JP4827882B2 - Heat exchanger module, heat exchanger, indoor unit and air-conditioning refrigeration apparatus - Google Patents

Description

  The present invention relates to a heat exchanger module, a heat exchanger, an indoor unit, and an air conditioning refrigeration apparatus, and in particular, a heat exchanger module that improves heat exchange efficiency by flowing a refrigerant (working fluid) flowing through the heat exchanger, The present invention relates to a heat exchanger, an indoor unit, and an air conditioning refrigeration apparatus.

  Conventionally, there is a plate fin and tube type heat exchanger. As such, “a heat transfer tube provided with a plurality of flow paths inside a U-shaped flat cross section, a header in which the end of the heat transfer tube communicated, and a space in the header are separated. A heat exchanger that includes a vertical partition plate and a horizontal partition plate that form a refrigerant flow from an inflow pipe to an outflow pipe and that forms a refrigerant flow that is a counterflow or a parallel flow with respect to a gas flow has been proposed. (For example, refer to Patent Document 1).

JP 2003-287390 A

  In a conventional heat exchanger such as Patent Document 1, heat exchange air flows in the width direction of the flat heat transfer tube, and heat exchange is performed between the heat exchange air and the cooling medium. When this heat exchanger acts as an evaporator, the refrigerant flowing in the refrigerant flow path in the heat transfer tube on the windward side of the flat heat transfer tube is cooled by heat exchange air (low temperature air) that has not been sufficiently exchanged heat. Therefore, heat is exchanged efficiently and the refrigerant temperature is low. On the other hand, the refrigerant flowing in the refrigerant channel in the leeward heat transfer tube has already undergone heat exchange and heat exchange with the heat exchange air that is at a high temperature. It cannot be cooled sufficiently.

  Thus, in the conventional heat exchanger, there is a problem that a large difference occurs in the heat exchange amount between the windward side and the leeward side of the flat heat transfer tube, and the overall heat exchange amount becomes small. It was. On the other hand, in the conventional heat exchanger, a flat heat transfer tube having a flat shape is used. Therefore, by installing the heat exchanger so that the long axis direction of the flat tube coincides with the main flow direction of the air flow, Ventilation resistance is significantly reduced, and the driving power of the blower that generates the air flow can be greatly reduced.

  However, when such a conventional heat exchanger is used as an evaporator, condensed water will be generated. However, since a flat heat transfer tube is used, a circular heat transfer tube is used. Compared to existing heat exchangers, the drainage of condensed water was poor and the condensed water would be held. That is, when a conventional heat exchanger using a flat-shaped flat heat transfer tube is used as an evaporator, there is a problem that the effect of reducing ventilation resistance cannot be sufficiently obtained by the generated condensed water.

  In order to solve such a problem, by providing a partition plate that divides the header longitudinal direction inside the header and a partition plate that divides the header lateral direction, a refrigerant flow that becomes a counterflow or a parallel flow with respect to the gas flow direction is provided. There is a heat exchanger designed to be configured. However, in the case of such a configuration, when it is desired to greatly shift the position of the flat heat transfer tube between the windward and leeward, or when it is desired to conduct the flat heat transfer tube at a position farther from the adjacent heat transfer, it is structurally realized. Has the problem of being difficult or impossible. Moreover, when realizing an air conditioner using such a conventional heat exchanger, optimization of the form of the air conditioner, optimization of the shape of the heat exchanger according to each capability, and flow of the refrigerant In order to realize this optimization, it is necessary to produce a dedicated header for each, which may cause a significant cost increase.

  The present invention has been made in order to solve the above-described problems, and a heat exchanger module, a heat exchanger module, and a heat exchanger module having a configuration in which a flow path of a working refrigerant (refrigerant) can be freely set to improve heat exchange efficiency. It aims at providing an exchanger, an indoor unit, and an air-conditioning refrigerating apparatus.

A heat exchanger module according to the present invention is stacked in parallel at a predetermined interval, and a plurality of plate-like fins through which a fluid passes, and inserted so as to be orthogonal to the plate-like fins, have a flow path cross-sectional shape. Connected to the plurality of heat transfer tubes, each having a flat shape and having a plurality of partition walls therein, and the ends of the plurality of heat transfer tubes forming the flow path of the working fluid, and communicating the plurality of heat transfer tubes A pair of headers, an inflow pipe attached to at least one of the headers and allowing a working fluid to flow into the heat transfer pipe, and attached to at least one of the headers and flowing out the working fluid from the heat transfer pipes A plurality of chambers to which at least one of the end portions of the heat transfer tubes is connected, and the plurality of chambers formed in the pair of headers are formed in the header. Wherein the working fluid from the inlet pipe is passed through the heat transfer tubes of the plurality of forming a flow path of a series of working fluid to flow out from the outlet pipe, one said inlet pipe and two the heat transfer tubes of the in A collision part that causes the working fluid flowing in from the inflow pipe to collide with a position corresponding to an intermediate part of the two heat transfer tubes in the room to which the gas is connected to mix the working fluid in the gas state and the working fluid in the liquid state The heat transfer tube is formed by forming a projecting portion provided with an area of the impingement portion larger than the cross-sectional area of the flow path of the inflow tube, and connecting the projecting portion to the chamber in which the projecting portion is formed. It protrudes from the edge part of this.

A heat exchanger according to the present invention is configured by combining a plurality of the above heat exchanger modules. Moreover, the indoor unit which concerns on this invention accommodated said heat exchanger and an indoor air blower, It is characterized by the above-mentioned. Furthermore, an air-conditioning refrigeration apparatus according to the present invention is characterized in that the above-described indoor unit is mounted. Furthermore, the manufacturing method of the heat exchanger which concerns on this invention manufactures said heat exchanger.

  According to the indoor unit module of the present invention, the pitch in the laminating direction of the plate-like fins, the fin thickness, the width of the fin along the air flow, the step pitch adjacent to the step direction of the heat transfer tube, the long axis length of the heat transfer tube In addition, the short axis length can be easily designed within a predetermined range. That is, in the heat exchanger module according to the present invention, labor and cost required for manufacturing can be greatly reduced.

  According to the heat exchanger according to the present invention, by combining the above heat exchanger modules, it is possible to easily form a plurality of refrigerant channels communicating in series, and to form a wide variety of refrigerant paths. . Further, when this heat exchanger functions as an evaporator, the refrigerant that has flowed through the refrigerant channel on the windward side of the heat transfer tube can be flowed through the refrigerant channel on the leeward side to reciprocate the refrigerant, The air flow and the parallel flow can be realized, and the heat exchange efficiency is improved. Furthermore, when this heat exchanger functions as a condenser, the refrigerant that has flowed through the refrigerant channel on the lee side of the heat transfer tube can be caused to flow through the refrigerant channel on the windward side to reciprocate the refrigerant. The air flow can be counterflowed, and the heat exchange efficiency is improved.

  According to the indoor unit of the present invention, heat exchangers that can form a wide variety of refrigerant paths are accommodated. For example, each heat exchanger is divided into a condenser and a part. A path pattern that functions as an evaporator can be formed, and a reheat dehumidification operation can be performed. As a result, it is possible to increase capacity and improve energy efficiency. Moreover, a piping space can be omitted and a compact indoor unit can be realized. Furthermore, according to the air conditioner according to the present invention, since the indoor unit described above is mounted, an increase in capacity, an improvement in energy efficiency, and a reduction in size are realized.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a perspective view showing an example of the overall configuration of a heat exchanger module 12A according to Embodiment 1 of the present invention. Based on FIG. 1, the structural example of 12 A of heat exchanger modules is demonstrated. The heat exchanger module 12A is a minimum unit constituting the heat exchanger. That is, when actually used as a heat exchanger, it is possible to configure a heat exchanger with one heat exchanger module 12A, but heat exchange is performed by combining two or more heat exchanger modules 12A. It is also possible to configure a vessel. 1 to 6, the heat exchanger module 12A as a minimum unit of the heat exchanger will be described, and then the heat exchanger configured by combining the heat exchanger modules 12A will be described.

  This heat exchanger module 12 </ b> A has an external air (fluid) flowing from a gap formed between the refrigerant that conducts through the flat tube 3 that is a heat transfer tube provided inside and the plate-like fins 4. And has a function of exchanging heat. As shown in FIG. 1, the heat exchanger module 12A includes two headers 1A, a lid 2 that seals the header 1A, a plurality of (here, twelve) flat tubes 3, and a plurality of flat tubes 3 inserted therein. The plate-like fins 4 are formed, an inflow pipe 5 that is a refrigerant pipe communicating with the header 1A, and an outflow pipe 6 that is a refrigerant pipe communicating with the header 1A. As shown in FIG. 1, the flat tube 3 is arranged in the step direction (direction orthogonal to the refrigerant flow), the longitudinal direction of the flat tube 3 is the longitudinal direction (refrigerant flow direction), the step direction, and the longitudinal direction. The direction that intersects perpendicularly is defined as the column direction and is used in the following description.

  A pair of headers 1A are attached to opposite side surfaces of the heat exchanger module 12A. In addition, two inflow pipes 5, two outflow pipes 6, and a plurality of flat tubes 3 are connected to the header 1 </ b> A. The header 1A is connected to both ends of each flat tube 3 and has a function of conducting the refrigerant flowing in from the inflow tube 5 to each flat tube 3, and a function of flowing out the refrigerant from each flat tube 3 to the outflow tube 6. ,have. That is, the header 1 </ b> A forms a refrigerant flow path in which the inflowing refrigerant flows out through the flat tube 3. The lid 2 seals the inside of the header 1A from the side where the inflow pipe 5 and the outflow pipe 6 of the header 1A are connected. That is, the inflow pipe 5 and the outflow pipe 6 are attached to the header 1A via the lid 2 and communicate with the room 8 inside the header 1A.

  The plate-like fins 4 are made of a metal plate having a predetermined thickness. In the heat exchanger module 12A, a plurality of plate-like fins 4 are arranged so as to be stacked at a predetermined interval. The flat tube 3 is disposed so as to be inserted into the plate-like fins 4 and conducts the refrigerant flowing in through the header 1A. The inflow pipe 5 allows the refrigerant to be conducted to the flat pipe 3 to flow into the header 1A. The outflow pipe 6 allows the refrigerant that has been conducted through the flat tube 3 to flow out of the header 1A. Note that the functions of the inflow pipe 5 and the outflow pipe 6 are reversed depending on how the refrigerant flows. In FIG. 1, two in the central part are the inflow pipe 5 and two in the both end parts are the outflow pipes 6. The case is shown as an example. Although FIG. 1 is simplified, actually, a plurality of plate-like fins 4 are arranged so as to be orthogonal to the flat tube 3.

  FIG. 2 is a perspective view showing the inside of the header 1A so as to be visible. Based on FIG. 2, the inside of the header 1A will be described. As shown in FIG. 2, the lid 2 is detachable from the header 1A, and the inside of the header 1A can be seen by removing the lid 2. As can be seen from FIGS. 1 and 2, the heat exchanger module 12 </ b> A according to the first embodiment exchanges heat between the refrigerant that conducts in the flat tube 3 and the air that flows outside the flat tube 3. Generally, it is what is called the plate fin and tube type. The configuration of the heat exchanger module 12A will be described in more detail.

  This heat exchanger module 12A is configured by arranging a plurality of plate-like fins 4 and a plurality of flat tubes 3 inserted so as to be substantially orthogonal to the plate-like fins 4 in one row. ing. A header 1 </ b> A to which the inflow pipe 5 and the outflow pipe 6 are connected is connected to one side in the longitudinal direction of the plurality of flat tubes 3. That is, holes are formed in the header 1A at a predetermined interval so that one end of each of the plurality of flat tubes 3 can be connected thereto. Further, another header 1A (hereinafter referred to as header 1A ′) to which the inflow pipe 5 and the outflow pipe 6 are not connected is connected to the other side in the longitudinal direction of the plurality of flat tubes 3. Has been. Further, a plurality of chambers 8 in which one or two flat tubes 3 are connected are formed inside the header 1A and the header 1A '.

  Then, by attaching the lid 2 to which the inflow pipe 5 and the outflow pipe 6 are connected to the header 1A, the header 1A is sealed and a refrigerant flow path from the inflow pipe 5 to the outflow pipe 6 is formed. become. That is, this refrigerant flow path is in the order of the inflow pipe 5, each room 8 of the header 1 A, each flat pipe 3, each room 8 of the header 1 A ′, each flat pipe 3, each room 8 of the header 1 A, and the outflow pipe 6. It will be formed to connect. With reference to FIG. 3, the refrigerant flow in the heat exchanger module 12A will be described in detail.

  FIG. 3 is a cross-sectional view showing an example of a cross-sectional configuration of the heat exchanger module 12A. Based on FIG. 3, the flow of the refrigerant in the heat exchanger module 12A will be described. In addition, the arrow shown in FIG. 3 represents the flow of the refrigerant. In FIG. 3, the intermediate portion of the heat exchanger module 12A is omitted. As shown in FIG. 3, the refrigerant flowing in from the inflow pipe 5 conducts each flat tube 3 through the header 1A and the header 1A 'installed on the opposite side of the header 1A. That is, in the heat exchanger module 12A, the refrigerant flows out after reciprocating a predetermined number of times between the header 1A and the header 1A '.

  That is, in the heat exchanger module 12 </ b> A, when the refrigerant is conducted through each flat tube 3, the flat tube 3 is inserted so as to be substantially orthogonal, and air is passed through the plate-like fins 4 joined to the flat tube 3. It is designed to exchange heat. In FIG. 3, the case where two refrigerant flow paths are formed in the heat exchanger module 12A, that is, the case where there are two paths is shown as an example. However, the present invention is not limited to this. For example, as shown in FIG. A plurality of refrigerant flow paths may be formed.

  FIG. 4 is a schematic cross-sectional view illustrating an example of a vertical cross-sectional configuration of the flat tube 3 that is a heat transfer tube. Based on FIG. 4, the longitudinal cross-sectional structure of the flat tube 3 used for 12 A of heat exchanger modules, ie, a flow-path cross-sectional structure, is demonstrated. As shown in FIG. 4, a plurality of partition walls 9 are provided inside the flat tube 3, and a plurality of flow paths 10 separated by the partition walls 9 are formed. That is, the refrigerant flowing in from the header 1A is distributed to the flow path 10 and is conducted through the flat tube 3. In addition, although the material which comprises the flat tube 3 is not specifically limited, For example, it is good to comprise aluminum or its alloy as a material.

  FIG. 5 is a schematic cross-sectional view showing an example of a vertical cross-sectional configuration of another shape of the flat tube 3 (hereinafter referred to as a flat tube 3a). Based on FIG. 5, the longitudinal cross-sectional structure of the flat tube 3a used for 12 A of heat exchanger modules, ie, a flow-path cross-sectional structure, is demonstrated. Similarly to the flat tube 3, the flat tube 3 a is also provided with a plurality of partition walls 9, and a plurality of flow paths 10 separated by the partition walls 9 are formed. The flat tube 3 shown in FIG. 4 has a constant width in the short direction in the cross section of the flow path, whereas the flat tube 3 shown in FIG. 5 has a width on one side in the short direction in the cross section of the flow path ( The difference is that the width on the lower side of the drawing is narrower than the width on the other side (the width on the upper side of the drawing). Note that the flat tube 3a may be made of, for example, aluminum or an alloy thereof, similarly to the flat tube 3.

  FIG. 6 is an explanatory view of the plate-like fin 4 showing a part of the plate-like fin 4. Based on FIG. 6, the structure of the plate-shaped fin 4 used for 12 A of heat exchanger modules is demonstrated. 6A shows the configuration of the plate-like fin 4 in a state where the flat tube 3 shown in FIG. 4 is inserted, and FIG. 6B shows the state where the flat tube 3a shown in FIG. 5 is inserted. The structure of the plate-like fin 4 is shown respectively. In the following description, the plate-like fin 4 described in FIG. 6A may be referred to as a plate-like fin 4a, and the plate-like fin 4 described in FIG. 6B may be referred to as a plate-like fin 4b.

  As shown in FIGS. 6A and 6B, the plate-like fin 4 is formed with a cut and raised 11 between the flat tubes 3 adjacent to each other in the step direction. By cutting and raising 11 in the plate-like fins 4a, the heat exchange efficiency between the air passing between the plate-like fins 4a and the flat tubes 3 inserted in the plate-like fins 4a is improved, that is, the heat transfer is promoted. -ing Similarly, the cut and raised portions 11 are formed on the plate-like fins 4b shown in FIG. In addition, when the flat tube 3 (including the flat tube 3a) is inserted, the flat tube 3 and the plate-like fins 4 are closely fixed to each other and the fin stacking direction pitch is secured to the fins at the insertion portions of the flat tubes 3. A color (not shown) is provided. The fin collar and the flat tube 3 are joined by brazing.

  In the first embodiment, the pitch Fp in the stacking direction of the plate-like fins 4 is Fp = 0.001 to 0.0015 m, the fin thickness Ft is Ft = 0.0001 m, and the fin width Lp along the air flow is Lp = 0.0127 to 0.0137 m, the step pitch Dp, which is the center distance of the flat tubes adjacent in the step direction of the flat tube 3, is Dp = 0.000 to 0.012 m, and the long axis length Dl of the flat tube 3 is Dl = It is assumed that 0.01 to 0.02 m and the minor axis length Ds are set as Ds = 0.002 to 0.003 m. Moreover, in FIG. 1, although the case where the number of the flat tubes 3 is set to 12 is shown as an example, it can be set between 8 and 16 as necessary. In this way, the heat exchanger module 12A, which is the minimum unit constituting the heat exchanger, is configured. In actual use, a heat exchanger is often configured by combining a large number of modules.

  The length in the column direction of each room 8 formed inside the header 1A is equal to or longer than the length in the longitudinal direction of the cross section of the flow path of the flat tube 3, and the length in the step direction of each room 8 is one flat. When the pipe 3 is installed, the inner diameters of the inflow pipe 5 and the outflow pipe 6 attached to the lid 2 are substantially the same. When two flat tubes 3 are installed, the length of each room 8 in the step direction is set to the step pitch Dp + the short axis length Ds * 2 of the flat tube 3. The length in the step direction of the header 1 </ b> A is the step pitch Dp * the number of the flat tubes 3. The length of the header 1A in the row direction is limited to the width of the plate-like fins 4 (length in the step direction) +0.02 m. By doing so, the continuity of the plate-like fins 4 can be maintained when the heat exchanger modules 12A are arranged in the step direction, and the gap between the plate-like fins 4 is minimized when they are stacked in the row direction. be able to.

  FIG. 7 is a perspective view showing a heat exchanger 100A configured by stacking two heat exchanger modules 12A in the air flow direction. Based on FIG. 7, a heat exchanger 100A configured by stacking two heat exchanger modules 12A in the air flow direction will be described. That is, FIG. 7 shows a state where two of the heat exchanger modules 12A described in FIGS. 1 to 6 are overlapped in the air flow direction and function as one heat exchanger 100A. is there. In FIG. 7, the air flow is indicated by an arrow 14. Further, the leeward heat exchanger module 12A constituting the heat exchanger 100A is shown as a heat exchanger module 12a, and the leeward heat exchanger module 12A is shown as a heat exchanger module 12b.

  As shown in FIG. 7, the heat exchanger 100A is configured by connecting a heat exchanger module 12a and a heat exchanger module 12b with a U bend 13 which is a U-shaped refrigerant pipe. Specifically, the heat exchanger 100A connects the two outflow pipes 6 of the heat exchanger module 12a and the two inflow pipes 5 of the heat exchanger module 12b with U-bends 13, respectively, It is comprised so that a path may be formed. That is, in the heat exchanger module 12a, the central part is the inflow pipe 5 and both ends are the outflow pipes 6, and in the heat exchanger module 12b, the central part is the outflow pipe 6 and both ends are the inflow pipes 5, and both end portions thereof. Are connected by a U-bend 13.

  FIG. 8 is a schematic configuration diagram showing a refrigerant circuit of a heat pump type air-conditioning refrigeration apparatus 150 using the heat exchanger 100A. Based on FIG. 8, the circuit configuration and operation of the air conditioning refrigeration apparatus 150 will be described. This air-conditioning refrigeration apparatus 150 includes a refrigeration cycle in which a compressor 15, an outdoor heat exchanger 17, a throttling device 18, and an indoor heat exchanger 19 are sequentially connected by a refrigerant pipe 24 and a refrigerant pipe 25. The cooling operation or the heating capability is executed by circulating the refrigerant. The refrigerant flow during the cooling operation is indicated by a solid arrow, and the refrigerant flow during the heating operation is indicated by a broken arrow.

  The air-conditioning refrigeration apparatus 150 includes an outdoor unit 26 and an indoor unit 27. The outdoor unit 26 and the indoor unit 27 are connected by a refrigerant pipe 24 and a refrigerant pipe 25 to communicate with each other. In addition, in FIG. 8, although the case where the outdoor unit 26 and the indoor unit 27 are provided one each is shown as an example, it is not limited to this, You may provide two or more each. Moreover, the refrigerant | coolant piping 24 and the refrigerant | coolant piping 25 are piping which can connect the refrigerant | coolant of a liquid state, and a refrigerant | coolant of a gas state, and do not specifically limit a constituent material.

  In the outdoor unit 26, the compressor 15, the four-way valve 16, the outdoor heat exchanger 17, and the expansion device 18 are mounted in series. The outdoor unit 26 includes an outdoor fan 20 and an outdoor fan motor 21 that drives the outdoor fan 20. The compressor 15 sucks the refrigerant and compresses the refrigerant to be in a high temperature / high pressure state. For example, the compressor 15 may be of a type in which the rotation speed is controlled by an inverter and the capacity is controlled. The four-way valve 16 functions as a flow path switching unit, and switches between a refrigerant flow during heating operation and a refrigerant flow during cooling operation.

  The outdoor heat exchanger 17 functions as a condenser during the cooling operation and as an evaporator during the heating operation, performs heat exchange between the air supplied from the outdoor blower 20 and the refrigerant, and evaporates or condenses the refrigerant. Is. The expansion device 18 expands the refrigerant by reducing the pressure. The expansion device 18 may be constituted by, for example, an electronic expansion valve whose opening degree can be variably controlled. The outdoor blower 20 is constituted by a cross-flow blower or the like, and is driven by an outdoor blower motor 21 to supply air to the outdoor heat exchanger 17. The outdoor blower motor 21 is driven by the power supply to drive the outdoor blower 20. In addition, although the case where the expansion device 18 is provided in the outdoor unit 26 is shown as an example, it may be provided in the indoor unit 27.

  The indoor unit 27 is mounted with the indoor heat exchanger 19 connected to the refrigerant pipe 24 and the refrigerant pipe 25, and an indoor fan 22 and an indoor fan motor 23 that drives the indoor fan 22. ing. The indoor heat exchanger 19 functions as an evaporator during the cooling operation and as a condenser during the heating operation, and performs heat exchange between the air supplied from the indoor blower 22 and the refrigerant, and evaporates or condenses the refrigerant. Is. The indoor heat exchanger 19 is applied with the heat exchanger 100A described above. Therefore, the heat exchange efficiency in the indoor unit 27 can be improved. The indoor blower 22 is driven by the indoor blower motor 23 and supplies air to the indoor heat exchanger 19. The indoor blower motor 23 receives power supply and drives the indoor blower 22.

  FIG. 9 is a perspective view showing the internal configuration of the heat exchanger 100A in the header major axis direction (stage direction). FIG. 10 is a graph showing the distribution of the air temperature and the refrigerant temperature in the heat exchanger when the heat exchanger 100A functions as an evaporator. FIG. 11 is a graph showing the distribution of the air temperature and the refrigerant temperature in the heat exchanger when the heat exchanger 100A functions as a condenser. Based on FIGS. 9 to 11, the flow of the refrigerant in the heat exchanger 100 </ b> A will be described, and the heat exchange mode in the heat exchanger 100 </ b> A will be described.

  9A is a perspective view seen from the side where the inflow pipe 5 and the outflow pipe 6 are connected, and FIG. 9B is from the side where the inflow pipe 5 and the outflow pipe 6 are not connected. Each state seen through is shown. 10 and 11, the vertical axis indicates the temperature, and the horizontal axis indicates the air flow direction. In FIG. 10, the line (A) shows the air temperature flowing into the heat exchanger 100A, and the line (A) shows the refrigerant temperature that conducts the heat exchanger 100A. In FIG. 11, the line (U) shows the heat exchange. The temperature of the air flowing into the vessel 100A and the temperature of the refrigerant through which the line (D) conducts the heat exchanger 100A are shown.

  As shown in FIGS. 9 (a) and 9 (b), for convenience, the upwind heat exchanger module 12a shown in FIG. 7 is referred to as a heat exchanger module 1a and a heat exchanger module 1c. The heat exchanger module 12b on the leeward side indicated by is represented as a heat exchanger module 1b and a heat exchanger module 1d. When the heat exchanger 100A functions as an evaporator, that is, when the cooling operation is performed, the flow of the refrigerant is indicated by a solid arrow, and when the heat exchanger 100A functions as a condenser, that is, when the heat operation is performed, The flow is indicated by broken line arrows. Further, the flow direction of the air flowing into the heat exchanger 100A is indicated by an arrow 14 as in FIG.

  First, the case where the heat exchanger 100A functions as an evaporator will be described. In this case, the refrigerant flows from the inflow pipe 5 of the heat exchanger module 1a. This refrigerant conducts the flat tube 3 through the header 1A, and finally reaches the chambers 8 at both ends of the header 1A after passing through the header 1A on the opposite side. This refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1a, is guided to the U bend 13, and flows into the inflow pipe 5 of the heat exchanger module 1b. This refrigerant conducts the flat tube 3 through the header 1A, and finally reaches the room 8 at the center of the header 1A after passing through the header 1A on the opposite side. And this refrigerant | coolant flows out from the outflow pipe | tube 6 of the heat exchanger module 1b.

  Therefore, in the heat exchanger 100A, the refrigerant temperature decreases due to the refrigerant pressure loss in the direction from the inflow pipe 5 to the outflow pipe 6 (see the line (A) shown in FIG. 10). On the other hand, the temperature of the air flowing into the heat exchanger 100A decreases with respect to the flow direction 14 (see the line (a) shown in FIG. 10). Therefore, in the heat exchanger 100A, the flat tube in the plurality of flow paths 10 formed in the flat tube 3 is formed by using the header structure as shown in FIG. 3 and defining the refrigerant flow direction in the flat tube 3. The refrigerant flow direction in the cross-sectional major axis direction (column direction) of the flat tube 3 orthogonal to the three axial directions (stage direction) is parallel to the air flow direction 14. That is, since the refrigerant that has flowed through the refrigerant channel on the leeward side of the flat tube 3 can be caused to flow through the refrigerant channel on the leeward side to reciprocate the refrigerant to be parallel to the air flow, heat exchange efficiency Will improve.

  Therefore, it is possible to realize a heat exchange mode that can always ensure a constant temperature difference between the air temperature and the refrigerant temperature with respect to the air flow direction 14. This is also apparent from FIG. 10 showing the air temperature and the refrigerant temperature distribution in the heat exchanger at this time. That is, in the heat exchanger 100A, the temperature difference between the air temperature (line (A)) and the refrigerant temperature (line (A)) can always be kept substantially constant. Therefore, the heat exchanger 100A can effectively use the entire flat tube 3 for heat exchange, and can increase the heat exchange efficiency.

  Next, the case where the heat exchanger 100A functions as a condenser will be described. In this case, the refrigerant flows from the inflow pipe 5 of the heat exchanger module 1b. This refrigerant conducts the flat tube 3 through the header 1A, and finally reaches the chambers 8 at both ends of the header 1A after passing through the header 1A on the opposite side. This refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1b, is led to the U bend 13, and flows into the inflow pipe 5 of the heat exchanger module 1a. This refrigerant is conducted through the flat tube 3 via the header 1A, and finally reaches the room 8 at the center of the header 1A. And this refrigerant | coolant flows out from the outflow pipe | tube 6 of the heat exchanger module 1a. Thus, the refrigerant flow is in the opposite direction.

  Accordingly, in the heat exchanger 100A, the refrigerant temperature decreases due to the refrigerant pressure loss in the direction from the inflow pipe 5 to the outflow pipe 6 (see the line (d) shown in FIG. 11). On the other hand, the temperature of the air flowing into the heat exchanger 100A rises with respect to the flow direction 14 (see the line (c) shown in FIG. 11). Therefore, in the heat exchanger 100A, the flat tube in the plurality of flow paths 10 formed in the flat tube 3 is formed by using the header structure as shown in FIG. 3 and defining the refrigerant flow direction in the flat tube 3. The refrigerant flow direction in the cross-sectional major axis direction (column direction) of the flat tube 3 orthogonal to the three axial directions (stage direction) is opposed to the air flow direction 14. That is, the refrigerant that has flowed through the refrigerant channel on the leeward side of the flat tube 3 can be flowed through the refrigerant channel on the leeward side to reciprocate the refrigerant, and can be counterflowed with the air flow. Will improve.

  Therefore, it is possible to realize a heat exchange mode that can always ensure a constant temperature difference between the air temperature and the refrigerant temperature with respect to the air flow direction 14. This is also apparent from FIG. 11 showing the air temperature and the refrigerant temperature distribution in the heat exchanger at this time. That is, in the heat exchanger 100A, the temperature difference between the air temperature (line (A)) and the refrigerant temperature (line (A)) can always be kept substantially constant. Therefore, the heat exchanger 100A can effectively use the entire flat tube 3 for heat exchange, and can increase the heat exchange efficiency. Moreover, according to the required capacity | capacitance of the air-conditioning refrigerating apparatus 150, many heat exchanger modules 12A can be combined and heat exchange efficiency can further be improved.

  An example of how to make the heat exchanger 100A will be described. First, how to make the header 1A will be described. A square member made of aluminum is prepared, a through hole through which the flat tube 3 is inserted is provided in the square member, and a recess that becomes the room 8 is formed. These can be carried out by cutting, forging, pressing or the like. In this way, the header 1A is manufactured. Next, a necessary number of plate-like fins 4 are prepared and arranged so as to overlap. Then, the flat tube 3 is inserted into the header 1 </ b> A and is inserted into the arranged plate-like fins 4. Then, the lid 2 to which the inflow pipe 5 and the outflow pipe 6 are attached is attached to the header 1A. Thereafter, a brazing material for joining the plate-like fins 4 and the flat tube 3 is installed on the upper portion of the flat tube 3. As the brazing material, a rod wax having a circular or rectangular cross section, a paste wax, or the like can be used.

  In the case of the heat exchanger 100A configured with two or more heat exchanger modules 12A, the insertion of the flat tubes 3 into the plate fins 4 of the heat exchanger module 12A installed below, the plate fins 4 and Since it is difficult to install a brazing filler metal with the flat tube 3, one row is manufactured up to this point. Furthermore, a brazing material is installed to attach the header 1A and the lid 2, the header 1A and the flat tube 3, the lid 2 and the inflow tube 5, and the lid 2 and the outflow tube 6, respectively. In the case of the heat exchanger 100A having two or more rows, a U bend 13 is installed to overlap the heat exchanger modules 12A and communicate them. As the brazing material to be supplied to them, a rod wax, a ring wax, a paste wax or the like can be used. It is put into a vacuum furnace, Noclock furnace, and other atmospheric furnaces, and all parts are brazed at once. At this time, the flat tube 3a in which the width on one side in the short side direction shown in FIG. 5 is narrower than the width on the many side is set to the insertion direction on the narrow side, and the shape of the flat tube 3a is matched. By using the fin collar of the plate-like fin 4, insertion becomes easy, and the adhesion between the flat tube 3 a and the fin collar of the plate-like fin 4 can be further improved.

  Therefore, the thermal resistance between the plate-like fin 4 and the flat tube 3 is minimized, and the heat transfer performance is improved. Further, the sealing and pressure resistance of the header 1A and the flat tube 3, the header 1A and the lid 2, the lid 2 and the inflow tube 5, the lid 2 and the outflow tube 6, and the U bend 13 communicating between the heat exchanger module 12A are provided. improves. Further, the material of the plate fins 4 is pure aluminum, for example, A1050, the material of the flat tube 3 is pure aluminum, for example, A1050 or an Al—Mn-based aluminum alloy, for example, A3003, and the material of the header 1A is pure aluminum, for example, A1050 or Al-Mn based aluminum alloy, for example, A3003, and heat exchanger that can withstand aging by improving corrosion resistance by applying Al-Mg based aluminum alloy and zinc spraying them when more strength is required 100A can be obtained.

  Further, the heat exchanger module 12A constituting the heat exchanger 100A has a width of 0.072 m to 0.0168 m with respect to the stacking width direction of the plate-like fins 4, and thus has a height of 0.017 m and is small. Therefore, the heat capacity required for brazing can be reduced. Therefore, when brazing is performed in units of the heat exchanger module 12A, the brazing time is shortened, and it is possible to manufacture even in a small furnace. 1 to 11, the case where the heat exchanger module 12 </ b> A has a two-pass specification has been described as an example. Can be obtained. Moreover, in FIGS. 1-12, although the case where the flat tube 3 became a row was demonstrated to the example, it is not limited to this, As shown in FIG.13 and FIG.14, the flat tube 3 is made into 2 rows. The same effect can be obtained.

  FIG. 12 is a cross-sectional view showing an example of a cross-sectional configuration of the heat exchanger module 12B. Based on FIG. 12, the heat exchanger module 12B of the 3-pass specification will be described. In addition, the arrow shown in FIG. 12 represents the flow of the refrigerant. In FIG. 12, the intermediate portion of the heat exchanger module 12B is omitted. In the heat exchanger module 12B shown in FIG. 12, three refrigerant flow paths are formed by changing the arrangement of the rooms 8 inside the header 1A. That is, the heat exchanger module 12B can easily change the number of passes by changing the arrangement of the rooms 8 inside the header 1A.

  FIG. 13 is a perspective view showing an example of the overall configuration of the heat exchanger module 12C. Based on FIG. 13, the structural example of the heat exchanger module 12C is demonstrated. The heat exchanger module 12C shown in FIG. 13 is configured to reduce the number of flat tubes 3 arranged in parallel in the step direction and overlap in the row direction. That is, the length in the step direction of the heat exchanger module 12C is shortened and the length in the row direction is increased. However, the structure of the header 1A must be changed (see FIG. 14). In addition, the number of the flat tubes 3 in each row composed of the flat tubes 3 is not particularly limited, and may be, for example, about half the number of the flat tubes 3 illustrated in FIGS.

  FIG. 14 is a perspective view showing the inside of the header 1A attached to the heat exchanger module 12C shown in FIG. Based on FIG. 14, the inside of the header 1A attached to the heat exchanger module 12C shown in FIG. 13 will be described. The basic configuration is as described with reference to FIG. 2, but the rooms 8 inside the header 1 </ b> A are arranged according to the arrangement of the flat tubes 3. That is, the room 8 is also formed so as to have two steps in the row direction while shortening the length in the step direction. Even if the heat exchanger module 12C has a structure as shown in FIGS. 13 and 14, the same effects as in FIGS. 1 to 12 can be obtained.

Embodiment 2. FIG.
FIG. 15 is a perspective view illustrating a part of the overall configuration of the indoor unit 27a according to Embodiment 2 of the present invention. FIG. 16 is a perspective view showing a combination of the heat exchanger modules 12A housed in the indoor unit 27a. FIG. 17 is a schematic cross-sectional view showing a simplified vertical cross-sectional configuration of the indoor unit 27a as viewed from the side. Based on FIGS. 15-17, the case where the heat exchanger module 12A demonstrated in Embodiment 1 is combined and accommodated in the indoor unit 27a is demonstrated. In the second embodiment, the differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment are denoted by the same reference numerals and the description thereof will be omitted.

  This indoor unit 27a corresponds to the indoor unit 27 constituting the air conditioning refrigeration apparatus 150 shown in FIG. The indoor unit 27a is installed on a wall surface such as a room, and blows out air for cooling or air for air conditioning in an area such as the room. The indoor unit 27a accommodates the heat exchanger module 12A in combination. This indoor unit 27a is housed in the housing 50 in which an air inlet 51 for inhaling air and an air outlet 52 for blowing out cooling air or heating air is formed, and inhales air. The indoor blower 22 that blows out the air, the indoor blower motor 23 that drives the indoor blower 22, and the air passage from the suction port 51 to the indoor blower 22 and the air passage from the indoor blower 22 to the outlet 52 are arranged. And a heat exchanger 100A.

  The heat exchanger 100A will be described in more detail. The heat exchanger 100A is configured by combining the heat exchanger module 12A as described in the first embodiment. This heat exchanger module 12 </ b> A is housed in the housing 50 so as to surround the indoor blower 22, with two as one set. That is, four heat exchanger modules 12A (heat exchanger modules 12c to 12f) are provided on the front side of the casing 50, and two heat exchanger modules 12A (heat exchange modules are provided on the rear side of the casing 50. 12g and a heat exchanger module 12h) are provided and surround the indoor blower 22.

  In FIG. 16, the combination of the heat exchanger module 12 c (windward side) and the heat exchanger module 12 d (leeward side) disposed in the lower part on the front side of the casing 50 is the lower heat exchanger 100 a and the front side of the casing 50. A combination of the heat exchanger module 12e (windward side) and the heat exchanger module 12f (leeward side) disposed on the upper part is the upper heat exchanger 100b and the heat exchanger module 12g disposed on the back side of the housing 50. A combination of the (windward side) and the heat exchanger module 12h (leeward side) is referred to as a rear heat exchanger 100c. FIG. 16 also shows a distributor 28 that distributes refrigerant to the lower heat exchanger 100a, the upper heat exchanger 100b, and the rear heat exchanger 100c, and the lower heat exchanger 100a, the upper heat exchanger 100b, and the rear surface during cooling operation. A piping header 29 that collects and conducts the refrigerant that has flowed out of the heat exchanger 100c is illustrated.

  In FIG. 17, the refrigerant flow in the indoor unit 27a during the cooling operation is indicated by a solid arrow, the refrigerant flow in the indoor unit 27a during the heating operation is indicated by a broken arrow, and the air flow direction is indicated by a white arrow. As described above, the lower heat exchanger 100a, the upper heat exchanger 100b, and the rear heat exchanger 100c are disposed so as to surround the indoor blower 22, and the air sucked into the indoor blower 22 is lower heat exchanger 100a. The upper heat exchanger 100b and the rear heat exchanger 100c are substantially uniform.

  During the heating operation, the gas refrigerant from the pipe header 29 flows into each of the heat exchanger modules 12A (the heat exchanger module 12d, the heat exchanger module 12f, and the heat exchanger module 12h) installed on the leeward side. The air supplied from the blower 22 is heat-exchanged and condensed, and flows out from each of the heat exchanger modules 12A (the heat exchanger module 12c, the heat exchanger module 12e, and the heat exchanger module 12g) installed on the windward side. Are joined by the distributor 28. At this time, the refrigerant flows from the heat exchanger module 12A installed on the leeward side to the heat exchanger module 12A installed on the leeward side, each facing the air flow direction (arrows 14a, 14b, and 14c). Therefore, the temperature difference between the air temperature and the refrigerant temperature can always be secured with respect to the air flow direction.

  During the cooling operation, the refrigerant flowing into the inlet of the distributor 28 is a two-phase flow in which liquid and gas are mixed. Therefore, if the refrigerant flows into each heat exchanger module without any contrivance, it flows into each heat exchanger module 12A in a state where the ratio of the liquid and the gas is not uniform. Therefore, in the indoor unit 27a, a distributor 28 is provided on the upstream side before the refrigerant flows into each heat exchanger module 12A so that the refrigerant in the two-phase flow state is evenly distributed. Further, the refrigerant distributed by the distributor 28 flows into the heat exchanger module 12A on the windward side and flows to the pipe header 29, but in order to make the pressure loss in the pipe from the distributor 28 to the pipe header 29 uniform. The lengths of the inflow pipes 5 connected to the distributor 28 and the upwind heat exchanger module 12A are the same.

  The refrigerant branched by the distributor 28 flows into each of the heat exchanger modules 12A installed on the windward side, and flows into each of the heat exchanger modules 12A installed on the leeward side via the U bend 13. . This refrigerant flows out from each of the heat exchanger modules 12 </ b> A installed on the leeward side, and merges at the pipe header 29. At this time, the refrigerant flows from the heat exchanger module 12A installed on the leeward side to the heat exchanger module 12A installed on the leeward side, and each of them is parallel to the air flow direction. A temperature difference between the air temperature and the refrigerant temperature can always be secured.

  In addition, each heat exchanger module 12A which comprises the lower heat exchanger 100a, the upper heat exchanger 100b, and the back surface heat exchanger 100c has the horizontal width with respect to the stacking width direction of the plate-like fin 4 0.072 m- Since it is 0.0168 m, the height is 0.017 m, and since it is small, it can be easily combined and installed according to the surroundings of the indoor blower 22 as shown in FIG. 17, and the indoor unit 27a is compact. Can be realized. Therefore, when producing indoor units with different air-conditioning capabilities, it is only necessary to change the number of installed heat exchanger modules 12A accommodated therein, and there is no need to make a new heat exchanger corresponding to the indoor unit. Can be reduced in labor and cost.

  On the other hand, due to the structure of the indoor unit 27a, the air flow may become non-uniform, and the speed of the air flowing through each heat exchanger module 12A may become non-uniform for each heat exchanger module 12A. In that case, the pressure loss and heat transfer area of the air flowing through the heat exchanger module 12A are adjusted by changing the step pitch of the flat tubes 3 of each heat exchanger module 12A or the fin pitch in the laminating direction of the plate-like fins 4. The heat transfer performance of the heat exchanger module 12A can be adjusted. Therefore, several types of heat exchanger modules 12A having different specifications of the flat tube 3 and the fin pitch in the stacking direction of the plate-like fins 4 are prepared, and the heat exchanger module 12A is installed so as to be suitable for the indoor unit 27a. In this case, labor and cost required for manufacturing can be further reduced.

  Further, when the step pitch of the flat tube 3 is narrowed, the width in the step direction of the heat exchanger module 12A is inevitably reduced, so that the step pitch of the flat tube 3 and the fin pitch in the stacking direction of the plate fins 4 are different. By combining the heat exchanger module 12A, the indoor unit 27a can be made more compact. Further, when the fin pitch in the laminating direction of the plate fins 4 is reduced, the number of the plate fins 4 increases and the heat transfer area increases if the length of the heat exchanger module 12A in the longitudinal direction is the same. Since the heat transfer performance is improved, the air conditioning capacity of the indoor unit 27a can be increased by combining such a heat exchanger module 12A.

  Note that the heat exchanger 100A (the lower heat exchanger 100a, the upper heat exchanger 100b, and the rear heat exchanger 100c) housed in the indoor unit 27a described in the second embodiment is the heat exchanger described in the first embodiment. Since it is configured by the combination of the modules 12A, it is possible to deal with the indoor unit 27a having various specifications simply by preparing several types of heat exchanger modules 12A having different specifications and making them common. . Moreover, it is not necessary to produce a heat exchanger corresponding to each of the air conditioning capabilities of the indoor unit 27a, and it is possible to reduce labor and cost required for manufacturing. Furthermore, the same effect can be obtained by using the heat exchanger module 12B and the heat exchanger module 12C.

Embodiment 3.
FIG. 18 is a perspective view showing an example of the overall configuration of a heat exchanger module 12D according to Embodiment 3 of the present invention. FIG. 19 is a perspective view showing the inside of the header 1A so as to be visible. Based on FIG.18 and FIG.19, the structural example of 12 A of heat exchanger modules is demonstrated. The heat exchanger module 12D is a minimum unit constituting the heat exchanger, similar to the heat exchanger modules 12A to 12C according to the first embodiment. In the third embodiment, the difference from the first embodiment and the second embodiment described above will be mainly described, and the same parts as those in the first embodiment and the second embodiment are denoted by the same reference numerals. Therefore, the description will be omitted.

  The heat exchanger module 12D according to the third embodiment is different in the structure of the header 1B from the header 1A of the heat exchanger module 12A to the heat exchanger module 12C according to the first embodiment. As shown in FIG. 18, a plurality of inflow pipes 5 and outflow pipes 6 are attached to the header 1B. By doing so, a plurality of refrigerant flow paths, that is, a plurality of paths are formed in the heat exchanger module 12B. Moreover, the point which forms the protrusion part 30 inside the header 1B is also different. The protrusion 30 has a function of making the ratio of the refrigerant gas and liquid flowing in from the inflow pipe 5 substantially equal. Further, the protrusion 30 is formed so as to protrude from the end of the flat tube 3 connected to the chamber 8 in which the protrusion 30 is formed.

  FIG. 20 is a cross-sectional view illustrating an example of a cross-sectional configuration of the heat exchanger module 12D. Based on FIG. 20, the flow of the refrigerant in the heat exchanger module 12D will be described. In addition, the arrow shown in FIG. 20 represents the flow of the refrigerant. In FIG. 20, the intermediate portion of the heat exchanger module 12D is omitted. As shown in FIG. 20, the inflow pipe 5 is provided at a position corresponding to an intermediate portion between the two flat tubes 3, and a protrusion 30 is formed in a room 8 where the inflow pipe 5 is provided. Yes. This protrusion 30 protrudes on the opposite side with respect to the refrigerant inflow direction. That is, the protrusion 30 is provided between the flat tube 4 and the flat tube 4 in the room 8 to which the two flat tubes 3 are connected, and has a collision portion larger than the flow path cross-sectional area of the inflow tube 5. The interval between the inflow pipe 5 provided on the lid 2 and the protrusion 30 is set to 0.001 m to 0.003 m.

  As shown in FIG. 20, the refrigerant that has flowed in from the inflow pipe 5 collides with the protrusion 30 formed in the chamber 8 inside the header 1B and is distributed in two directions (up and down in the drawing). The pipe 3 is conducted, reaches each room 8 inside the header 1B ′ on the opposite side (another header 1B to which the inflow pipe 5 and the outflow pipe 6 are not connected), and then moves to the adjacent flat pipe 3 Then, it flows again through each flat tube 3, reaches each room 8 inside the header 1 </ b> B, and flows out from the outflow tube 6. That is, in the heat exchanger module 12D, when the refrigerant is conducted through each flat tube 3, heat is exchanged with air through the plate-like fins 4 joined to the flat tube 3.

  In FIG. 20, in the heat exchanger module 12D, the refrigerant flows in three passes, is branched into two in the header 1B, and flows out in six passes. The specifications of the flat tube 3 and the plate-like fin 4 used in the heat exchanger module 12D of the third embodiment are the same as those of the first embodiment. Moreover, in FIGS. 18-20, although the case where the number of the flat tubes 3 is set to 12 is shown as an example, it sets between 8-16 as needed similarly to Embodiment 1. Can do. In this way, the heat exchanger module 12D which is the minimum unit constituting the heat exchanger is configured. In actual use, a heat exchanger is often configured by combining a large number of modules.

  Here, the function of the protrusion 30 will be described. FIG. 21 is a schematic view showing one of the rooms 8 in which the protruding portion 30 of the header 1B to which the two flat tubes 3 are connected is not installed. FIG. 22 is a schematic view showing one of the rooms 8 in which the protrusions 30 of the header 1B to which two flat tubes 3 are connected are installed. FIG. 23 is a schematic view showing a state in which the concave portion 33 is formed in the protrusion 30. Based on FIGS. 21-23, the mechanism to change the flow of a refrigerant | coolant by the presence or absence of the projection part 30 is demonstrated. In addition, in FIGS. 21-23, the flow of the refrigerant | coolant is represented by the arrow. Further, the refrigerant in the room 8 is represented as a gas refrigerant 31, a liquid refrigerant 32, and a uniform refrigerant 34.

  When the heat exchanger is used as an evaporator, the refrigerant flowing from the inflow pipe 5 is a two-phase flow in which liquid and gas are mixed. When the header 1B is installed vertically in the step direction, if the refrigerant is distributed to the two flat tubes 3, the liquid refrigerant 32 and the gas refrigerant 31 are separated by gravity in the structure of FIG. That is, the liquid refrigerant 32 having a large liquid ratio flows into the flat tube 3 on the lower side in the gravity direction (lower side in the drawing), and the ratio of the gas is higher in the flat tube 3 on the upper side in the gravity direction (upper side in the drawing). The gas refrigerant 31 will flow in. As a result, the heat exchange amount in the heat exchanger module 12D becomes non-uniform.

  Therefore, as shown in FIG. 22, the refrigerant flowing from the inflow pipe 5 is once collided with the protrusion 30, and the gas refrigerant and the liquid refrigerant in the room 8 are mixed with the momentum to thereby cause gas to flow into the upper and lower flat tubes 3. The uniform refrigerant 34 having a substantially equal ratio between the liquid and the liquid can be introduced. As a result, the non-uniformity of the heat exchange amount in the heat exchanger module 12D is improved, and the heat exchange amount can be made substantially uniform. Furthermore, as shown in FIG. 23, by forming the concave portion 33 having a predetermined depth in the protruding portion 30, the liquid and the gas can be mixed more easily. In addition, the shape of the recessed part 33 is not specifically limited, For example, what is necessary is just to form cross-sectional shape as circular shape or polygonal shape.

  FIG. 24 is a perspective view showing a heat exchanger 100B configured by stacking two heat exchanger modules 12D in the air flow direction. Based on FIG. 24, a heat exchanger 100B configured by stacking two heat exchanger modules 12D in the air flow direction will be described. That is, FIG. 24 shows a state in which two heat exchanger modules 12D described in FIGS. 18 to 23 are overlapped in the air flow direction and function as one heat exchanger 100B. is there. In FIG. 24, the air flow is indicated by an arrow 14. Further, the heat exchanger module 12D in which the protrusion 30 is not formed will be referred to as a heat exchanger module 12D '.

  As shown in FIG. 24, in the heat exchanger 100B, the heat exchanger module 12D in which the protrusions 30 are formed is disposed on the leeward side, the heat exchanger module 12D ′ is disposed on the leeward side, and they are U-bended. 13 is connected. Specifically, the heat exchanger 100B connects the six outflow pipes 6 of the heat exchanger module 12D and the six inflow pipes 5 of the heat exchanger module 12D ′ with U-bends 13, respectively. It is comprised so that a flow path may be formed. The flow of the refrigerant in the heat exchanger 100B configured as described above will be described with reference to FIG. In the following description, it is assumed that the header 1B on which the protrusion 30 is not formed is referred to as a header 1B '.

  FIG. 25 is a perspective view showing the internal configuration of the heat exchanger 100B in the header major axis direction (stage direction). Based on FIG. 25, the flow of the refrigerant in the heat exchanger 100B will be described. 25 (a) is a perspective view seen from the side where the inflow pipe 5 and the outflow pipe 6 are connected, and FIG. 25 (b) is from the side where the inflow pipe 5 and the outflow pipe 6 are not connected. Each state seen through is shown. For convenience, the leeward heat exchanger module 12D shown in FIG. 24 is referred to as a heat exchanger module 1a ′ and a heat exchanger module 1c ′, and the leeward heat exchanger module 12D ′ shown in FIG. Are represented as heat exchanger module 1b ′ and heat exchanger module 1d ′. The refrigerant flow is indicated by solid arrows and broken line arrows as in FIG. 9, and the air flow direction is indicated by arrows 14 as in FIG.

  First, the case where the heat exchanger 100B functions as an evaporator will be described. In this case, the refrigerant flows from the inflow pipe 5 of the heat exchanger module 1a '. This refrigerant collides with the protrusions 30 of the header 1B, is distributed, conducts the flat tube 3 connected up and down across the protrusions 30, passes through the header 1B 'on the opposite side, and then adjoins each other. It reaches the room 8 of the header 1B. This refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1a ', is guided to the U bend 13, and flows into the inflow pipe 5 of the heat exchanger module 1b'. This refrigerant passes through the flat tube 3 through the header 1B ', passes through the header 1B' on the opposite side, and then reaches the chamber 8 of each adjacent header 1B '. Then, this refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1b '.

  When the heat exchanger 100B is used as an evaporator, the uniform refrigerant uniformly flows through all the flat tubes 3 due to the refrigerant mixing action by the protrusions 30 formed inside the header 1B. As a result, it is possible to reduce performance degradation due to non-uniform refrigerant. In addition, the case where there are three refrigerant flow paths, that is, three paths, is shown as an example in the heat exchanger 100B. The refrigerant flowing into the inflow pipe 5 of the heat exchanger module 1a ′ is distributed after being distributed by a distributor (not shown) (for example, the distributor 28 described in the second embodiment). . In addition, the refrigerant that has flowed out of the outflow pipe 6 of the heat exchanger module 1b 'is joined at a pipe header (not shown) (for example, the pipe header 29 described in the second embodiment).

  Next, the case where the heat exchanger 100B functions as a condenser will be described. In this case, the refrigerant flows from the inflow pipe 5 of the heat exchanger module 1b '. This refrigerant passes through the flat tube 3 connected to each room 8 of the header 1B ', passes through the header 1B' on the opposite side, and reaches the room 8 of the adjacent header 1B '. This refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1b ', is guided to the U bend 13, and flows into the inflow pipe 5 of the heat exchanger module 1a'. The refrigerant passes through the flat tube 3 through the header 1B, passes through the header 1B 'on the opposite side, and reaches the room 8 of the header 1B. Then, this refrigerant flows out from the outflow pipe 6 of the heat exchanger module 1a '.

  When the heat exchanger 100A is used as a condenser, the refrigerant flows in the opposite direction when functioning as an evaporator. In the chamber 8 of the header 1B 'to which the inflow pipe 5 into which the refrigerant flows is connected, no projection 30 is distributed to the two flat tubes 3 connected to the room 8. However, since the refrigerant flowing into the heat exchanger module 1b ′ is only the gas refrigerant, it is evenly distributed in each room 8 of the header 1B ′ without considering the separation between the liquid refrigerant and the gas refrigerant. become.

  In order to increase the air conditioning capability of the heat exchanger, it is necessary to increase the amount of air flowing into the heat exchanger or the flow rate of the refrigerant conducted to the heat exchanger tube of the heat exchanger. When the flow rate of the refrigerant that is conducted to the heat transfer tube is increased, the flow rate of the refrigerant that is conducted through the heat transfer tube must be increased, and the pressure loss is also increased. Therefore, in order to secure the refrigerant flow rate, it is necessary to use a compressor having a large compression force. Therefore, it is necessary to suppress the pressure loss by increasing the number of passes in the heat exchanger. However, when the number of paths in the heat exchanger increases, the distributor must be increased in accordance with the increase, and the number of pipes connected to the distributor and forming the refrigerant flow path also increases. The indoor units that house them must secure their occupied space and cannot meet the demand for miniaturization.

  Therefore, by using the heat exchanger 100B configured by combining the heat exchanger module 12D according to the third embodiment, the number of distribution can be halved outside the heat exchanger 100B, and the occupied space can be reduced. Compactness can be realized. Therefore, in the heat exchanger 100B, a plurality of paths are formed, and the header 1B having the protrusions 30 is provided so that the refrigerant having an equal proportion of the liquid refrigerant and the gas refrigerant is conducted to the flat tube 3. Therefore, the heat exchange efficiency can be further improved while having the same effect as the heat exchanger 100A according to the first embodiment. Moreover, by accommodating this heat exchanger 100B in the indoor unit 27a according to Embodiment 2, the heat exchange efficiency can be improved, and the indoor unit 27a can be made more compact.

Embodiment 4.
FIG. 26 is a schematic cross-sectional view showing a simplified vertical cross-sectional configuration of an indoor unit 27b according to Embodiment 4 of the present invention as viewed from the side. Based on FIG. 26, the indoor unit 27b which accommodated combining the assist heat exchanger 46 is demonstrated. The assist heat exchanger 46 is a plate fin and tube type heat exchanger that uses a circular tube as a heat transfer tube. In the fourth embodiment, the difference from the above-described first to third embodiments will be mainly described, and the same parts as those in the first to third embodiments are denoted by the same reference numerals. Therefore, the description will be omitted.

  This indoor unit 27b corresponds to the indoor unit 27 constituting the air conditioning refrigeration apparatus 150 shown in FIG. The indoor unit 27b is installed on a wall surface such as a room, and blows out air for cooling and air for heating to an air-conditioning target area such as the room. The indoor unit 27b accommodates the heat exchanger 100B according to the third embodiment and the assist heat exchanger 46 in combination. Other configurations of the indoor unit 27b are the same as those of the indoor unit 27a according to the embodiment. In FIG. 26, the refrigerant flow in the indoor unit 27b during the reheat dehumidifying operation is indicated by a solid line arrow, and the air flow direction is indicated by a white arrow.

  The heat exchanger 100B is configured by combining the heat exchanger module 12D as described in the third embodiment. This heat exchanger module 12 </ b> D is housed in the housing 50 so as to surround the indoor blower 22, with two as one set. That is, four heat exchanger modules 12D (heat exchanger module 12c ′ to heat exchanger module 12f ′) are provided on the front side of the casing 50, and two heat exchanger modules 12D ( A heat exchanger module 12g ′ and a heat exchanger module 12h ′) are provided and surround the indoor blower 22.

  In FIG. 26, the combination of the heat exchanger module 12c ′ (windward side) and the heat exchanger module 12d ′ (leeward side) disposed in the lower part on the front side of the casing 50 is the lower heat exchanger 100a ′ and the casing 50. A combination of a heat exchanger module 12e ′ (windward side) and a heat exchanger module 12f ′ (leeward side) disposed on the upper front side of the upper heat exchanger 100b ′ is disposed on the rear side of the housing 50. A combination of the heat exchanger module 12g ′ (windward side) and the heat exchanger module 12h ′ (leeward side) is referred to as a rear heat exchanger 100c ′. FIG. 26 also shows three distributors (a distributor 28a, a distributor 28b, and a distributor 28c) that distribute refrigerant to the lower heat exchanger 100a, the upper heat exchanger 100b, and the rear heat exchanger 100c, and a dehumidification valve. 45 is also illustrated.

  The assist heat exchanger 46 includes a lower assist heat exchanger 46 a disposed in the lower front side of the housing 50, an upper assist heat exchanger 46 b disposed in the upper front side of the housing 50, and the housing 50. And a back assist heat exchanger 46c disposed on the back side. The lower assist heat exchanger 46a is juxtaposed with the lower heat exchanger 100a ′, the upper assist heat exchanger 46b is juxtaposed with the upper heat exchanger 100b ′, and the rear assist heat exchanger 46c ′ is rear heat. It is juxtaposed with the exchanger 100c. That is, each assist heat exchanger is arranged on the windward side with respect to each heat exchanger.

  A path pattern in the indoor unit 27b will be described. In this indoor unit 27b, each heat exchanger is divided during a dehumidifying operation for reducing the humidity of the room in which the indoor unit 27b is installed, and a path pattern is set such that a part functions as a condenser and a part functions as an evaporator. Thus, the indoor air taken into the indoor unit 27b can be lowered below the dew point by the evaporator to reduce the humidity and be mixed with the air that has passed through the condenser. By adopting such a path pattern, the indoor unit 27b can perform dehumidification without lowering the room temperature. Such an operation is referred to as a reheat dehumidification operation.

  The refrigerant flow during the reheat dehumidifying operation performed by the indoor unit 27b will be described in detail. Refrigerant from an outdoor unit (not shown) flows from the suction pipe 47 connected to the back assist heat exchanger 46c into the back assist heat exchanger 46c of the indoor unit 27b. Thereafter, the refrigerant flowing out from the back assist heat exchanger 46c flows into the distributor 28c after passing through the lower assist heat exchanger 46a and the upper assist heat exchanger 46b. The refrigerant flowing in from the suction pipe 47 is condensed in the back assist heat exchanger 46c, the lower assist heat exchanger 46a, and the upper assist heat exchanger 46b, enters a distributor 28c in a two-phase state, and this distributor 28c. And then flows into the rear heat exchanger 100c ′.

  That is, the refrigerant flowing into the distributor 28c is branched into three at the distributor 28c and flows into the heat exchanger module 12g 'constituting the rear heat exchanger 100c'. The refrigerant flowing into the heat exchanger module 12g ′ is further divided into two by the distributor structure provided inside the header 1B of the heat exchanger module 12g ′, and is conducted through the flat tube 3 in the process. And the flat tube 3 of the heat exchanger module 12h ′ is conducted, where it exchanges heat with air again and flows out from the rear heat exchanger 100c ′. The refrigerant that has flowed out of the rear heat exchanger 100c 'is joined by the distributor 28b. The heat exchanger through which the refrigerant has passed so far acts as a condenser and acts to raise the temperature of the air.

  The refrigerant combined in the distributor 28b flows out of the distributor 28b and then flows into the dehumidifying valve 45. The dehumidifying valve 45 includes a throttle mechanism, a valve, and a circuit that bypasses the throttle mechanism, and can switch between a case where the throttle mechanism is operated by operating the valve and a case where the throttle mechanism is bypassed. It can be configured. During the reheat dehumidifying operation, the refrigerant flowing into the dehumidifying valve 45 is throttled and depressurized by the dehumidifying valve 45. The refrigerant decompressed by the dehumidifying valve 45 then flows into the distributor 28a. The refrigerant flowing into the distributor 28a is divided into six by the distributor 28a, and flows into the heat exchanger module 12c 'of the lower heat exchanger 100a' and the heat exchanger module 12e 'of the upper heat exchanger 100b'.

  The refrigerant flowing into the heat exchanger module 12c ′ and the heat exchanger module 12e ′ is further divided into two by the distribution mechanism provided inside each header 1B, and the flat tube 3 is conducted. Heat exchange with air is conducted through the flat tubes 3 of the heat exchanger module 12d ′ and the heat exchanger module 12f ′, where heat is exchanged again with air, and flows out from the lower heat exchanger 100a ′ and the upper heat exchanger 100b ′. To do. Since the evaporation temperature of the refrigerant in the lower heat exchanger 100a 'and the upper heat exchanger 100b' is set to be equal to or lower than the dew point of the air, moisture in the air can be taken and the humidity can be lowered.

  The refrigerant that has flowed out of the lower heat exchanger 100a ′ and the upper heat exchanger 100b ′ is then merged in the pipe header 29, flows out of the indoor unit 27b through the outflow pipe 48, and returns to the outdoor unit. . Therefore, the assist heat exchanger 46, the heat exchanger module 12g ′, and the heat exchanger module 12h warm the air as a condenser, and the heat exchanger module 12c ′, the heat exchanger module 12d ′, the heat exchanger module 12e ′, and The heat exchanger module 12f ′ can mix the warmed air and the cooled air by taking the humidity of the air and cooling the air, and can perform a dehumidifying operation without lowering the temperature of the air.

  During normal cooling operation, the throttle mechanism constituting the dehumidifying valve 45 may be used so as to be bypassed. Further, the flow of the refrigerant during the heating operation is opposite to the arrow shown in FIG. Also at this time, the throttle mechanism constituting the dehumidifying valve 45 may be used so as to be bypassed. Further, although the two-phase refrigerant flows into the heat exchanger module 12g ′ and the heat exchanger module 12h ′ in any of the reheat dehumidifying operation, the cooling operation, and the heating operation, the refrigerant is distributed. The devices 28b and 28c can be evenly distributed, and the performance does not deteriorate.

  As described above, even when a part of the heat exchanger is used as a condenser and a part as an evaporator at the same time in the same indoor unit 27b, the heat exchanger is separated in units of modules. It is possible to set the condenser and the evaporator. Further, by using a distribution mechanism in the header such as the heat exchanger module 12D according to the third embodiment, the refrigerant can be evenly distributed without increasing the number of distributor pipes of the distributor so much. No performance degradation will occur. Furthermore, by using the heat exchanger module 12D according to the embodiment, all the effects of the first to third embodiments are obtained.

  FIG. 27 is a schematic cross-sectional view showing a simplified vertical cross-sectional configuration of the indoor unit 27b 'as viewed from the side for comparison with the internal configuration of the indoor unit 27a. The effect of the indoor unit 27b according to Embodiment 4 will be described based on FIG. In FIG. 27, an indoor unit 27b ′ that houses a heat exchanger configured by combining heat exchanger modules that do not use a distribution mechanism (protrusion 30 described in the third embodiment) in the header is taken as an example. Show. The other configuration and path pattern of the indoor unit 27b 'are the same as those of the indoor unit 27b.

  As apparent from FIGS. 26 and 27, the indoor unit 27b according to the fourth embodiment is connected to a distributor (distributor 28a, distributor 28b, and distributor 28c) as compared with the indoor unit 27b ′. The number of pipes is half. That is, the indoor unit 27b can reduce the number of connection of the distributor pipes by providing a distribution mechanism inside the header, and can omit the space. Therefore, the indoor unit 27b can be more effectively downsized.

Embodiment 5 FIG.
FIG. 28 is a perspective view showing an example of the overall configuration of a heat exchanger module 12E according to Embodiment 5 of the present invention. Based on FIG. 28, the structural example of the heat exchanger module 12E is demonstrated. This heat exchanger module 12E is the minimum unit constituting the heat exchanger, similar to the heat exchanger module 12A to the heat exchanger module 12C according to the first embodiment and the heat exchanger module 12D according to the third embodiment. Is. This heat exchanger module 12E is different in header structure from the header 1A of the heat exchanger module 12A to the heat exchanger module 12C according to the first embodiment and the header 1B of the heat exchanger module 12D according to the fourth embodiment. is doing.

  As shown in FIG. 28, two types of headers (header 35 and header 37) are attached to the heat exchanger module 12E. The header 35 has a space inside, the two flat tubes 3 are connected, and the lid 36 is joined. The header 37 has a space inside, and a flat tube 3 is connected to the header 37, and a lid 38 to which the inflow pipe 5 and the outflow pipe 6 are connected is joined. In addition, about the plate-like fin 4, the same thing as Embodiment 1- Embodiment 4 is used.

  This heat exchanger module 12E is characterized by a structure in which the header 1A according to the first and second embodiments is divided for each room 8, and the heat exchanger module 12A according to the first and second embodiments. -It has the same function and effect as the heat exchanger module 12C. Moreover, if the protrusion part 30 is formed in the chamber 8 corresponding between the two flat tubes 3 in the header 35, it has the same function and effect as the heat exchanger module 12D according to the third embodiment. Furthermore, since the header is divided | segmented, the heat exchanger module 12E has the advantage that the path pattern which flows a refrigerant | coolant to a heat exchanger can be freely selected with the combination.

  It should be noted that the contents of Embodiments 1 to 5 described above can be combined as appropriate. Therefore, an optimum heat exchanger can be configured according to conditions such as necessary air conditioning capacity, installation space of the heat exchanger, necessity of reheat dehumidification operation, and the like. Moreover, the heat exchanger which considered conditions, such as a place and the objective in which the indoor unit which accommodates the heat exchanger combined in this way is installed, can be comprised. Therefore, the air-conditioning refrigeration apparatus 150 equipped with such a heat exchanger and an indoor unit is excellent in heat exchange efficiency, satisfies the demand for downsizing, and reduces labor and cost required for manufacturing.

  Moreover, although the refrigerant | coolant which circulates through the refrigerating cycle of the air-conditioning refrigerating apparatus 150 which concerns on Embodiment 1-Embodiment 5 is not specifically limited, methane, ethane, propane, butane, isobutane, propylene, isopropylene, etc. A single HC refrigerant or a mixed refrigerant containing HC may be used. This is because the global warming potential can be made extremely small by using such a refrigerant. Propane has a characteristic that the temperature drop degree with respect to the refrigerant pressure loss is larger than that of the conventional refrigerant R22. This is because, for example, when the refrigerant saturation temperature changes from 10 ° C. to 0 ° C., R22 has a pressure change of 0.183 MPa, while propane has a pressure change of 0.162 MPa.

  Further, isobutane also has a characteristic that the degree of temperature drop with respect to refrigerant pressure loss is larger than that of the conventional refrigerant R134a. This is because, for example, when the refrigerant saturation temperature changes from −20 ° C. to −30 ° C., R134a has a pressure change of 0.0483 MPa, whereas isobutane has a pressure change of 0.0258 MPa. For this reason, when these refrigerants are used in the air conditioning refrigeration apparatus 150, it is necessary to make the absolute value of the refrigerant pressure loss smaller than that of the conventional refrigerant.

  The heat exchanger according to the above embodiment is provided with a plurality of flow paths separated by the partition wall 9 in the flat tube 3 and increases the number of the flat tubes 3 connected to one header, thereby increasing the The heat exchanger module of the passage can be configured, and the absolute value of the refrigerant pressure loss can be very easily reduced. Alternatively, the absolute value of the medium pressure loss can be reduced by increasing the number of passes. Even if the number of passes increases, if a branch mechanism is provided inside the header as in the third embodiment, it is possible to suppress an increase in the number of pipes connected to a distributor or the like. Therefore, even when a single HC refrigerant or a mixed refrigerant containing HC is used, the highly efficient air-conditioning refrigeration apparatus 150 can be provided.

  Further, since these refrigerants are flammable, it is desirable that the amount of refrigerant is as small as possible for safety. If the heat exchanger comprised with the flat tube 3 is used, since the capacity | capacitance of a pipe is small, there exists an effect which can reduce the refrigerant | coolant amount. If the pipe capacity is small, the pressure loss tends to increase, but the absolute value can be reduced by increasing the number of passes. Even if the number of passes increases, if a branch mechanism is provided inside the header as in the third embodiment, it is possible to suppress an increase in the number of pipes connected to a distributor or the like.

  Further, as a refrigerant for circulating the refrigeration cycle of the air-conditioning refrigeration apparatus 150 according to Embodiments 1 to 5, a single refrigerant of R32 or a mixed refrigerant containing R32 (R407A, R407B, R407C, R407D, R407E, R410A, By using R410B, etc., the global warming potential can be made very small. When using a single R32, the number of passes can be reduced because the pressure loss is reduced. If a branching mechanism is provided inside the header as in the third embodiment, piping connected to the outside becomes simple, and downsizing and cost reduction can be realized.

  Furthermore, by using a single ammonia or a mixed refrigerant containing ammonia as a refrigerant for circulating the refrigeration cycle of the air-conditioning refrigeration apparatus 150 according to the first to fifth embodiments, the global warming potential is greatly reduced. Can be small. However, ammonia will corrode the copper heat transfer tubes used in conventional circular tube plate fin type heat exchangers. Therefore, the heat exchanger according to the first to fifth embodiments is configured such that the plate-like fin material 4, the flat tube 3, and the header are made of aluminum having corrosion resistance. Also, by brazing them in an integrated furnace, it is possible to provide a heat exchanger that can ensure corrosion resistance and prevent refrigerant leakage due to poor brazing, and ensure high efficiency and sufficient safety. .

  The compressor may be configured in any form, for example, a reciprocating compressor (single cylinder, multiple cylinders), a rotary compressor (single cylinder, multiple cylinders), a scroll compressor, a linear compressor, or the like. Further, when an electric motor that rotates the compression portion is built in the shell of the compressor, the pressure structure in the shell may be either a high-pressure shell or a low-pressure shell. In the high-pressure shell method, the refrigerant exiting the compression cylinder cools the motor and is heated and discharged from the compressor, so the discharge temperature becomes high. On the other hand, in the low-pressure shell method, the refrigerant flowing into the shell is sucked into the compression cylinder after being heated by cooling the motor, so that the suction temperature becomes high. However, since the refrigerant flowing out from the compression cylinder is directly discharged out of the compressor, the discharge temperature is lowered.

  Depending on the refrigerant used, the discharge temperature is increased or decreased. In particular, the R32 refrigerant has a higher discharge temperature than the R410A refrigerant, and the propane has a lower discharge temperature than the R410A refrigerant. It is sufficient to determine whether to use a high pressure shell or a low pressure shell in consideration. In general, the high-pressure shell has a larger amount of refrigerant dissolved in the compressor refrigeration oil than the low-pressure shell. Therefore, it is better to select the low-pressure shell method when it is desired to reduce the refrigerant charging amount. However, if the refrigeration oil that is difficult to dissolve the refrigerant is used, the refrigerant amount can be reduced even in the high-pressure shell.

It is a perspective view which shows an example of the whole structure of the heat exchanger module which concerns on Embodiment 1. FIG. It is a perspective view which makes the inside of a header visible and shows. It is sectional drawing which shows an example of the cross-sectional structure of a heat exchanger module. It is a schematic sectional drawing which shows an example of the longitudinal cross-section structure of the flat tube which is a heat exchanger tube. It is a schematic sectional drawing which shows an example of the longitudinal cross-section structure of the flat tube of another shape. It is explanatory drawing of the plate-shaped fin which showed a part of plate-shaped fin. It is a perspective view which shows the heat exchanger which overlapped and comprised the two heat exchanger modules in the air flow direction. It is a schematic block diagram which shows the refrigerant circuit of the heat pump type air-conditioning refrigerating device which uses a heat exchanger. It is a perspective view which shows the internal structure of the header major axis direction (stage direction) of a heat exchanger. It is a graph which shows distribution of the air temperature in case a heat exchanger functions as an evaporator, and the refrigerant | coolant temperature in a heat exchanger. It is a graph which shows distribution of the air temperature in case a heat exchanger functions as a condenser, and the refrigerant | coolant temperature in a heat exchanger. It is sectional drawing which shows an example of the cross-sectional structure of a heat exchanger module. It is a perspective view which shows an example of the whole structure of a heat exchanger module. It is a perspective view which makes visible the inside of the header attached to the heat exchanger module shown in FIG. It is a perspective view which shows a part of whole structure of the indoor unit which concerns on Embodiment 2 through. It is a perspective view which shows the combination of the heat exchanger module accommodated in an indoor unit. It is a schematic sectional drawing which simplifies and shows the longitudinal cross-sectional structure which looked at the indoor unit from the side. It is a perspective view which shows an example of the whole structure of the heat exchanger module which concerns on Embodiment 3. FIG. It is a perspective view which makes the inside of a header visible and shows. It is sectional drawing which shows an example of the cross-sectional structure of a heat exchanger module. It is the schematic which shows one of the rooms where the protrusion part of the header to which two flat tubes were connected is not installed. It is the schematic which shows one of the rooms in which the protrusion part of the header to which two flat tubes were connected was installed. It is the schematic which shows the state which formed the recessed part in the projection part. It is a perspective view which shows the heat exchanger which overlapped and comprised the two heat exchanger modules in the air flow direction. It is a perspective view which shows the internal structure of the header major axis direction (stage direction) of a heat exchanger. It is a schematic sectional drawing which simplifies and shows the longitudinal cross-sectional structure which looked at the indoor unit which concerns on Embodiment 4 from the side surface. It is a schematic sectional drawing which simplifies and shows the longitudinal cross-sectional structure which looked at the indoor unit for comparing with the internal structure of an indoor unit from the side. It is a perspective view which shows an example of the whole structure of the heat exchanger module which concerns on Embodiment 5. FIG.

Explanation of symbols

  1A header, 1A 'header, 1B header, 1B' header, 1a heat exchanger module, 1a 'heat exchanger module, 1b heat exchanger module, 1b' heat exchanger module, 1c heat exchanger module, 1c 'heat exchange Module, 1d heat exchanger module, 1d 'heat exchanger module, 2 lid, 3 flat tube, 3a flat tube, 4 plate fin, 4a plate fin, 4b plate fin, 5 inflow tube, 6 outflow tube, 8 rooms, 9 partitions, 10 channels, 11 cut and raised, 12A heat exchanger module, 12B heat exchanger module, 12C heat exchanger module, 12D heat exchanger module, 12D 'heat exchanger module, 12E heat exchanger module 12a heat exchanger module, 12a 'heat exchanger module, 12b heat exchange Module, 12b ′ heat exchanger module, 12c heat exchanger module, 12c ′ heat exchanger module, 12d heat exchanger module, 12d ′ heat exchanger module, 12e heat exchanger module, 12e ′ heat exchanger module, 12f heat Exchanger module, 12f ′ heat exchanger module, 12g heat exchanger module, 12g ′ heat exchanger module, 12h heat exchanger module, 12h ′ heat exchanger module, 13 U bend, 14 arrow, 14a arrow, 14b arrow, 14c arrow, 15 compressor, 16 four-way valve, 17 outdoor heat exchanger, 18 throttling device, 19 indoor heat exchanger, 20 outdoor blower, 21 outdoor blower motor, 22 indoor blower, 23 indoor blower motor, 24 refrigerant piping 25 refrigerant pipes, 26 outdoor units, 27 rooms Inner unit, 27a Indoor unit, 27b Indoor unit, 28 Distributor, 28a Distributor, 28b Distributor, 28c Distributor, 29 Piping header, 30 Projection part, 31 Gas refrigerant, 32 Liquid refrigerant, 33 Concave part, 34 Equal refrigerant, 35 header, 36 lid, 37 header, 38 lid, 45 dehumidification valve, 46 assist heat exchanger, 46a lower assist heat exchanger, 46b upper assist heat exchanger, 46c rear assist heat exchanger, 47 suction pipe, 48 outflow pipe , 50 housing, 51 inlet, 52 outlet, 100A heat exchanger, 100B heat exchanger, 100a lower heat exchanger, 100a ′ lower heat exchanger, 100b upper heat exchanger, 100b ′ upper heat exchanger, 100c Back heat exchanger, 100c 'Back heat exchanger, 150 Air-conditioning refrigeration equipment.

Claims (18)

A plurality of plate-like fins stacked in parallel at a predetermined interval, through which a fluid passes,
A plurality of heat transfer tubes that are inserted so as to be orthogonal to the plate fins, have a flat channel cross-sectional shape, and are provided with a plurality of partition walls inside,
A pair of headers that are respectively connected to ends of the plurality of heat transfer tubes that form a flow path of the working fluid, and communicate with the plurality of heat transfer tubes;
An inflow pipe that is attached to at least one of the headers and allows a working fluid to flow into the heat transfer pipe;
An outlet pipe attached to at least one of the headers and allowing the working fluid from the heat transfer pipe to flow out;
In the header, a plurality of rooms to which at least one of the end portions of the heat transfer tube is connected are formed,
A series of working fluid flow paths are formed through which the working fluid from the inflow pipe flows through the plurality of heat transfer pipes and flows out of the outflow pipe through the plurality of chambers formed in the pair of headers. ,
The working fluid that has flowed in from the inflow pipe collides with a position corresponding to an intermediate portion of the two heat transfer pipes in the room to which the one inflow pipe and the two heat transfer pipes are connected to form a gas state. Forming a protrusion provided with a collision portion for mixing the working fluid and the liquid working fluid;
The area of the collision portion is larger than the flow path cross-sectional area of the inflow pipe,
The protrusions,
A heat exchanger module, characterized in that the heat exchanger module protrudes from an end of the heat transfer tube connected to the room in which the protrusion is formed . The plurality of heat transfer tubes,
The heat exchanger module according to claim 1, wherein the heat exchanger modules are arranged in one row or two or more rows in the air flow direction. The heat exchanger module according to claim 1 or 2, wherein the inside of the header is divided into a plurality of working fluid flow paths. The heat exchanger module according to any one of claims 1 to 3 , wherein a concave portion is formed at a position where the working fluid of the protrusion collides. The heat exchanger module according to claim 4 , wherein the working fluid is distributed from the room in which the protrusion is formed to two working fluid flow paths. The heat exchanger module according to any one of claims 1 to 5 , wherein the number of the heat transfer tubes is 8 to 16. The heat exchanger module according to any one of claims 1 to 6 , wherein the heat transfer tubes have different lengths in the short direction. In the plate fin,
The heat exchanger module according to any one of claims 1 to 7 , wherein a cut and raised portion is formed by cutting and raising a part of the surface. It is comprised combining the heat exchanger module in any one of the said Claims 1-8 . The heat exchanger characterized by the above-mentioned. The heat exchanger according to claim 9 , wherein at least one of the interval between the plate-like fins or the interval between the heat transfer tubes among the plurality of the heat exchanger modules is different. The heat exchanger according to claim 9 or 10 , wherein the heat exchanger modules are arranged in a plurality of rows with respect to an air flow. It is a manufacturing method of the heat exchanger in any one of the above-mentioned Claims 9-11,
Providing a through hole into which the heat transfer tube is inserted into a square bar made of aluminum, and further forming the recess to be the room, the header is produced,
Arrange multiple plate-like fins to overlap,
Inserting the heat transfer tube into the header, inserting the heat transfer tube into the plate-like fins arranged, and attaching the lid to which the inflow pipe and the outflow pipe are attached to the header,
Thereafter, the heat exchanger module is produced by joining the plate fins and the heat transfer tubes,
The heat exchanger is manufactured by combining the produced heat exchanger modules.
The manufacturing method of the heat exchanger characterized by the above-mentioned. A plurality of heat exchangers according to any one of claims 9 to 11 ;
An indoor unit that houses an indoor blower that supplies air to the heat exchanger. The plurality of heat exchangers are:
It is arrange | positioned so that the said indoor air blower may be enclosed. The indoor unit of Claim 13 characterized by the above-mentioned. The indoor unit according to claim 14 , wherein an assist heat exchanger is provided on the windward side of each of the plurality of heat exchangers. The indoor unit according to any one of claims 13 to 15, wherein a reheat dehumidifying operation in which the heat exchanger is divided so that a part functions as a condenser and a part functions as an evaporator is possible. An air-conditioning refrigeration apparatus comprising the indoor unit according to any one of claims 13 to 16 . As working fluid,
The air-conditioning refrigerating apparatus according to claim 17 , wherein one of HC refrigerant, a mixed refrigerant containing HC, R32, ammonia, or carbon dioxide is used.

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