluid passage belonging to the same row becomes narrower. It is possible to secure a heat transfer path between the fluid flow path through which the first fluid flows and the fluid flow path through which the second fluid provided far away, and the second provided far away. It is possible to suppress a decrease in the heat exchange amount of the fluid flow path through which the fluid flows.

In general, for fins, fin efficiency η (fin surface area S is defined as fin height d, fin width t, fin thermal conductivity λ, and heat transfer coefficient of fluid in contact with the fin α. Although the thermal resistance R (R = 1 / αS) can be reduced by increasing the temperature, a temperature distribution is actually generated on the fin, so that the thermal resistance R does not decrease as the surface area S increases. Is η = tanh (Ub) / Ub and Ub = d (2α / λt) ^0.5 .
When this relationship is applied to the heat exchanger 1, the fin width t corresponds to the interval between rows formed by the second fluid channel 5 and the third fluid channel 7, that is, the width of the heat transfer path between the rows. The fin height d corresponds to the length of the heat transfer path between the rows in the row direction, and the fin efficiency η corresponds to the efficiency of heat exchange.
That is, as shown in the above relational expression, as the width of the heat transfer path between rows becomes wider, the efficiency of heat exchange improves. Therefore, like the heat exchanger 1, the heat transfer path between rows, in particular, the first fluid flow. By increasing the width of the heat transfer path on the side close to the path 3, it is possible to improve the efficiency of heat exchange.
Further, as shown in the above relational expression, the heat exchange efficiency decreases as the length of the heat transfer path between the rows increases, but the second fluid flow path 5 as in the heat exchanger 1 decreases. When the length of each of the third fluid flow paths 7 in the row direction is increased, that is, when the cross-sectional area of each of the second fluid flow path 5 and the third fluid flow path 7 is increased, the transmission between the rows is increased. The surface area S of the heat path can be increased, and the thermal resistance R can be reduced to compensate for the decrease in heat exchange efficiency associated with the increase in the length of the heat transfer path between the lines in the row direction. It becomes.

  In FIG. 1, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the nearest first fluid channel 3 increases. The two-fluid channel 5 and the third fluid channel 7 are provided so that the distance from the nearest fluid channel belonging to the same row becomes narrower as the distance from the nearest first fluid channel 3 increases. Both are implemented, but either one may be selected according to the refrigerant flow rate. When both are implemented, it is possible to further suppress a decrease in the heat exchange amount of the fluid flow path through which the second fluid provided far away flows.

FIG. 2 is a perspective view showing a modification of the heat exchanger according to the first embodiment.
As shown in FIG. 2, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the nearest first fluid channel 3 increases. The fluid channel 5 and the third fluid channel 7 are provided such that the distance from the nearest fluid channel belonging to the same row becomes narrower as the distance from the nearest first fluid channel 3 increases. Further, the distance between the second fluid channel 5 and the nearest fluid channel provided on the third fluid channel 7 side becomes wider as the distance from the nearest first fluid channel 3 increases. Provided.

  Thus, the distance between the second fluid flow path 5 and the closest fluid flow path provided on the third fluid flow path 7 side increases as the distance from the closest first fluid flow path 3 increases. By providing as described above, it is possible to secure a heat transfer path to the surface on the fluid flow path side through which the first fluid flows in the fluid flow path through which the second fluid is provided far away. A decrease in the amount of heat exchange in the fluid flow path through which the second fluid flows can be suppressed.

  In FIG. 2, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the nearest first fluid channel 3 increases. The two-fluid channel 5 and the third fluid channel 7 are provided so that the distance from the nearest fluid channel belonging to the same row becomes narrower as the distance from the nearest first fluid channel 3 increases. The distance between the second fluid channel 5 and the nearest fluid channel provided on the third fluid channel 7 side increases as the distance from the nearest first fluid channel 3 increases. However, any one of them may be selected according to the refrigerant flow rate. When all are implemented, it is possible to further suppress a decrease in the heat exchange amount of the fluid flow path through which the second fluid provided far away flows.

FIG. 3 is a perspective view showing a modification of the heat exchanger according to the first embodiment.
For example, as shown in FIG. 3, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the nearest first fluid channel 3 increases. As the distance from the nearest first fluid channel 3 increases, the distance between the second fluid channel 5 and the nearest fluid channel provided on the third fluid channel 7 side increases. Even when only the provision is made, it is possible to suppress a decrease in the heat exchange amount of the fluid flow path through which the second fluid provided far away flows.

4 to 6 are perspective views showing modifications of the heat exchanger according to the first embodiment.
As shown in FIG. 4, the number of the third fluid flow paths 7 may be one. Further, as shown in FIG. 5, a plurality of sets of the first fluid channel row 4, the second fluid channel row 6 and the third fluid channel row 8 may be provided (in FIG. 5, the number of stages is 2). Although one case is described, it is not limited to two.) In addition, as shown in FIG. 6, the first fluid flow path row 4 may be one row or a plurality of rows, and the second fluid flow passage row 6 and the third fluid flow passage row 8 are the first fluid flow passage row 4. May be provided only on one side or on both sides (in FIG. 6, the first fluid flow path row 4 has two rows, but may be one row or three or more rows). Further, the number of the first fluid flow paths 3 may be plural or one (FIGS. 1 to 6 show the case where there are five first fluid flow paths 3, but the number is not limited to five. ).

Next, an application example of the heat exchanger according to Embodiment 1 will be described.
FIG. 7 is a diagram illustrating an example in which the heat exchanger according to Embodiment 1 is applied to a heat pump heating system.
The heat pump heating system 10 includes a first fluid circuit 11 through which a first fluid flows, a second fluid circuit 12 through which a second fluid flows, and a heat exchanger 1 that performs heat exchange between the first fluid and the second fluid. Have In this example, R410A is used as the first fluid, and water is used as the second fluid. The first fluid circuit 11 includes a compressor 13, an expansion valve 14, an outdoor heat exchanger 15, and a fan 16. The second fluid circuit 12 includes a pump 17 and a use side heat exchanger 18. In addition, the kind of fluid is not limited to this, and as the first fluid, for example, a natural refrigerant such as a chlorofluorocarbon refrigerant, a hydrocarbon, or a mixture thereof may be used. Moreover, you may use water, such as a tap water, distilled water, and a brine, as a 2nd fluid.

  In the first fluid circuit 11, the first fluid that has become high temperature and pressure in the compressor 13 exchanges heat with the second fluid in the heat exchanger 1. Thereafter, the first fluid, which has been decompressed by the expansion valve 14 to become low temperature and pressure, evaporates by exchanging heat with the air from the fan 16 in the outdoor heat exchanger 15, and then returns to the compressor 13. In the second fluid circuit 12, the second fluid heated by the heat exchanger 1 is sent out from the pump 17 and radiated by the use side heat exchanger 18. As the use-side heat exchanger 18, for example, a radiator, a floor heater, or the like can be used.

FIG. 8 is a diagram illustrating an example in which the heat exchanger according to Embodiment 1 is applied to a heat pump hot water supply system.
In addition to the configuration of the heat pump heating system 10, the heat pump hot water supply system 19 includes a tank 20 in which a use side heat exchanger 18 is provided. Water in the tank 20 is heated by the use side heat exchanger 18 and the water is taken.

  As shown in FIGS. 7 and 8, by applying the heat exchanger according to the first embodiment to a heat pump heating system or a heat pump hot water supply system, the system can be downsized even when the refrigerant flow rate is increased. it can. Further, even when the refrigerant flow rate is increased, it is possible to suppress a decrease in system performance. Further, the durability of the system can be improved even when the refrigerant flow rate is increased. In addition, since such a heat pump type heating system and a heat pump type hot water supply system use the utilization side heat exchanger 18 as a heat source, they are energy saving compared with the heating system and hot water supply system which used the conventional boiler as the heat source.

Embodiment 2. FIG.
FIG. 9 is a perspective view of a heat exchanger according to the second embodiment.
In the heat exchanger according to the second embodiment, the second fluid channel row 6 and the third fluid channel row 8 have an arc shape with respect to one first fluid channel 3 provided in the heat transfer member 2. Provided. In addition, about the structure, an effect, an application example, etc., the description which overlaps with Embodiment 1 is abbreviate | omitted suitably.

  The second fluid channel 5 and the third fluid channel 7 are set to have a cross-sectional area and an interval according to the distance from the first fluid channel 3. As shown in FIG. 9, the second fluid channel 5 and the third fluid channel 7 are provided such that the cross-sectional area increases as the distance from the first fluid channel 3 increases. The second fluid channel 5 and the third fluid channel 7 are provided such that the distance from the nearest fluid channel belonging to the same row becomes narrower as the distance from the first fluid channel 3 increases. It is done. The second fluid channel 5 is provided such that the distance from the nearest fluid channel provided on the third fluid channel 7 side increases as the distance from the first fluid channel 3 increases. .

  In FIG. 9, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the first fluid channel 3 increases, and the second fluid channel The flow path 5 and the third fluid flow path 7 are provided so that the distance from the closest fluid flow path belonging to the same row becomes narrower as the distance from the first fluid flow path 3 increases. All of the two fluid flow paths 5 are provided so that the distance from the closest fluid flow path provided on the third fluid flow path 7 side increases as the distance from the first fluid flow path 3 increases. However, any one may be selected according to the refrigerant flow rate. When all are implemented, it is possible to further suppress a decrease in the heat exchange amount of the fluid flow path through which the second fluid provided far away flows.

FIG. 10 is a perspective view showing a modification of the heat exchanger according to the second embodiment.
For example, as shown in FIG. 10, the second fluid channel 5 and the third fluid channel 7 are provided so that the cross-sectional area increases as the distance from the first fluid channel 3 increases. The second fluid channel 5 is only provided so that the distance from the nearest fluid channel provided on the third fluid channel 7 side becomes wider as the distance from the first fluid channel 3 increases. Even when the above is implemented, it is possible to suppress a decrease in the heat exchange amount of the fluid flow path through which the second fluid provided far away flows.

11 to 15 are perspective views showing modifications of the heat exchanger according to the second embodiment.
As shown in FIG. 11, the number of the third fluid flow paths 7 may be one. In addition, as shown in FIG. 12, the second fluid flow channel row 6 and the third fluid flow channel row 8 surround one region or a plurality of regions of the entire circumference even if they surround substantially the entire circumference of the first fluid flow channel 3. (Although FIG. 12 shows a case where about 150 ° of the entire circumference of the first fluid flow path row 4 is surrounded, it is not limited to about 150 °). Further, as shown in FIG. 13, a plurality of first fluid flow paths 3 may be provided in one row to form a first fluid flow path row 4 (in FIG. 13, the first fluid flow path 3 is 3). Although one case is described, it is not limited to three.) Further, as shown in FIG. 14, a plurality of sets of the first fluid channel row 4, the second fluid channel row 6, and the third fluid channel row 8 may be provided (in FIG. 14, the number of stages is 2). Although one case is described, it is not limited to two.) Further, as shown in FIG. 15, the first fluid flow path row 4 may be one row or a plurality of rows (in FIG. 15, the case where the first fluid flow passage row 4 is two rows is described, Alternatively, the second fluid channel row 6 and the third fluid channel row 8 may be provided only on one side of the first fluid channel row 4 or on both sides.

In the heat exchanger according to the first and second embodiments, a hole is formed in the heat transfer member 2 to form the first fluid channel 3, the second fluid channel 5, and the third fluid channel 7. Other configurations may be used. For example, a tube is provided inside a hollow heat transfer member 2 in which a heat transfer medium such as gas is sealed, and a coolant is allowed to flow from the outside of the heat transfer member 2 to the tube, whereby the first fluid flow path 3 and the second fluid flow The channel 5 and the third fluid channel 7 may be formed.
Moreover, it is also possible to combine each embodiment and each modification.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 Heat-transfer member, 1st fluid flow path, 4th 1st fluid flow path row | line | column, 5 2nd fluid flow path row | line, 6 2nd fluid flow path row | line | column, 7 3rd fluid flow path row | line, 8 3rd Fluid passage array, 9 horizontal hole, 10 heat pump heating system, 11 first fluid circuit, 12 second fluid circuit, 13 compressor, 14 expansion valve, 15 outdoor heat exchanger, 16 fan, 17 pump, 18 user side heat Exchanger, 19 heat pump hot water supply system, 20 tanks.

Claims (8)

At least one second fluid channel in which at least one first fluid channel through which the first fluid flows and a plurality of second fluid channels through which the second fluid that exchanges heat with the first fluid flows are arranged in a row. At least a heat transfer member formed with at least one fluid flow path row and at least one third fluid flow path through which the second fluid flows;
The first fluid channel, the second fluid channel array, and the third fluid channel are provided in the order of the first fluid channel, the second fluid channel column, and the third fluid channel,
The second fluid channel and the third fluid channel form at least two fluid channel rows,
A row of fluid flow paths provided in a row among the first fluid flow path, the second fluid flow path, and the third fluid flow path is provided so as not to cross each other.
The second fluid flow channel row is provided so as to intersect a straight line connecting the cross-sectional center of the first fluid flow channel and the cross-sectional center of the third fluid flow channel,
The second fluid channel and the third fluid channel are arranged in a row so that the closer to the first fluid channel, the smaller the cross-sectional area, or the closer to the first fluid channel. The cross-sectional area is reduced and provided in a row so that the interval between the provided fluid channels and the closest fluid channel belonging to the same row in the same row becomes wider or closer to the first fluid channel. Provided so that the distance between the closest fluid flow path belonging to the same row of fluid flow paths is wide,
A heat exchanger characterized by that. The second fluid channel and the third fluid channel are narrower as the distance from the closest fluid channel provided on the side far from the first fluid channel is closer to the first fluid channel. Provided as
The heat exchanger according to claim 1. The fluid channels provided in a row of the second fluid channel and the third fluid channel have the same fluid channel belonging to the same column with respect to the nearest first fluid channel. Provided to be a distance,
The heat exchanger according to claim 1 or 2, characterized in that. The plurality of first fluid flow paths are provided in a row to form at least one first fluid flow path row.
The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is provided. The second fluid channel row and the third fluid channel are provided on one side of the first fluid channel row,
The heat exchanger according to claim 4. The second fluid channel row and the third fluid channel are provided on both sides of the first fluid channel row,
The heat exchanger according to claim 4. The first fluid flow path is one.
The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is provided. The third fluid flow path is a plurality, and is provided in a row to form a third row of third fluid flow paths.
The heat exchanger according to any one of claims 1 to 7, wherein

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