JP5744316B2 - Heat exchanger and heat pump system equipped with the heat exchanger - Google Patents

Description

  The present invention relates to a stacked heat exchanger configured by stacking heat transfer tubes and a heat pump system including the heat exchanger.

  2. Description of the Related Art Conventionally, a laminated heat exchanger configured by using a flat tube as a heat transfer tube and laminating the flat tubes has been disclosed. Such a heat exchanger includes a first flat tube that conducts a refrigerant that is a low-temperature fluid and a second flat tube that conducts a refrigerant that is a high-temperature fluid such that the refrigerant flows in the first direction. The flat tube and the second flat tube are laminated.

  As such, “a first flat tube 1 through which a low-temperature fluid flows, a second flat tube 2 arranged so that a high-temperature fluid flows and the flow direction of the high-temperature fluid is parallel to the flow direction of the low-temperature fluid; The at least one flat tube is composed of a plurality of flat tubes arranged in the stacking direction, and both ends of the plurality of flat tubes are connected to each other in the flow direction and the stacking direction. Bend in a direction orthogonal to any of the above, and a plurality of flat tubes, an inlet header and an outlet header constitute a parallel flow path, and either the inlet header or the outlet header is constituted by a tubular header, A plurality of flat tubes constituting parallel flow paths are bundled and connected so that the tube axis direction of the tubular header and the flow direction of fluid in the flat tubes are the same (for example, Patent Document 1)

WO 2007/122585 (for example, FIG. 17)

  Since the heat exchanger as described in Patent Document 1 adopts a structure in which heat transfer tubes (flat tubes) are stacked, it has high performance and high space efficiency. However, since at least one of the header tubes into which the refrigerant flows is connected to a heat transfer tube bent in a direction perpendicular to the stacking direction of the heat transfer tubes, the heat transfer tube at that time is bent in the width direction. However, there are still problems in increasing the dead space due to the header tube.

  The present invention has been made to solve the above-described problems. A heat exchanger that eliminates bending in the width direction of the heat transfer tube and reduces dead space due to the header tube, and the heat exchanger are provided. It aims at providing the heat pump system provided.

  The heat exchanger according to the present invention includes a plurality of first heat transfer tubes having a flow path through which a first fluid flows, and a flow path through which the second fluid flows, alternately stacked with the first heat transfer tubes. A plurality of second heat transfer tubes, a first header that distributes the first fluid to the first heat transfer tubes, a second header that distributes the second fluid to the second heat transfer tubes, and the first header A lid projecting portion communicating with the first heat transfer tube, a first lid provided at a flow channel end portion of the first heat transfer tube, and a lid projecting portion communicating with the second header, and a flow channel of the second heat transfer tube. A second lid provided at the end, and the lid protrusion of the first lid and the lid protrusion of the second lid are arranged in the stacking direction of the first heat transfer tube and the second heat transfer tube. The first header and the second header are arranged so as not to overlap each other, and each of the first heat transfer tube and the second heat transfer tube has a width range. It is intended to be placed within.

  The heat pump system according to the present invention includes a first refrigerant circuit and a second refrigerant circuit that are cascade-connected via the heat exchanger.

  According to the heat exchanger according to the present invention, the first header and the second header do not protrude into the width of the first heat transfer tube and the second heat transfer tube, and the dead space in the width direction of the heat transfer tube can be reduced. it can. As a result, the entire heat exchanger can be made compact.

  According to the heat pump system according to the present invention, since the heat exchanger is provided, the unit on which the heat exchanger is mounted can be made compact.

It is a schematic perspective view which shows an example of the external appearance structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the cover inserted in the flow-path edge part of the heat exchanger which concerns on Embodiment 1 of this invention. It is principal part sectional drawing which shows the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the heat exchanger which concerns on Embodiment 2 of this invention. It is explanatory drawing for demonstrating the heat exchanger which concerns on Embodiment 3 of this invention. It is a schematic side view which shows the state which looked at the principal part of the heat exchanger which concerns on Embodiment 3 of this invention from the side surface. It is a schematic sectional drawing which shows the principal part cross section of the heat exchanger tube part of the heat exchanger which concerns on Embodiment 4 of this invention. It is a circuit diagram which shows typically an example of the basic composition of the heat pump system which concerns on Embodiment 5 of this invention. It is a circuit diagram which shows typically another example of the basic composition of the heat pump system which concerns on Embodiment 5 of this invention. It is a circuit diagram which shows typically another example of the basic composition of the heat pump system which concerns on Embodiment 5 of this invention. It is a circuit diagram which shows typically another example of the basic composition of the heat pump system which concerns on Embodiment 5 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a schematic perspective view showing an example of an external configuration of a heat exchanger 10 according to Embodiment 1 of the present invention. FIG. 2 is an explanatory view for explaining the heat exchanger 10 ((a) is a top view, (b) is an AA cross-sectional view, and (c) is a side view). FIG. 3 is an explanatory view for explaining a lid inserted into the end of the flow path of the heat exchanger 10 ((a) is a front view and (b) is a top view). FIG. 4 is a cross-sectional view of a main part showing the configuration of the heat exchanger 10. The heat exchanger 10 will be described with reference to FIGS. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. In the drawings, the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification.

  As shown in FIGS. 1 and 2, the heat exchanger 10 includes a plurality of first heat transfer tubes 1 and second heat transfer tubes 2 having the same length and having a flow path through which a fluid such as a refrigerant flows. It has a structure. The first heat transfer tube 1 and the second heat transfer tube 2 have a flat cross-sectional shape that is a straight line at the long side portion and a semicircular shape at the short side portion, for example. And the 1st heat exchanger tube 1 and the 2nd heat exchanger tube 2 are laminated | stacked alternately by making a long-length part into the joining surface 7. FIG. As shown in FIG. 4, the first heat transfer tube 1 and the second heat transfer tube 2 are joined to each other using a brazing material 21 on the joining surface 7. By using the brazing material 21, it is possible to improve the brazing performance of the lid 8 to be mounted thereafter.

  Further, inside the first heat transfer tube 1, a plurality of communication holes 1a are provided side by side in the width direction. Inside the second heat transfer tube 2, a plurality of communication holes 2a are provided side by side in the width direction. A fluid flows inside the communication hole 1a and the communication hole 2a. That is, the communication hole 1a and the communication hole 2a serve as a fluid flow path. The fluid flowing through the communication hole 1a of the first heat transfer tube 1 is referred to as a first refrigerant, and the fluid flowing through the communication hole 2a of the second heat transfer tube 2 is referred to as a second refrigerant.

  The flow path end 5 of the first heat transfer tube 1 and the flow path end 6 of the second heat transfer tube 2 are provided with a lid 8 having a lid protruding portion 8a as shown in FIG. The lid 8 is provided at the flow path end 5 of the first heat transfer tube 1 and the flow path end 6 of the second heat transfer tube 2 so that the lid protrusion 8a does not overlap in the stacking direction of the heat transfer tubes. The lid 8 provided at the flow path end 5 of the first heat transfer tube 1 corresponds to the first lid of the present invention, and the lid 8 provided at the flow path end 6 of the second heat transfer tube 2 is provided. This corresponds to the second lid of the present invention. The lid protrusion 8 a is provided so as to be biased to one side in the width direction of the lid 8. The lid protrusion 8a of the lid 8 provided at the flow path end 5 of the first heat transfer tube 1 and the lid protrusion 8a of the lid 8 provided at the flow path end 6 of the second heat transfer tube 2 are transferred. It arrange | positions so that it may not overlap in the lamination direction of a heat tube. That is, the lid protrusions 8a are arranged in a staggered manner when the heat exchanger 10 is viewed from the header side.

  The first header 3 is provided so that the lid protrusion 8 a provided at the flow path end 5 of the first heat transfer tube 1 communicates in the stacking direction of the first heat transfer tube 1. Similarly, the 2nd header 4 is provided so that the cover protrusion part 8a provided in the flow-path edge part 6 of the 2nd heat exchanger tube 2 may be connected in the lamination direction of the 2nd heat exchanger tube 2. FIG. That is, the first header 3 and the second header 4 are arranged so as to be arranged in parallel without protruding from the width of the first heat transfer tube 1 and the second heat transfer tube 2 when the heat exchanger 10 is viewed from the header side. Has been. The first and second refrigerants communicate with each other by the first header 3 and the second header 4.

  Here, the heat exchanger 10 should just comprise the heat exchanger tube part by laminating | stacking the 1st heat exchanger tube 1 and the 2nd heat exchanger tube 2, and the 1st heat exchanger tube 1 and the 2nd heat exchanger which are each formed as a different body. The heat transfer tube portion may be configured by laminating the heat tubes 2, or the heat transfer tube portion may be configured by integrally forming the first heat transfer tube 1 and the second heat transfer tube 2 by integral extrusion molding or integral drawing. . By integrally molding the first heat transfer tube 1 and the second heat transfer tube 2, the number of parts can be reduced, the brazing of the heat transfer tube portion becomes unnecessary, and the performance as a heat exchanger can be improved. it can.

  The second heat transfer tube 2 is made of a material having good thermal conductivity, such as an aluminum alloy, copper, stainless steel, or the like. The second heat transfer tube 2 is formed by bending a flat plate by roll forming or the like and then electro-sewing (welding) seams at both ends of the flat plate, roll forming or press forming a cylinder, or extrusion forming. Alternatively, it can be produced by pultrusion.

  On the other hand, the first heat transfer tube 1 is made of a material having good heat conductivity, for example, an aluminum alloy, copper, stainless steel or the like, similar to the second heat transfer tube 2, but is formed by extrusion or pultrusion. Is manufactured by.

  The first header joint portion 50, which is a connection portion between the first heat transfer tube 1 and the first header 3, is brazed using a brazing material 21 such as an aluminum-silicon system. Similarly, the 2nd header junction part 51 which is a connection part of the 2nd heat exchanger tube 2 and the 2nd header 4 is brazed using the brazing materials 21, such as an aluminum-silicon system. Note that the port 3 </ b> A of the first header 3 and the port 4 </ b> A of the second header 4 are connected to a refrigerant circuit of a cooling system such as a heat pump device, which will be described later, on which the heat exchanger 10 is mounted.

  The lid 8 is made of a material having good thermal conductivity, such as an aluminum alloy, copper, stainless steel or the like. The lid protrusion 8a is made of a material having good thermal conductivity, such as aluminum alloy, copper, stainless steel, etc., and is constructed as a separate part from the lid 8, or as an integrally molded product such as casting. The lid 8 is configured as a processed product such as cutting. The shape of the lid protrusion 8a provided at the end of the lid 8 is shown as a circular shape in FIGS. 1 and 3, but is not limited to this, for example, a rectangular shape, an elliptical shape, other shapes, etc. But you can.

  As shown in FIG. 4, the heat exchanger 10 has a flat surface (joint surface 7) of the first heat transfer tube 1 and a flat surface (joint surface 7) of the second heat transfer tube 2, such as an aluminum-silicon system. It is configured by brazing and joining using a brazing material 21. With such a configuration, the heat exchanger 10 can reduce the dead space in the width direction of the heat transfer tubes, and the entire heat exchanger can be made compact. In other words, in the conventional heat exchanger, the header tube has been arranged so as to widen the width direction of the heat transfer tube, thereby reducing the space efficiency, but in the heat exchanger 10, without increasing the width direction of the heat transfer tube, The dead space can be reduced accordingly.

Here, a method for manufacturing the heat exchanger 10 will be described.
First, a plurality of first heat transfer tubes 1 and second heat transfer tubes having the same length and having a refrigerant flow path through which the refrigerant flows are prepared. And the 1st heat exchanger tube 1 and the 2nd heat exchanger tube 2 are laminated alternately. Next, a lid 8 having a lid protrusion 8 a is attached to the flow path end 5 of the first heat transfer tube 1 and the flow path end 6 of the second heat transfer tube 2. In this state, the heat transfer tube portion of the heat exchanger 10 is formed by brazing the joining surfaces of the first heat transfer tube 1 and the second heat transfer tube 2 and the lid 8 and the periphery of the lid 8.

  At that time, in order to perform brazing smoothly, as shown in FIG. 4, a lid mounting portion 9 a is provided at the flow path end 5 of the first heat transfer tube 1 and the flow path end 6 of the second heat transfer tube 2. Similarly, it is desirable to provide the heat transfer tube mounting portion 9b at the end portion of 8 as well. That is, it is preferable that the lid mounting portion 9a is male and the heat transfer tube mounting portion 9b is female so that both can be mounted and brazing can be performed smoothly. Then, using the lid protrusion 8a, the first heat transfer tube 1 and the first header 3 are communicated, the second heat transfer tube 2 and the second header 4 are communicated, and the lid projection 8a, the first header 3, and the lid The protrusion 8a and the second header 4 are connected and brazed. The heat exchanger 10 is completed by the manufacturing method as described above.

  The heat exchanger 10 is mounted on a refrigerant circuit of a cooling / heating system such as a heat pump device that uses heating / cooling. When using hot heat, the high temperature 1st refrigerant | coolant from a refrigerant circuit is supplied to the 1st heat exchanger tube 1, and it returns to a refrigerant circuit through the communicating hole 1a. On the other hand, the 2nd refrigerant | coolant which heat-exchanges with a 1st refrigerant | coolant is supplied to the 2nd heat exchanger tube 2, and the 2nd refrigerant | coolant heat-exchanged through the communicating hole 2a is applied to a utilization side, for example, heating or hot water supply. The first refrigerant and the second refrigerant exchange heat by flowing through the first heat transfer tube 1 and the second heat transfer tube 2 in a counterflow or parallel flow.

  The refrigerant channel cross-sectional area of the first heat transfer tube 1 and the refrigerant channel cross-sectional area of the second heat transfer tube 2 may be the same, but not necessarily the same. When there is a difference in the thermophysical value such as specific heat and density, the flow rate, the pressure condition, or the fluid property between the first refrigerant and the second refrigerant, the refrigerant channel cross-sectional area is set to the first heat transfer tube. What is necessary is just to make it differ with 1 and the 2nd heat exchanger tube 2. FIG. For example, when using carbon dioxide or a fluorocarbon refrigerant as the first refrigerant and using tap water or the like whose water quality is not sufficiently controlled as the second refrigerant, in order to improve the heat exchange performance, In order to suppress an increase in pressure loss due to adhesion of scale to the second heat transfer tube 2, the refrigerant flow passage area is preferably larger than the first heat transfer tube 1.

In the above description, the first heat transfer tube 1 and the second heat transfer tube 2 have been described using the same type of metal, but may be manufactured using different metals. In that case, for example, when the first heat transfer tube 1 is made of copper and the second heat transfer tube 2 is made of aluminum, the lid and header tube connected to the first heat transfer tube 1 are copper and the second heat transfer tube. Each of the heat transfer tubes, the lid, and the header tube may be made of the same type of metal so that the lid and header tube connected to 2 are made of aluminum. Alternatively, when the first heat transfer tube 1 is made of copper and the second heat transfer tube 2 is made of aluminum, the lid and header tube connected to each heat transfer tube are made of a metal (for example, stainless steel) other than copper and aluminum. You may comprise using the metal different from the metal used for each heat exchanger tube.
According to the present embodiment, even in the case of heat exchangers composed of heat transfer tubes made of different metals, it is possible to prevent the metal constituting the other flow channel from being exposed in the flow channel, corrosion prevention, corrosion resistance, etc. From this point of view, a more reliable heat exchanger can be configured.

Embodiment 2. FIG.
FIG. 5 is an explanatory diagram for explaining a heat exchanger 10A according to Embodiment 2 of the present invention (a top view showing an enlarged main part of the heat exchanger 10 according to Embodiment 1). The figure and (b) are the top views which expand and show the principal part of 10 A of heat exchangers which concern on Embodiment 2. FIG. The heat exchanger 10A will be described based on FIG. The basic configuration of the heat exchanger 10A according to the second embodiment is the same as that of the heat exchanger 10 described in the first embodiment. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  As shown in FIG. 5 (b), the heat exchanger 10A adopts a configuration in which the larger lid protrusion 8a is lengthened when at least one of the first header 3 and the second header 4 becomes larger. This is different from the heat exchanger 10 according to the first embodiment. FIG. 5 shows an example in which the second header 4 is larger. The large header means that the area is large when the header is viewed in plan. To lengthen the lid protrusion 8a means to make it longer than the length of the other lid protrusion 8a in the refrigerant flow direction. How much longer it may be determined by the size of the smaller header (first header 3 in FIG. 5). Other configurations and functions are the same as those of the heat exchanger 10 shown in the first embodiment.

  By adopting such a configuration, the first header 3 and the second header 4 can be arranged without interference. That is, when the first header 3 and the second header 4 having a size as shown in FIG. 5A are arranged in parallel, the first heat transfer tube 1 and the second heat transfer tube 2 are arranged in the direction of widening the width direction. As shown in FIG. 5 (b), the lid protrusion 8a connected to the larger header can be lengthened so that interference between the headers can be avoided and the dead space in the width direction of the heat transfer tube is reduced. Therefore, the entire heat exchanger can be made compact.

Embodiment 3 FIG.
FIG. 6 is an explanatory diagram for explaining a heat exchanger 10B according to Embodiment 3 of the present invention ((a) is a front view and (b) is a top view). FIG. 7 is a schematic side view showing a state in which the main part of the heat exchanger 10B is viewed from the side. The heat exchanger 10B will be described based on FIGS. The basic configuration of the heat exchanger 10B according to Embodiment 3 is the same as that of the heat exchanger 10 described in Embodiment 1. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.

  As shown in FIGS. 6 and 7, the heat exchanger 10B is configured so that the thickness of the lid protrusion 8a (thickness in the stacking direction of the heat transfer tubes) is changed from the thickness of the lid 8 (thickness in the stacking direction of the heat transfer tubes). It is different from the heat exchangers according to the first and second embodiments in that a configuration in which the through hole 15 is provided so as to penetrate the surface where the lid protrusions 8a are in contact with each other when the 8a is increased to contact with the stacking direction. ing. That is, in the heat exchanger 10B, the flow path cross-sectional area of the lid protrusion 8a is made larger than that of the lid protrusion 8a of the heat exchanger according to Embodiment 1 and Embodiment 2. Other configurations and functions are the same as those of the heat exchanger according to the first and second embodiments.

  By adopting such a configuration, the use of the through hole 15 becomes an alternative to the header, and the number of parts can be reduced. Regarding the sealing of the end portion of the lid protruding portion 8a at that time, as shown in FIG. 11A, the end sealing material 9c may be used for sealing. Or as shown in FIG.11 (b), you may respond by taking the cover protrusion part 8a long and providing the edge crushing part 9d, and sealing. In addition, it can replace with a header by connecting the connection port 16 to the through-hole 15 formed in the lid | cover protrusion part 8a of the 1st heat exchanger tube 1 located in the uppermost stage (same also about the 2nd heat exchanger tube 2).

  By adopting such a configuration, the first header 3 and the second header 4 can be omitted, and the dead space can be reduced accordingly. That is, if the cover protrusion 8a having the structure as shown in FIG. 7 is provided, the first header 3 and the second header 4 are not provided, and there is a problem of dead space caused by the presence of the header. Disappear. Therefore, according to the heat exchanger 10B, the entire heat exchanger can be made compact by the amount that the header is not provided.

Embodiment 4 FIG.
FIG. 8: is a schematic sectional drawing which shows the principal part cross section of the heat exchanger tube part of the heat exchanger which concerns on Embodiment 4 of this invention. Based on FIG. 8, the heat exchanger tube part (the 1st heat exchanger tube 1 and the 2nd heat exchanger tube 2) of the heat exchanger which concerns on Embodiment 4 is demonstrated. The basic configuration of the heat exchanger according to the fourth embodiment is the same as that of the heat exchanger 10 described in the first embodiment. In the fourth embodiment, differences from the first to third embodiments will be mainly described, and the same parts as those in the first to third embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.

  In the fourth embodiment, several patterns of cross-sectional shapes of the first heat transfer tube 1 and the second heat transfer tube 2 constituting the heat exchanger will be described. FIG. 8A shows a heat transfer tube portion whose cross-sectional shape is rectangular, FIG. 8B shows a heat transfer tube portion whose cross-sectional shape is elliptical, and FIG. 8C shows an elliptical cross-sectional shape. The heat transfer tube portion having a shape and a groove formed on the inner peripheral surface, and the heat transfer tube portion in which the corrugated plate is inserted in FIG. FIG. 8 (e) shows a heat transfer tube portion in which the cross-sectional shape is an elliptical shape and a large number of holes are formed inside.

  The heat exchanger according to the first to third embodiments includes a heat transfer tube portion in which a cross-sectional shape is rectangular and a plurality of communication holes (communication holes 1a and communication holes 2a) are formed. As an example, the shape of the heat transfer tube portion may be a shape as shown in FIG. 8 or a shape obtained by appropriately combining them.

Embodiment 5 FIG.
FIG. 9 is a circuit diagram schematically showing an example of the basic configuration of the heat pump system 100 according to Embodiment 5 of the present invention. FIG. 10 is a circuit diagram schematically showing another example of the basic configuration of the heat pump system 100 according to Embodiment 5 of the present invention. FIG. 11 is a circuit diagram schematically showing still another example of the basic configuration of the heat pump system 100 according to Embodiment 5 of the present invention. FIG. 12 is a circuit diagram schematically showing still another example of the basic configuration of the heat pump system 100 according to Embodiment 5 of the present invention. The heat pump system 100 will be described with reference to FIGS.

  The heat pump system 100 shown in FIGS. 9 to 12 includes the heat exchanger according to any one of the first to third embodiments, and two circuits are cascade-connected via the heat exchanger. The exchanger includes the heat transfer tube section shown in any of the fourth embodiment. Therefore, heat pump system 100 shown in FIGS. 9 to 12 can achieve a compact unit in which the heat exchanger according to any one of Embodiments 1 to 3 is mounted. In the fifth embodiment, the heat pump system 100 is described as including the heat exchanger 10 according to the first embodiment. However, the heat pump system 100 includes the heat exchanger according to the second or third embodiment. May be.

  A heat pump system 100 shown in FIG. 9 includes a first refrigerant circuit 101 through which a first refrigerant flows, a second refrigerant circuit 102 through which a second refrigerant flows, and a heat exchanger 10 that performs heat exchange between the first refrigerant and the second refrigerant. have. The first refrigerant circuit 101 is configured by connecting the compressor 31, the first refrigerant flow path side of the heat exchanger 10, the expansion valve 33, and the outdoor heat exchanger 34 by piping. A fan 39 that supplies air to the outdoor heat exchanger 34 is installed in the vicinity of the outdoor heat exchanger 34. The second refrigerant circuit 102 is configured such that the use side heat exchanger 35, the pump 36, and the second refrigerant flow path side of the heat exchanger 10 are connected by piping. Here, a case where R410A is used as the first refrigerant and water is used as the second refrigerant will be described as an example.

  In the 1st refrigerant circuit 101, the 1st refrigerant | coolant which became high temperature high pressure with the compressor 31 is heat-exchanged with a 2nd refrigerant | coolant with the heat exchanger 10, and is condensed. Further, the first refrigerant is decompressed by the expansion valve 33, is evaporated by exchanging heat with the air from the fan 39 by the outdoor heat exchanger 34, and returns to the compressor 31. In the second refrigerant circuit 102, the second refrigerant heated by the heat exchanger 10 is supplied to the use side heat exchanger 35 by the pump 36 and radiates heat. As the use-side heat exchanger 35, for example, a radiator or a floor heating heater is applied and used as a heating system.

  Heating the heat pump system 100 using the heat exchanger 10 as a heat source with the use side heat exchanger 35 as described above has an energy saving effect as compared with a heating or hot water supply system using a conventional boiler as a heat source. When water is used as the second refrigerant, the second heat transfer tube 2 and the second header 4 are formed of a corrosion-resistant material, and the portion of the heat exchanger 10 in contact with water is configured to have corrosion resistance to water. It is better to do it. For the same reason, the lid 8 and the lid protrusion 8a may be formed of a corrosion resistant material.

  The heat pump system 100 shown in FIG. 10 is the same as the heat pump system 100 shown in FIG. 9 in that it has the first refrigerant circuit 101, the second refrigerant circuit 102, and the heat exchanger 10, but the use side The heat exchanger 35 is installed in a tank 38 and is applied as a hot water supply system that heats and supplies water supplied to the tank 38. Other configurations and functions are the same as those of the heat pump system 100 shown in FIG. Thus, by supplying hot water with the use side heat exchanger 35 using the heat pump system 100 using the heat exchanger 10 as a heat source, there is an energy saving effect as compared with a heating or hot water supply system using a conventional boiler as a heat source.

  In addition, in the heat pump system 100 (hot water supply system) shown in FIG. 10, by changing the refrigerant circuit (not shown) and using a four-way valve (not shown), not only the dedicated use for hot water supply but also cold water Needless to say, it can be used exclusively or by switching between hot water supply and cold water.

  The heat pump system 100 shown in FIG. 11 is the same as the heat pump system 100 shown in FIG. 9 in that the first refrigerant circuit 101, the second refrigerant circuit 102, and the heat exchanger 10 are included. The circulation of the first refrigerant in the refrigerant circuit 101 is opposite to that of the heat pump system 100 shown in FIG. Here, a case where R410A is used as the first refrigerant and water is used as the second refrigerant will be described as an example.

  In the first refrigerant circuit 101, the first refrigerant that has become high temperature and high pressure in the compressor 31 is condensed by exchanging heat with the air from the fan 39 in the outdoor heat exchanger 34. Further, the first refrigerant is decompressed by the expansion valve 33, exchanges heat with the second refrigerant in the heat exchanger 10, evaporates, and returns to the compressor 31. The second refrigerant cooled by the heat exchanger 10 is supplied to the use side heat exchanger 35 by the pump 36. As the use side heat exchanger 35, for example, an air heat exchanger may be applied and used as a cooling system or a radiant cooling system using a cold water panel or the like. In this way, the heat pump system 100 using the heat exchanger 10 can be used as a heat source to cool or cool the use side heat exchanger 35.

  A heat pump system 100 shown in FIG. 12 includes a four-way valve 32 and can be switched between hot and cold. The heat pump system 100 shown in FIGS. 9 to 11 uses heat or cold exclusively, but the heat pump system 100 shown in FIG. 12 uses the four-way valve 32 to switch between heat and cold. It can be used. Thus, by using the heat pump system 100 using the heat exchanger 10 with heat or cold, there is an energy saving effect compared to a heating or hot water supply system using a conventional boiler as a heat source.

  In the fifth embodiment, the case where R410A is used as the first refrigerant and water is used as the second refrigerant has been described as an example. However, the type of the refrigerant is not limited to these, and other chlorofluorocarbon refrigerants as the first refrigerant, Alternatively, natural refrigerants such as carbon dioxide and hydrocarbons may be used, and fluorocarbon refrigerants, natural refrigerants such as carbon dioxide and hydrocarbons, tap water, distilled water, brine, and the like may be used as the second refrigerant.

  1 1st heat transfer tube, 1a communication hole, 2nd heat transfer tube, 2a communication hole, 3rd header, 3A port, 4th header, 4A port, 5 channel end, 6 channel end, 7 joint Surface, 8 lid, 8a lid protrusion, 9a lid mounting portion, 9b heat transfer tube mounting portion, 9c end sealing material, 9d end crushing portion, 10 heat exchanger, 10A heat exchanger, 10B heat exchanger, 15 Through hole, 16 connection port, 21 brazing material, 31 compressor, 32 four-way valve, 33 expansion valve, 34 outdoor heat exchanger, 35 user side heat exchanger, 36 pump, 38 tank, 39 fan, 50 header joint, 51 header joint, 100 heat pump system, 101 refrigerant circuit, 102 refrigerant circuit.

Claims (8)

A plurality of first heat transfer tubes having flow paths through which the first fluid flows;
A plurality of second heat transfer tubes that are alternately stacked with the first heat transfer tubes and have flow paths through which a second fluid flows;
A first header that distributes the first fluid to the first heat transfer tubes;
A second header that distributes the second fluid to the second heat transfer tubes;
A lid protrusion that communicates with the first header, and a first lid that is provided at a flow path end of the first heat transfer tube;
A lid protrusion that communicates with the second header, and a second lid that is provided at a flow path end of the second heat transfer tube;
The lid protrusion of the first lid and the lid protrusion of the second lid are arranged so as not to overlap in the stacking direction of the first heat transfer tube and the second heat transfer tube,
Each of said 1st header and said 2nd header is arrange | positioned in the range of the width | variety of said 1st heat exchanger tube and said 2nd heat exchanger tube. The heat exchanger characterized by the above-mentioned. The first heat transfer tube and the second heat transfer tube are:
The heat exchanger according to claim 1, wherein the heat exchanger is configured in a flat shape in which a part of a cross-sectional shape is linear. The first heat transfer tube and the second heat transfer tube are:
The heat exchanger according to claim 2, wherein the flat surfaces are joined by brazing. The first heat transfer tube and the second heat transfer tube are:
The heat exchanger according to claim 1, wherein the heat exchanger is constituted by an integral heat transfer tube. In the one using the first header and the second header having different sizes,
The heat exchanger according to any one of claims 1 to 4, wherein the lid protrusion connected to the larger side is longer than the lid protrusion connected to the smaller side. vessel. The thickness of the lid protrusion is larger than the thickness of the first lid and the second lid, the lid protrusions are in contact with each other in the stacking direction, and a through hole passes through the joint surface of the lid protrusions. The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger is formed and uses the through hole as the first header and the second header. The cross-sectional shapes of the first heat transfer tube and the second heat transfer tube are configured by a rectangular shape, an elliptical shape, a grooved shape, a shape with a corrugated plate inserted, a flat multi-hole tube shape, or a combination thereof. The heat exchanger according to claim 1, wherein: A heat pump system comprising: a first refrigerant circuit and a second refrigerant circuit that are cascade-connected via the heat exchanger according to any one of claims 1 to 7.

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