WO2019207838A1 - Refrigerant distributor, heat exchanger, and air conditioner - Google Patents

Abstract

A refrigerant distributor that is connected to the respective end portions of a plurality of flat heat transfer tubes (1) forming a refrigerant flow path, and that connects the plurality of flat heat transfer tubes (1), thereby distributing a refrigerant. The refrigerant distributor (3x) is equipped with a flat-tube-side header member (31x) and a combined header member (34x) which are combined with each other. The flat-tube-side header member (31x) and the combined header member (34x) are combined to form a narrow flow path (38) in which the cross-sectional area of a portion serving as the refrigerant flow path is narrowed.

Description

Refrigerant distributor, heat exchanger and air conditioner

The present invention relates to a refrigerant distributor, a heat exchanger equipped with the refrigerant distributor, and an air conditioner.

Many air conditioners that support air conditioning are currently using cross fin tube heat exchangers composed of circular copper heat transfer tubes and aluminum strip fins. This heat exchanger performs heat exchange between the refrigerant and air by flowing a fluorocarbon refrigerant in the copper heat transfer tube.

On the other hand, parallel flow type heat exchangers are widely used in automobile radiators and air conditioners for cooling to reduce size, weight, performance, and cost. In this heat exchanger, two header pipes are provided at both end openings of a plurality of flat heat transfer tubes brazed with aluminum fins on the outer surface, and the inflow side header pipe is connected to the outflow side via each flat heat transfer tube. It is a heat exchanger of the form which makes a refrigerant flow toward a header pipe.

In a parallel flow type heat exchanger, in order to make all the fin areas work effectively, it is necessary to flow an appropriate amount of liquid refrigerant to each of a plurality of flat heat transfer tubes arranged vertically.

However, in the heat exchanger, the refrigerant flows as a refrigerant in a gas-liquid two-phase state while changing the phase of evaporation and condensation, so that it stands in the vertical direction under the condition that the flow rate of the refrigerant is small and the momentum is low. Since the liquid refrigerant in the header pipe on the inflow side stays downward due to the influence of gravity, there is a tendency that it is difficult to supply sufficient liquid refrigerant to the flat heat transfer pipe connected to the upper part of the header pipe on the inflow side.

As a result, when the parallel flow heat exchanger is used as an evaporator, the amount of liquid refrigerant to be supplied is reduced in the upper one of the stacked flat heat transfer tubes, and all of the liquid refrigerant is upstream of the flat heat transfer tubes. Since it evaporates, heat absorption due to the evaporation of the liquid refrigerant does not occur downstream from the middle stream. That is, in the upper flat heat transfer tube, there is a problem that the liquid component of the refrigerant is small and the degree of superheat increases from the middle flow to the downstream, and the heat transfer area in that portion is not effectively used.

On the other hand, in the laminated flat heat transfer tubes below, the amount of liquid refrigerant supplied is excessive, so that the liquid refrigerant remains even at the outlet of the flat heat transfer tubes. That is, from the flat heat transfer tube below, the liquid refrigerant that has left the heat absorption capacity flows out, which causes a problem that the efficiency of the entire heat exchanger is deteriorated.

In addition, if a “liquid return” occurs in which the liquid refrigerant flows from the lower flat heat transfer tube into the compressor downstream of the heat exchanger, the liquid refrigerant may damage the compression chamber of the compressor. In order to avoid this, it is necessary to evaporate the liquid refrigerant completely by the expansion valve upstream of the heat exchanger and reducing the evaporation pressure to reach the outlet of the heat exchanger. There is a problem that the energy consumption in the vessel is increased.

In order to avoid such problems, when using a parallel flow type heat exchanger as an evaporator, the liquid refrigerant in each flat heat transfer tube is completely eliminated at a substantially aligned position near the header tube on the outflow side. Desirable to maximize heat exchanger performance. In particular, when supplying air at a constant wind speed to a heat exchanger, such as an outdoor unit of an air conditioner, it is required that the refrigerant can be equally distributed to each flat heat transfer tube without drift.
As a conventional technique for solving such a problem, for example, there is one shown in FIG. In this example, in order to improve refrigerant distribution in a vertically standing header, a part of the internal space of the header is partitioned by a partition, and a plurality of through holes are provided in the partition. As a result, the refrigerant is to be uniformly distributed to the flat heat transfer tubes.

In addition, Patent Document 2 and Patent Document 3 have a header structure that is divided in the longitudinal direction for ease of manufacturing itself and ease of making an internal structure for refrigerant distribution, regardless of the distribution structure. It is shown.

Japanese Patent No. 5775226 Japanese Patent No. 4827882 Japanese Patent No. 4405819

In Patent Document 1, the refrigerant discharged from the partitioned space in the header has an enlarged flow path cross-sectional area, so the flow rate of the liquid refrigerant is reduced, and the liquid refrigerant easily falls under the action of gravity and falls down in the header. Cheap. In particular, the liquid refrigerant tends to stay in the lower part due to the influence of gravity in the low refrigerant flow rate region. In such a case, the liquid may flow unevenly in the lower heat transfer tube.

In Patent Document 2, a folded flow path or a branch flow path is configured by a divided header structure. As the refrigerant flow path, the refrigerant flows one flat heat transfer tube at a time, and the refrigerant does not flow through the plurality of heat transfer tubes. When the amount of circulation is large, the cross-sectional area of the flow path is insufficient, so that the pressure loss becomes large and the saturation temperature is lowered downstream in the flow direction.

In Patent Document 3, in the divided header structure, the refrigerant flow path cannot be narrowed, and the liquid refrigerant accumulates below due to the action of gravity, and the problem of refrigerant distribution when the heat exchanger is used as an evaporator. was there.

The present invention is an invention for solving the above-described problems, and is capable of supplying liquid refrigerant to each flat heat transfer tube in a parallel flow evaporator even when operating under minimum load conditions or intermediate load conditions. An object of the present invention is to provide a refrigerant distributor capable of suppressing the unevenness of the quantity with a simple structure and improving the performance as an evaporator, a heat exchanger including the refrigerant distributor, and an air conditioner.

In order to achieve the above object, the refrigerant distributor of the present invention is a refrigerant distributor that is connected to the end portions of a plurality of heat transfer tubes forming a refrigerant flow path, communicates the plurality of heat transfer tubes, and distributes the refrigerant. The refrigerant distributor includes a first member and a second member that are combined with each other, and a narrow flow path in which a cross-sectional area of a portion that becomes a flow path of the refrigerant is narrowed by combining the first member and the second member. It is characterized by forming.

The first member and the second member are formed of a plate material, and the first member and the second member have a D-shaped cross section formed by bending the plate material, and are spaced apart from a part of the D-shaped linear portion. And the first member and the second member are combined through the separated portion, and a narrow channel is formed between the D-shaped straight portions of the first member and the second member facing each other. And The first member has a concave cross section, and the second member is fitted to the inner surface of the first member to form a narrow channel. Other aspects of the present invention will be described in the embodiments described later.

According to the present invention, even during operation under a minimum load condition or an intermediate load condition, the bias of the liquid refrigerant supply amount to each flat heat transfer tube in the parallel flow type evaporator is suppressed with a simple structure, The performance as an evaporator can be improved.

It is a figure which shows the external appearance structure of the heat exchanger which concerns on 1st Embodiment. It is a figure which shows the structure of the heat exchanger at the time of using the flat heat exchanger tube which concerns on 1st Embodiment. It is a figure which shows the structure of the flat heat exchanger tube which concerns on 1st Embodiment. It is a figure which shows the structure of the header of the heat exchanger which concerns on 1st Embodiment. It is a figure which shows the cross section of the header of the heat exchanger which concerns on 1st Embodiment. It is a figure which shows that the header which concerns on 1st Embodiment is point symmetrical. It is a figure which shows the decomposition | disassembly state of the header of the heat exchanger which concerns on 1st Embodiment. It is a figure which shows the longitudinal cross-section of the header of the heat exchanger which concerns on 1st Embodiment. It is a figure which shows the brazing surface of the refrigerant distributor which concerns on 1st Embodiment. It is a figure which shows the other brazing surface of the refrigerant distributor which concerns on 1st Embodiment. It is a figure which shows the external appearance structure of the heat exchanger which concerns on 2nd Embodiment. It is a figure which shows the cross section of the header of Example 1 which concerns on 2nd Embodiment. It is a figure which shows the side surface of the header of the heat exchanger of Example 1 which concerns on 2nd Embodiment. It is a figure which shows the cross section of the header of the heat exchanger of Example 2 which concerns on 2nd Embodiment, and a header insertion member is a figure of a concave shape member. It is a figure which shows the cross section of the header of the heat exchanger of Example 2 which concerns on 2nd Embodiment, and a header insertion member is a figure of a cylinder shape (hollow shape). It is a figure which shows the cross section of the header of the heat exchanger of Example 2 which concerns on 2nd Embodiment, and a header insertion member is a figure of H shape. It is a figure which shows the cross section of the header of the heat exchanger of Example 2 which concerns on 2nd Embodiment, and a header insertion member is a figure of trapezoid shape. It is a figure which shows the cross section of the header of the heat exchanger of Example 3 which concerns on 2nd Embodiment. It is a figure which shows the cross section of the header of the heat exchanger of Example 4 which concerns on 2nd Embodiment. It is a figure which shows the cross section of the header of the heat exchanger of Example 5 which concerns on 2nd Embodiment, and is a figure used as a reference | standard. It is a figure which shows the cross section of the header of the heat exchanger of Example 5 which concerns on 2nd Embodiment, and is a figure which sets the insertion length of a header insertion member long. It is a figure which shows the cross section of the header of the heat exchanger of Example 5 which concerns on 2nd Embodiment, and is a figure which inserts a member different from a header insertion member in a flow path. It is a figure which shows the attachment method of the perforated partition plate in the header of Example 6 which concerns on 2nd Embodiment. It is a figure which shows the other example of the attachment method of the perforated partition plate in the header of Example 6 which concerns on 2nd Embodiment. It is a figure which shows the other example of the attachment method of the perforated partition plate in the header of Example 6 which concerns on 2nd Embodiment. It is a figure which shows the structure of the perforated partition plate of the header of Example 7 which concerns on 2nd Embodiment. It is a figure which shows the other structure of the perforated partition plate of the header of Example 7 which concerns on 2nd Embodiment. It is a figure which shows the perforated board for the drift prevention in the header of Example 8 which concerns on 2nd Embodiment. It is a figure which shows the longitudinal cross-section of the perforated board for drift prevention in the header of Example 8 which concerns on 2nd Embodiment. It is a figure which shows the position of the partition plate of the header insertion member of Example 9 which concerns on 2nd Embodiment. It is a front view of the heat exchanger of Example 10 which concerns on 3rd Embodiment. It is a longitudinal cross-sectional view of the header vicinity in the heat exchanger of Example 10 which concerns on 3rd Embodiment. It is a cross-sectional view near the header in the heat exchanger of Example 10 according to the third embodiment. It is a longitudinal cross-sectional view of the header vicinity in the heat exchanger of Example 11 which concerns on 3rd Embodiment. It is a longitudinal cross-sectional view of the header vicinity in the heat exchanger of Example 12 which concerns on 3rd Embodiment. It is a side view of the connecting pipe of a bypass pipe with which the heat exchanger of Example 12 concerning a 3rd embodiment is provided. In the heat exchanger of Example 12 which concerns on 3rd Embodiment, it is explanatory drawing which shows the cross section of a refrigerant | coolant inlet pipe in case the circulation amount of a refrigerant | coolant is comparatively large. In the heat exchanger of Example 12 which concerns on 3rd Embodiment, it is explanatory drawing which shows the cross section of a refrigerant | coolant inlet tube in case the circulation amount of a refrigerant | coolant is comparatively small. It is a longitudinal cross-sectional view of the header vicinity in the heat exchanger of Example 13 which concerns on 3rd Embodiment. It is a longitudinal cross-sectional view of the header vicinity in the heat exchanger of Example 14 which concerns on 3rd Embodiment. It is a cross-sectional view of the vicinity of the header in the heat exchanger of Example 14 according to the third embodiment. It is a disassembled perspective view at the time of seeing the header with which the heat exchanger of Example 15 which concerns on 3rd Embodiment is provided from the other side of a refrigerant | coolant inlet pipe. It is a disassembled perspective view at the time of seeing the header with which the heat exchanger of Example 15 which concerns on 3rd Embodiment is provided from the refrigerant | coolant inlet pipe side. In the header with which the heat exchanger of Example 15 which concerns on 3rd Embodiment is provided, it is an exploded view at the time of seeing the header cut | disconnected by the cross section containing a flat heat exchanger tube from right above. It is a disassembled perspective view at the time of seeing the header with which the heat exchanger of Example 16 which concerns on 3rd Embodiment is provided from the other side of a refrigerant | coolant inlet pipe. It is a disassembled perspective view at the time of seeing the header with which the heat exchanger of Example 16 which concerns on 3rd Embodiment is provided from the refrigerant | coolant inlet pipe side. In the header with which the heat exchanger of Example 16 which concerns on 3rd Embodiment is provided, it is an exploded view at the time of seeing the header cut | disconnected by the cross section containing a flat heat exchanger tube from right above. It is a front view of the heat exchanger of Example 17 which concerns on 3rd Embodiment. It is a perspective view which shows the external appearance structure of the heat exchanger of Example 18 which concerns on 3rd Embodiment. It is a perspective view of the heat exchanger which concerns on a 1st reference form. It is the perspective view which looked at the header vicinity of the heat exchanger which concerns on a 1st reference form from diagonally upward. It is a disassembled perspective view of the header vicinity of the heat exchanger which concerns on a 1st reference form. FIG. 34B is a VII direction arrow view of the duct of FIG. 34A in the first reference embodiment. FIG. 33 is a view taken along arrow VIII in FIG. 32 in the first reference embodiment. FIG. 35B is a sectional view taken along line IX-IX in FIG. 35A in the first reference embodiment. In 1st reference form, it is the Q1 part enlarged view of FIG. 35B. It is a top view of the heat exchanger which concerns on a 1st reference form. FIG. 36B is a sectional view taken along line XI-XI in FIG. 36A in the first reference embodiment. FIG. 36B is an enlarged view of part Q2 in FIG. 36B in the first reference embodiment. It is a perspective view which shows the heat exchanger which concerns on the modification of 1st reference form. It is a perspective view of the heat exchanger which concerns on a 2nd reference form. In order to make it easy to understand the structure of the header of the heat exchanger according to the second embodiment, the inner cylinder and the intermediate cylinder are pulled up from the outer cylinder and a part thereof is exposed. It is a cross-sectional view of the flat tube and header of the heat exchanger which concerns on a 2nd reference form. It is a longitudinal cross-sectional view of the heat exchanger which concerns on a 2nd reference form. It is the elements on larger scale which notched some heat exchangers concerning a 2nd reference form. It is a perspective view of the upper part vicinity of the header with which the heat exchanger which concerns on a 2nd reference form is provided. It is a figure explaining a refrigerating cycle. It is a figure explaining the superheat degree by the drift of the refrigerant | coolant distribution of a heat exchanger, and is a figure when there is no drift of a liquid refrigerant. It is a figure explaining the superheat degree by the drift of the refrigerant | coolant distribution of a heat exchanger, and is a figure in case there exists a drift of a liquid refrigerant. It is a schematic diagram of the header structure as a comparative example, and is a figure which shows a round cross section. It is a schematic diagram of the header structure as a comparative example, and is a figure which shows the cross section of the header comprised with two members. It is a schematic diagram of the header structure as a comparative example, and is a figure which shows the other cross section of the header comprised with two members.

DESCRIPTION OF EMBODIMENTS Embodiments for carrying out the present invention will be described in detail with reference to the drawings as appropriate.
First, a refrigeration cycle to which the refrigerant distributor and the heat exchanger of the present embodiment are applied will be described first, and conventional problems will be described in detail.

FIG. 44 is a diagram for explaining the refrigeration cycle. Here, with reference to FIG. 44, the refrigeration cycle of the heat pump type air conditioner AC will be described taking heating operation as an example. As shown here, the air conditioner AC includes a compressor 8, a four-way valve 9, an indoor heat exchanger 101, an expansion valve 103, an outdoor heat exchanger 106, and the like.

The compressor 8 compresses the gas refrigerant, and the refrigerant 60 that has been brought to a high temperature / high pressure state by the compressor 8 is led to the indoor heat exchanger 101 (condenser) in the indoor unit 100 via the four-way valve 9. It is burned. And the room | chamber interior is warmed because the high temperature refrigerant | coolant which flows through the inside of the flat heat exchanger tube of the indoor heat exchanger 101 dissipates to the indoor air supplied from the air blower 102. At this time, in the flat heat transfer tube, the gas refrigerant that has been deprived of heat gradually liquefies, and from the outlet of the indoor heat exchanger 101, the supercooled liquid refrigerant that is several degrees C lower than the saturation temperature flows out.

Thereafter, the liquid refrigerant that has flowed out of the indoor unit 100 becomes a gas-liquid two-phase refrigerant in a low-temperature and low-pressure state by an expansion action when passing through the expansion valve 103. This low-temperature, low-pressure gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 106 (evaporator) in the outdoor unit 105. And the low-temperature refrigerant | coolant which flows through the inside of the flat heat exchanger tube of the outdoor heat exchanger 106 absorbs heat from the external air supplied from the air blower 107, so that the dryness of the refrigerant (= mass velocity of gas / (mass velocity of liquid + gas) Mass velocity))). At the outlet of the outdoor heat exchanger 106, the refrigerant is gasified and returned to the compressor 8 with a degree of superheat of several degrees Celsius. The heating operation of the air conditioner AC is realized by the series of refrigeration cycles in which the refrigerant 60 circulates counterclockwise as described above.

On the other hand, during the cooling operation, the four-way valve 9 is switched to form a refrigeration cycle in which the refrigerant 61 circulates clockwise. In this case, the indoor heat exchanger 101 acts as an evaporator, and the outdoor heat exchanger 106 acts as a condenser.

Next, when the indoor heat exchanger 101 or the outdoor heat exchanger 106 acts as an evaporator, the state of refrigerant drift that occurs in the evaporator will be described with reference to FIGS. 45A and 45B. 45A and 45B are schematic and schematic views of the evaporator, and are partially simplified, such as omitting the individual display of the flat heat transfer tubes.

FIG. 45A is a diagram for explaining the degree of superheat due to the drift of refrigerant distribution in the heat exchanger, and is a diagram when there is no drift of liquid refrigerant. FIG. 45B is a diagram for explaining the degree of superheat due to the drift of refrigerant distribution in the heat exchanger, and is a diagram when there is a drift of liquid refrigerant. As shown in these figures, the heat exchanger is provided with headers 3a and 3b that are substantially perpendicular to the left and right, and connected by a number of flat heat transfer tubes 1 that are stacked in the vertical direction therebetween. Each flat heat transfer tube 1 is brazed with a fin for enlarging the heat transfer area, but is not shown here. Further, in the flat heat transfer tube 1, the hatched portion is a two-phase region 90 through which the gas-liquid two-phase refrigerant flows, and the white portion is an overheat region 91 through which the gas refrigerant flows.

45A and 45B, in the parallel flow type evaporator, low-temperature and low-pressure gas-liquid two-phase refrigerant flows from the lower part of the header 3b. The refrigerant flowing in flows in the flat heat transfer tubes 1 in the order of the regions (A) → (B) → (C) → (D) while changing the flow direction, and exchanges heat with the air passing between the flat heat transfer tubes 1 ( After the heat absorption), the refrigerant is discharged from the upper portion of the header 3b as a medium temperature / low pressure refrigerant.

As shown in FIG. 45A, when refrigerant drift does not occur, that is, when the flow rate of the refrigerant is large and a substantially equal amount of gas-liquid two-phase refrigerant is supplied to each flat heat transfer tube 1 in the region (D), Even in the flat heat transfer tube 1 of the height, since the two-phase region 90 becomes the superheated region 91 at the same distance from the inflow side, only the gas refrigerant that has sufficiently absorbed heat flows out from any flat heat transfer tube 1. .

On the other hand, as shown in FIG. 45B, when the liquid refrigerant drifts, that is, gravity acts on the gas-liquid two-phase refrigerant having a low flow velocity in the header 3a and flows into the flat heat transfer tube 1 above the region (D). When the amount of liquid refrigerant is small and the amount of liquid refrigerant flowing into the lower flat heat transfer tube 1 increases, the two-phase region 90 is below and the superheat region 91 is above in the vicinity of the outlet of the region (D).

As described above, when the gas-liquid two-phase refrigerant containing a large amount of liquid refrigerant returns to the compressor 8, the “liquid return” causes damage to the compression chamber. In order to avoid this, it is necessary to throttle the expansion valve 103 upstream of the evaporator and lower the evaporation pressure (temperature) so that the liquid refrigerant is completely gasified in the vicinity of the exit of the region (D) in FIG. 45B. There is. However, when the evaporation pressure is lowered, there is a problem that the compression work increases and the energy saving performance of the air conditioner is hindered.

Further, when refrigerant drift occurs, the two-phase region 90 is short and the superheat region 91 is long in the flat heat transfer tube 1 above the region (D), so that the two-phase region 90 greatly contributes to the heat absorption from the air. There is a problem that the heat transfer area decreases and the compression work increases.
In order to solve the above problems, various methods of Patent Documents 1 to 3 have been tried.

FIG. 46A is a schematic diagram of a header structure as a comparative example, and shows a round cross section. FIG. 46B is a schematic diagram of a header structure as a comparative example, and is a diagram illustrating a cross section of a header configured by two members. FIG. 46C is a schematic diagram of a header structure as a comparative example, and is a diagram showing another cross-section of the header constituted by two members.

FIG. 46A is a header showing a round cross section that is frequently used mainly for condensers such as radiators for automobiles. The header 3a to which the flat heat transfer tube 1 is connected has a round shape. FIG. 46B shows the structure of the header divided in Patent Document 3. The header 3a includes a first member 310a and a second member 340a. In addition, there is a divided header structure as shown in FIG. 46C. The header 3a includes a first member 311a and a second member 341a.

In the header structures of FIGS. 46A, 46B, and 46C, since the flow path cross-sectional area is large, the speed of the liquid refrigerant tends to be small and tends to accumulate in the lower part of the header due to the effect of weight.

For this reason, in this embodiment, even during operation under the minimum load condition or intermediate load condition, the bias of the liquid refrigerant supply amount to each flat heat transfer tube in the parallel flow evaporator is suppressed with a simple structure. And the refrigerant distributor (header) which can improve the performance as an evaporator is proposed.

<< first embodiment >>
FIG. 1 is a diagram illustrating an external configuration of a heat exchanger according to the first embodiment. FIG. 2 is a diagram illustrating a state before the headers 3x and 3y are inserted into the flat heat transfer tube 1 according to the first embodiment. The heat exchanger includes a large number of flat heat transfer tubes 1 in which the refrigerant flows and extends in the lateral direction, a plurality of fins 2 into which a large number of flat heat transfer tubes 1 are inserted, and heat exchange with the refrigerant is performed. The headers 3x and 3y are connected to one of the flat heat transfer tubes 1 and extend in the vertical direction (vertical direction), and the refrigerant is distributed to a large number of flat heat transfer tubes 1. A refrigerant inlet pipe 30 is connected below the header 3x. A refrigerant outlet pipe 33 is connected to the central portion of the header 3x. The refrigerant flows in from the refrigerant inlet pipe 30, flows through the plurality of flat heat transfer pipes 1, and flows out from the refrigerant outlet pipe 33. A partition plate 35x (see FIG. 4) is inserted in the upper part, middle lower part, and lower part of the header 3x. Similarly, a partition plate 35x is inserted in the upper part and the lower part of the refrigerant outlet pipe 33 of the header 3y.

FIG. 3 is a diagram showing a configuration of the flat heat transfer tube 1 according to the first embodiment. The flat heat transfer tube 1 includes a heat transfer tube body 11 that forms an appearance, and a partition rib 13 that allows a large number of refrigerant channels 12 to be formed inside the heat transfer tube body 11. The refrigerant that has flowed into the flat heat transfer tube 1 can be uniformly distributed and flown into the multiple refrigerant flow paths 12.

FIG. 4 is a diagram illustrating a configuration of the header 3x of the heat exchanger according to the first embodiment. FIG. 5 is a diagram showing a cross section of the header 3x of the heat exchanger according to the first embodiment. FIG. 5 shows an XX cross section of FIG. The header 3x includes a flat tube side header member 31x (first member) and a combination header member 34x (second member). In addition, partition plates 35x are inserted in the upper, middle, and lower portions of the header 3x.

The narrow flow path 38 is formed by combining the flat tube side header member 31x (first member) and the combined header member 34x (second member). The narrow flow path 38 is a flow path in which the cross-sectional area (area of the cross section) of the portion that becomes the flow path of the refrigerant is narrowed. And the cross-sectional area of the narrow flow path 38 is smaller than the cross-sectional area of the header 3x (refrigerant distributor).

The flat tube side header member 31x and the combination header member 34x are formed of a plate material, and the flat tube side header member 31x and the combination header member 34x have a D-shaped cross section formed by bending the plate material. A separation portion 39 (see FIG. 7) is provided in a part of the straight portion. The flat tube side header member 31x and the combination header member 34x are combined through the separation portion 39, and the narrow flow path 38 is formed between the D-shaped straight portions of the flat tube side header member 31x and the combination header member 34x facing each other. Forming. In addition, you may manufacture the flat tube side header member 31x and the combination header member 34x, or its combination member by extrusion molding.
Further, the flat tube side header member 31x and the combined header member 34x can be formed not only by bending the plate material but also by extrusion molding or the like.

FIG. 6 is a diagram showing that the header 3x according to the first embodiment is point-symmetric. The left diagram in FIG. 6 shows a cross section (XX cross section, see FIG. 4) of the header member in which the flat tube header member 31x and the combined header member 34x are combined. When this is rotated 180 degrees around the point O, the right diagram of FIG. 6 is obtained. As shown in FIG. 6, the cross-sectional shape of the header member in which the flat tube side header member 31x and the combined header member 34x are combined is a point-symmetric shape except for the hole position where the flat heat transfer tube 1 is inserted. I understand that.

The flat tube side header member 31x (first member) has an opening 31x3, and the combined header member 34x (second member) has an opening 34x3. The first member and the second member have an opening to which the same heat transfer tube is connected.

The flat tube side header member 31x (first member) has a parallel surface 31x4 parallel to the end surface of the flat heat transfer tube 1, and the combined header member 34x (second member) is parallel to the end surface of the flat heat transfer tube 1. It has a parallel surface 34x4. Each of the first member and the second member has a parallel surface parallel to the end surface of the heat transfer tube, and has at least one bent portion to form the parallel surface. The parallel plane corresponds to the D-shaped straight portion described above.

FIG. 7 is a diagram showing an exploded state of the header of the heat exchanger according to the first embodiment. The combined header member 34x is inserted into the flat tube side header member 31x from the upper part in the vertical direction in accordance with the separation portion 39. Thereafter, the combined header member is inserted into the flat heat transfer tube 1. The partition plate 35x is inserted into the upper part, middle lower part, and lower part of the combined header member.

FIG. 8 is a view showing a longitudinal section of the header of the heat exchanger according to the first embodiment. FIG. 8 shows a YY cross section of FIG. It can be seen that the narrow channel 38 is formed in the header 3x by combining the flat tube side header member 31x (first member) and the combined header member 34x (second member). Thus, the speed of the refrigerant inside the header according to the present embodiment is increased compared to the shape shown as the header cross-sectional structure of the comparative example shown in FIG. As a result, the momentum of the liquid refrigerant increases and the liquid refrigerant can reach the flat heat transfer tube 1 attached to the upper part of the header.

FIG. 9 is a view showing a brazing surface of the refrigerant distributor according to the first embodiment. The clad material is formed by laminating a brazing material 31x1 on the outer side of the base material 31x0 of the flat tube side header member 31x. The clad material is formed by laminating a brazing material 34x1 on the outside of the base material 34x0 of the combination header member 34x. The header structure according to the present embodiment can be brazed with such a configuration using a single-sided clad material.

FIG. 10 is a view showing another brazing surface of the refrigerant distributor according to the first embodiment. FIG. 10 shows the minimum required brazing surfaces 37a, 37b, and 37c. The brazing surface 37a is a joint surface between the flat tube side header member 31x and the flat heat transfer tube 1, and the brazing surfaces 37b and 37c are joint surfaces between the flat tube side header member 31x and the combined header member 34x. In the case of FIG. 10 as well, a substantially narrow channel 38 can be formed.

According to the first embodiment, the narrow flow path 38 can be formed by combining the header members, and by increasing the refrigerant flow rate, the liquid refrigerant can be raised to the upper part of the heat exchanger and the refrigerant distribution can be improved. Moreover, the combination member is a substantially equivalent member and has excellent assemblability.

<< Second Embodiment >>
Example 1
FIG. 11A is a diagram illustrating an external configuration of a heat exchanger according to the second embodiment. FIG. 11B is a diagram illustrating a cross section of the header of Example 1 according to the second embodiment. FIG. 11B shows a cross section taken along line II-II in FIG. 11A. As shown in FIG. 11A, there are two headers 3a and 3b arranged substantially vertically on the upstream side and the downstream side, and a plurality of flat heat transfer tubes 1 are connected between them in a substantially vertical direction. In each flat heat transfer tube 1, a plurality of fins 2 that expand the heat transfer area are arranged with a predetermined gap in the horizontal direction. Although the fin 2 is not shown in detail, when the heat exchanger is used as an evaporator, the fin 2 is devised so that water droplets condensed on the fin surface are likely to fall. It also has a shape for defining the gap between adjacent fins to be constant.

The header 3a includes a header base member 31a (first member) which is a concave-shaped member and a header insertion member 34b (second member). Similarly, the header 3b includes a header base member 31b (first member) that is a concave-shaped member, and a header insertion member 34b (second member).

The refrigerant inlet pipe 30 is connected below the header insertion member 34a. In addition, the refrigerant outlet pipe 33 is connected to the header insertion member 34b. The refrigerant flows in from the refrigerant inlet pipe 30, flows through the plurality of flat heat transfer pipes 1, and flows out from the refrigerant outlet pipe 33.

Heat is exchanged between the refrigerant and the air by air flowing between the fins in a direction substantially perpendicular to the paper surface. Under conditions widely used in air conditioners, the air side has a laminar heat transfer coefficient of about several tens to one hundred W / (m ² K), and the flow path of the flat heat transfer tube 1 is several thousand W / (m Heat transfer performance with a boiling heat transfer coefficient of about ² K). Therefore, since the effect of expanding the area on the air side is great, the fin 2 is a thin fin made of aluminum and has a fin gap of about 1 mm to several mm so that the area on the air side can be secured as much as possible if the heat exchanger has the same volume. Consists of.

The feature of the present embodiment is that the end of the flat heat transfer tube 1 is inserted into a hole provided in the flat portion of the header base member 31a of the concave-shaped member. The header insertion member 34a is inserted into the opposite opening side to which the flat heat transfer tube 1 of the concave shape member is connected. Both of them are brazed in a furnace such as an electric furnace, so that a header structure having a narrow flow path 38 serving as a refrigerant flow path is obtained. Similarly, the header 3b of the other header is inserted into the header base member 31b with the header insertion member 34b to form a narrow channel 38 serving as a coolant channel. That is, the contact surface between the header base member 31a and the header insertion member 34a, which are concave-shaped members, serves as a brazing surface.

In FIG. 11A, the flow of the refrigerant when the heat exchanger is used as an evaporator is indicated by white arrows. In FIG. 11A, the refrigerant that has become low temperature and low pressure due to the action of an expansion valve (not shown) flows through the number of flat heat transfer tubes in parallel for each space partitioned by the partition plates 35a and 35b in the heat exchanger. And a refrigerant | coolant flows upwards through the perforated partition plate 36a (partition plate with a hole), and flows the number of flat heat-transfer tubes in parallel. The refrigerant that has flowed in from the refrigerant inlet pipe 30 flows upward from the lower side of the heat exchanger as the area a → the area b → the area c, and finally flows out from the refrigerant outlet pipe 33.

In addition, although the flow of the refrigerant | coolant which flows upwards simply from the downward direction of a heat exchanger was shown in the figure, the flow which once went downward once for every partitioned space may be included. In this way, when the refrigerant flows from the bottom to the top in the heat exchanger, the supercooled liquid refrigerant accumulates due to gravity when the flow direction is changed by the same heat exchanger and used as a condenser. This is to make it easier to go downward so as not to occur.

In the refrigerant when used as an evaporator, the liquid component gradually evaporates in the flow direction and the gas component increases. Therefore, when flowing with the same flow path cross-sectional area, the pressure loss per unit increases due to the increased flow velocity of the gas refrigerant. As a result, there is a problem that an effective temperature difference with the air cannot be ensured due to a decrease in the saturation temperature of the refrigerant, and the energy saving performance is deteriorated due to an increase in compression work as a whole. Therefore, it is generally performed to increase the number of flat heat transfer tubes that gradually flow in parallel toward the outlet so that the pressure loss does not increase so much.

Fig. 11B shows an enlarged view of the II-II cross section. A header insertion member 34a is inserted into the header base member 31a, which is a concave member, and the contact surface is brazed to form a narrow channel 38 (header space). The area inside the header base member 31a of the concave-shaped member defined by a virtual surface on the opening side of the header base member 31a of the concave-shaped member is narrowed by inserting the header insertion member 34a into the narrow-shaped flow. A path 38 is formed. Thus, the speed of the refrigerant inside the header according to the present embodiment is increased compared to the shape shown as the header cross-sectional structure of the comparative example shown in FIG. As a result, the momentum of the liquid refrigerant increases and the liquid refrigerant can reach the flat heat transfer tube attached to the upper part of the header. Further, there is a perforated partition plate 36a, and the liquid refrigerant is guided upward in a state where the partition plate 36a is narrowed at the smallest area and the flow velocity is increased.

In FIG. 11A, a simplified example of a heat exchanger is shown for the sake of explanation, but actually, a plurality of these basic configurations are stacked in the height direction, or a similar heat exchanger is used for air. A predetermined heat transfer area can be secured by arranging them in the downwind and upwind directions. Furthermore, although the perforated partition plate 36a is provided in one place in FIG. 1 for the sake of simplifying the description, it may be provided in the header 3b at the same height position as the partition plate 35a, which improves the drift in the region b. I can plan.

FIG. 12 is a view of the end portion of the flat heat transfer tube 1 as viewed from the open side of the header base member 31a of the concave-shaped member (indicated by arrow III in FIG. 11A). The flat heat transfer tube 1 is provided with a plurality of small channels of about 1 mm to several mm through which a plurality of refrigerants flow, and is formed by extrusion or drawing. The header base member 31a of the concave shape member and each flat heat transfer tube 1 are brazed at the connection surface 131.

(Example 2)
FIG. 13A is a diagram illustrating a cross section of the header of the heat exchanger of Example 2 according to the second embodiment, and the header insertion member 34a is a diagram of a concave shape member. FIG. 13B is a diagram showing a cross section of the header of the heat exchanger of Example 2 according to the second embodiment, and the header insertion member 34a is a cylindrical shape (hollow shape). FIG. 13C is a diagram illustrating a cross-section of the header of the heat exchanger of Example 2 according to the second embodiment, and the header insertion member 34a is an H-shaped diagram. FIG. 13D is a diagram illustrating a header cross section of the heat exchanger of Example 2 according to the second embodiment, and the header insertion member 34a is a trapezoidal shape.

FIG. 13A is a reference configuration, and similarly to the header base member 31a of the concave-shaped member, the header insertion member 34a is also configured of a concave-shaped member that opens in the same direction. Such a configuration can most reduce the weight of the header portion as long as the strength with the header internal pressure is secured.

FIG. 13B shows the header insertion member 34a having a cylindrical shape (hollow shape). In such a configuration, it is possible to increase the rigidity of the header insertion member 34a. The header insertion member 34a may be a solid material. In this case, the rigidity can be further increased.

FIG. 13C shows that the header insertion member 34a is formed of a substantially H-shaped member. It can be manufactured by extrusion processing, and it becomes possible to further narrow the flow path area surrounded by the concave header base member 31a.

FIG. 13D shows the header base member 31a, which is a concave-shaped member, having a laterally widening cross section. With such a configuration, it is possible to perform brazing while applying a contact load to the contact surface by fixing using a jig or the like of the header base member 31a and the insertion member 34a of a concave-shaped member, or brazing while binding.

In addition, although each figure has shown as the shape which aligned the opening side end surface of the header base member 31a of a concave shape member, and the surface of the header insertion member 34, the shape which provided the level | step difference may be sufficient. When the end faces are aligned, the assembly accuracy of the parts can be improved, and the assembly condition can be managed by confirming the appearance.

(Example 3)
FIG. 14: is a figure which shows the cross section of the header of the heat exchanger of Example 3 which concerns on 2nd Embodiment. The difference from the invention up to FIG. 13 is that the other end is longer like 31a1 as compared to the end length of the header base member 31a of the concave-shaped member. With such a configuration, since the heat exchanger can be fixed via the housing 319 and the joining component 318, a separate member for fixing becomes unnecessary. Note that it is not necessary to provide all the stretched 31a1 in the longitudinal direction, and the material and weight can be reduced by providing only the portions necessary for fixation. Although FIG. 14 shows an example in which the heat exchanger and the casing are fixed, they may be used for fixing the heat exchangers.

Example 4
FIG. 15: is a figure which shows the cross section of the header of the heat exchanger of Example 4 which concerns on 2nd Embodiment. The clad material is formed by laminating a brazing material shown as 31a2 on the outer side of the base material 31a0 of the header base member 31a of a substantially U-shaped member. Further, the brazing material 34a1 is applied to the outside of the base material 34a0 of the header insertion member 34a. The header structure according to the present invention can be brazed with such a configuration using a single-sided clad material.

(Example 5)
FIG. 16A is a diagram illustrating a header cross-section of the heat exchanger of Example 5 according to the second embodiment, and serves as a reference. FIG. 16B is a diagram illustrating a header cross section of the heat exchanger of Example 5 according to the second embodiment, and is a diagram in which the insertion length of the header insertion member 34a is set longer. FIG. 16C is a diagram illustrating a header cross section of the heat exchanger of Example 5 according to the second embodiment, and is a diagram in which a member 340 different from the header insertion member 34a is inserted into the flow path.

FIG. 16B sets the insertion length of the header insertion member 34a inserted into the header base member 31a, which is a concave-shaped member, to be longer than that of FIG. 16A. By making the insertion length longer, it becomes possible to make adjustments such as reducing the flow path area of the refrigerant. In FIG. 16C, a member 340 different from the header insertion member 34a is inserted into the flow path cross section. With such a configuration, the refrigerant flow path can be further narrowed, so that the flow path can be partially narrowed in accordance with the region in the heat exchanger, and the degree of freedom in adjusting refrigerant drift in advance is increased. In FIG. 16B, it is preferable that the gap D1 between the outer surface of the insertion member 34a and the end surface of the flat heat transfer tube 1 inserted in the header facing the outer surface is 1 mm to 3 mm.

(Example 6)
FIG. 17A is a diagram illustrating a method of attaching the perforated partition plate 36a (partition plate with holes) in the header of Example 6 according to the second embodiment. FIG. 17B is a diagram showing another example of a method for attaching the perforated partition plate 36a in the header of Example 6 according to the second embodiment. FIG. 17C is a diagram illustrating another example of the attachment method of the perforated partition plate 36a in the header of Example 6 according to the second embodiment. The perforated partition plate 36 a has a square hole 360.

In FIG. 17A, the perforated partition plate 36a is installed by inserting the projection 36a1 of the perforated partition plate 36a into the hole 34a2 of the header insertion member 34a, and is built into the opening of the header base member 31a and brazed. FIG. 17B shows that the leakage of the refrigerant can be reduced by cutting off the corners of the insertion member 34a as shown in the drawing or by processing it into a round shape. In FIG. 17C, a groove 34a3 is provided in advance in the header insertion member 34a, and a perforated partition plate 36a having a protrusion 36a1 is provided in the groove 34a3.
Although FIG. 17 shows an example of the perforated partition plate 36a, the fixing method shown in FIG. 17 may be applied to the partition plates 35a and 35b.

(Example 7)
FIG. 18A is a diagram illustrating a configuration of the perforated partition plate 36a of the header of Example 7 according to the second embodiment. FIG. 18B is a diagram showing another configuration of the header perforated partition plate 36a of Example 7 according to the second embodiment. 18A and 18B relate to the perforated partition plate 36a described in the sixth embodiment. FIG. 18A shows a configuration in which one hole 360a is formed. FIG. 18B shows a configuration in which two holes 360a are formed. A round hole as well as the square hole shown in FIG. 17 may be used, and a faster refrigerant speed can be realized in the header space by selecting the hole diameter.

(Example 8)
FIG. 19A is a diagram illustrating a perforated plate 132 for preventing drift in the header 3a of Example 8 according to the second embodiment. FIG. 19A is a view showing a IV-IV cross section of FIG. 11A. FIG. 19B is a perspective view of the perforated plate 132 for preventing drift in the header 3a of Example 8 according to the second embodiment. A perforated plate 132 is built in the header base member 31a, which is a concave member, so that the end face and the surface of the flat heat transfer tube 1 are aligned. The perforated plate 132 is provided with a plurality of holes 133 into which the flat heat transfer tubes 1 are inserted. With such a configuration, the gap between the side surface of the flat heat transfer tube and the step between the upper and lower sides can be filled, so that the step in the flow path can be reduced and the drift due to the disturbance of the refrigerant in the header can be prevented.

Example 9
FIG. 20 is a diagram illustrating the position of the partition plate of the header insertion member of Example 9 according to the second embodiment. As shown in FIG. 11A, the header 3a is configured to insert a header insertion member 34a into a header base member 31a. In (b-1), (b-2), and (b-3) of FIG. 20, the mounting height positions of the partition plate 35a and the perforated partition plate 36a with respect to the header insertion member 34a are changed. Thus, while the header base member 31a of the concave-shaped member is used in common, the refrigerant described above can be changed by changing the mounting position of the header insertion member 34a and the partition plate (for example, the partition plate 35a and the perforated partition plate 36a). The combination of the number of flat heat transfer tubes to flow can be set freely. As a result, it is possible to make adjustments at the design stage, such as differences in capability models and whether to prioritize the performance of the condenser or the evaporator.

According to the second embodiment, the refrigerant distribution to the flat heat transfer tubes of the parallel flow type heat exchanger can be made uniform, and the heat exchanger can be operated efficiently. Thereby, the energy-saving property of an air conditioner can be improved.

According to this embodiment, even during operation under a minimum load condition or an intermediate load condition, it is possible to suppress a deviation in the amount of liquid refrigerant supplied to each flat heat transfer tube in the parallel flow evaporator with a simple structure. Headers 3a, 3b, 3x, 3y can be provided. Therefore, the heat exchanger (the indoor heat exchanger 101, the outdoor heat exchanger 106) (see FIG. 44) having the header, the air conditioner AC (see FIG. 44) including the heat exchanger, and the air conditioning system can be realized.

<< Third Embodiment >>
Next, as examples (Examples 10 to 18) of the third embodiment, a heat exchanger 10A including a bypass pipe 40A (see FIG. 21) and the like (see FIG. 21) will be described. In addition, about the flat heat exchanger tube 1 and the fin 2 with which heat exchanger 10A is provided, since it is the same as that of 1st Embodiment, description is abbreviate | omitted.

(Example 10)
FIG. 21 is a front view of a heat exchanger 10A of Example 10 according to the third embodiment.
As shown in FIG. 21, the heat exchanger 10A includes a flat heat transfer tube 1, fins 2, headers 3c and 3d, a refrigerant inlet pipe 30, a refrigerant outlet pipe 33, and a bypass pipe 40A. .
The refrigerant inlet pipe 30 is a pipe that guides the refrigerant to the lower part of the narrow channel i1 (see FIG. 22A) of the header 3c. The refrigerant inlet pipe 30 is connected to the lower part of the header 3c, and the downstream end thereof faces the narrow channel i1 (see FIG. 22A).
The refrigerant outlet pipe 33 is a pipe through which the refrigerant merged in the header 3d passes through the plurality of flat heat transfer pipes 1 and is connected to the upper part of the other header 3d.

When the heat exchanger 10A functions as an evaporator, the refrigerant flows into the refrigerant inlet pipe 30, and when the heat exchanger 10A functions as a condenser, the refrigerant flows out of the refrigerant inlet pipe 30. It will be. That is, the term “refrigerant inlet pipe 30” is used to mean that the refrigerant flows into the refrigerant inlet pipe 30 in at least one of the operation modes such as air conditioning. The same applies to the refrigerant outlet pipe 33.

The bypass pipe 40 </ b> A is a pipe that guides the refrigerant that is branched to itself through the refrigerant inlet pipe 30 to the upper portion of the narrow channel i <b> 1 (see FIG. 22A), and is connected to the refrigerant inlet pipe 30.
The “refrigerant distributor” that distributes the refrigerant in the heat exchanger 10A includes a header 3c and a bypass pipe 40A.

FIG. 22A is a longitudinal sectional view of the vicinity of the header 3c in the heat exchanger 10A of Example 10 according to the third embodiment.
As shown in FIG. 22A, the header 3c is provided with a narrow channel i1 that is elongated in the vertical direction. Then, the refrigerant flowing into the narrow flow path i1 through the refrigerant inlet pipe 30 rises through the narrow flow path i1 (see the white arrow in FIG. 22A), and is further distributed to the plurality of flat heat transfer tubes 1. It has come to be.

In FIG. 22A, the configuration of the header 3c is illustrated in a simplified manner. However, as the header 3c, for example, the configuration of the first embodiment (see FIG. 5) or the second embodiment (for example, see FIG. 11B) is also used. Applicable. That is, as the header 3c, a structure in which the “first member” and the “second member” are combined with each other may be used. The same applies to other examples 11 to 18 which will be described later.

As shown in FIG. 22A, the bypass pipe 40A includes connection pipes 41 and 42 and has an L shape. One connecting pipe 41 extends in the vertical direction so as to be parallel to the extending direction of the header 3 c, and the lower end thereof is connected to the refrigerant inlet pipe 30. Further, a hole h <b> 1 that guides the refrigerant to the other connection pipe 42 is provided on the side surface near the upper end of the connection pipe 41.

The other connecting pipe 42 extends in the horizontal direction, one end thereof is connected to the hole h1 of the connecting pipe 41, and the other end is connected to the upper portion of the header 3c. A part of the refrigerant flowing through the refrigerant inlet pipe 30 is led to the upper part of the narrow flow path i1 via the bypass flow path i2 in the bypass pipe 40A.

The refrigerant inlet pipe 30 and the bypass pipe 40A are connected by brazing, for example. That is, the other pipe (for example, the bypass pipe 40A) is inserted into the hole on the side surface of the pipe having the larger diameter (for example, the refrigerant inlet pipe 30), and a brazing is performed at the connection location. Then, it is brazed together in a brazing furnace (not shown).

FIG. 22B is a cross-sectional view of the vicinity of the header 3c in the heat exchanger 10A of Example 10 according to the third embodiment. 22B is a cross-sectional view taken along line VV in FIG. 22A.
As shown in FIG. 22B, the narrow channel i1 provided in the header 3c has a rectangular cross section. Further, in the wall surface of the header 3c constituting the narrow channel i1, the distance L1 between the pair of first wall surfaces n1 and n1 perpendicular to the direction in which the flat heat transfer tube 1 extends is the remaining pair of second wall surfaces. It is preferable that the distance is shorter than the distance L2 between n2 and n2 (L1 <L2). More specifically, the above-described distance L1 is preferably 1 mm or more and 3 mm or less, and the distance L2 is preferably 10 mm or more and 20 mm or less. As a result, the flow rate of the refrigerant is increased in the process of the refrigerant rising in the narrow channel i1 having a relatively small cross-sectional area.

According to such a configuration, the plurality of refrigerant flow paths 12 provided in the flat heat transfer tube 1 and the narrow flow path i1 can be communicated with each other. Moreover, the speed of the refrigerant rising through the narrow channel i1 is increased by making the channel cross-sectional area of the narrow channel i1 relatively small. Therefore, the refrigerant is guided to the upper part of the header 3c by the momentum.

For example, when the heat exchanger 10A functions as an evaporator, the gaseous refrigerant blown upward through the narrow channel i1 and the refrigerant flowing through the bypass pipe 40A are above the narrow channel i1. Join at. A part of the refrigerant flowing into the narrow flow path i1 through the bypass pipe 40A flows into the flat heat transfer pipe 1 having a relatively high height, and the rest descends through the narrow flow path i1.

Thus, in the process in which the refrigerant that descends through the narrow channel i1 and the refrigerant that rises through the narrow channel i1 from the refrigerant inlet pipe 30 merge, a speed component that moves the refrigerant in the lateral direction is generated. As a result, the refrigerant easily flows into the flat heat transfer tube 1 whose height position is near the middle. Thereby, the drift of the refrigerant in the height direction is improved, and the refrigerant is distributed substantially evenly to the plurality of flat heat transfer tubes 1.

22A shows an example in which the number of the flat heat transfer tubes 1 connected to the header 3c is 14, but the number is not limited to this, and other numbers (for example, 8) may be used. In addition to the refrigerant inlet pipe 30, a bypass pipe 40 </ b> A may be installed in the refrigerant outlet pipe 33.

Further, the connection position of the downstream end of the bypass pipe 40A is not limited to the example of FIG. 22A. For example, a bypass pipe may be connected to the middle part of the header 3c (that is, near the middle position in the height direction) in the height direction. That is, a bypass pipe may be provided that guides the refrigerant that is branched to itself through the refrigerant inlet pipe 30 to the intermediate portion of the narrow channel i1 in the height direction. According to such a configuration, a large amount of refrigerant flows locally through the flat heat transfer tube 1 in the intermediate portion in the height direction. Therefore, in the wind speed distribution of the air flowing through the gaps between the fins 2 of the heat exchanger 10A, when the wind speed is high at the intermediate portion in the height direction of the heat exchanger 10A, the heat exchange of the refrigerant is performed by the above-described configuration. High efficiency can be achieved.

(Example 11)
FIG. 23 is a longitudinal sectional view of the vicinity of the header 3c in the heat exchanger 10B of Example 11 according to the third embodiment.
In the example shown in FIG. 23, the bypass pipe 40B includes connection pipes 41 and 42 and pipe joints 43 and 44. The connecting pipes 41 and 42 are connected in an L shape via the pipe joint 43. Further, the lower end of the bypass pipe 40 </ b> B and the refrigerant inlet pipe 30 are connected via another pipe joint 44.

According to such a configuration, it is possible to braze the entire heat exchanger 10B at once, and brazing in a state where the horizontal connection pipe 42 and the refrigerant inlet pipe 30 are connected to the header 3c. It is also possible to burn the vertical connecting pipe 41 later. Therefore, it becomes easy to connect each pipe while preventing interference with a housing (not shown) such as an outdoor unit. Thus, according to the eleventh embodiment, the degree of freedom when manufacturing the heat exchanger 10B is higher than that of the tenth embodiment.

(Example 12)
FIG. 24 is a longitudinal sectional view of the vicinity of the header 3c in the heat exchanger 10C of Example 12 according to the third embodiment.
As shown in FIG. 24, the bypass pipe 40C includes connection pipes 41C and 42. Further, the height position of the lower end of the bypass pipe 40 </ b> C is lower than the lower surface of the refrigerant inlet pipe 30. The configuration of such a bypass pipe 40C will be described with reference to FIG.

FIG. 25A is a side view of a connection pipe 41C of a bypass pipe included in the heat exchanger of Example 12 according to the third embodiment. That is, FIG. 25A is a side view taken along line VI-VI in FIG.
As shown in FIG. 25A, the connection pipe 41 </ b> C included in the bypass pipe 40 </ b> C (see FIG. 24) has a U-shaped bent portion 411 </ b> C in the vicinity of the connection portion with the refrigerant inlet pipe 30. The bent portion 411 </ b> C includes a portion whose height is lower than that of the refrigerant inlet pipe 30, and is connected to the lower surface of the refrigerant inlet pipe 30.

Furthermore, the connecting pipe 41C has another bent part 412C at the intermediate part in the height position so that the position of the connecting pipe 42 (see FIG. 24) in the horizontal direction is directly above the refrigerant inlet pipe 30. Yes. Such a connecting pipe 41C is formed by bending a straight pipe.

FIG. 25B is an explanatory diagram illustrating a cross section of the refrigerant inlet pipe 30 when the refrigerant circulation amount is relatively large in the heat exchanger of Example 12 according to the third embodiment.
When the circulation amount of the refrigerant is relatively large and the flow velocity is high, the refrigerant flows through the refrigerant inlet pipe 30 in a so-called annular flow mode. That is, liquid refrigerant flows near the inner wall surface of the refrigerant inlet pipe 30, while gas refrigerant (or gas-liquid two-phase refrigerant) flows near the center of the cross section of the refrigerant inlet pipe 30.

When the refrigerant is flowing in such an annular flow, the liquid refrigerant flows substantially uniformly in the circumferential direction of the refrigerant inlet pipe 30. Therefore, for example, even if the bypass pipe 40A is connected to the upper surface of the refrigerant inlet pipe 30 (Example 10: see FIG. 21), or the bypass pipe 40C is connected to the lower surface of the refrigerant inlet pipe 30 (this book (Example 12: See FIG. 25A), the refrigerant is appropriately guided to the bypass pipe.

FIG. 25C is an explanatory diagram illustrating a cross section of the refrigerant inlet pipe 30 when the refrigerant circulation amount is relatively small in the heat exchanger of Example 12 according to the third embodiment.
When the circulation amount of the refrigerant is relatively small and the flow rate is low, the refrigerant flows through the refrigerant inlet pipe 30 in a so-called laminar flow or wave flow. That is, the liquid refrigerant flows in the lower part of the refrigerant inlet pipe 30 under the influence of gravity.

Here, in the heat exchanger 10C (see FIG. 24) of the twelfth embodiment, as described above, the upstream end of the bent portion 411C of the bypass pipe 40C (see FIG. 24) is connected to the lower surface of the refrigerant inlet pipe 30. ing. Therefore, even when the flow rate of the refrigerant is low, the liquid refrigerant flows into the U-shaped bent portion 411C due to gravity. Then, the liquid refrigerant that has flowed into the bent portion 411C rises in a mist form while accompanying the gas refrigerant blown up through the bypass pipe 40C. Therefore, according to the twelfth embodiment, the liquid refrigerant is appropriately guided to the upper part of the header 3c (see FIG. 24) even in a situation where the circulation amount of the refrigerant is small.

(Example 13)
FIG. 26 is a longitudinal sectional view of the vicinity of the header 30c in the heat exchanger 10D of Example 13 according to the third embodiment.
The refrigerant inlet pipe 30 shown in FIG. 26 is a pipe that guides the refrigerant to the upper part of the narrow flow path i1, and is connected to the upper part of the header 3c. The bypass pipe 40D is a pipe that guides the refrigerant that is branched to itself through the refrigerant inlet pipe 30 to the lower portion of the narrow channel i1 in the height direction. The bypass pipe 40D has a configuration in which a connection pipe 41 extending in the vertical direction and a connection pipe 42 extending in the horizontal direction are connected in an L shape. The upstream end of the bypass pipe 40D (the upper end of the connection pipe 41) is connected to the refrigerant inlet pipe 30, and the downstream end is connected to the lower part of the header 3c.

According to such a configuration, a part of the refrigerant flowing through the refrigerant inlet pipe 30 is guided to the upper part of the narrow channel i1 of the header 3c. Further, the remaining refrigerant flowing through the refrigerant inlet pipe 30 is lowered via the bypass pipe 40D and further blown up through the narrow flow path i1. Thus, in the process in which the refrigerant blown up through the narrow channel i1 and the refrigerant descending from the refrigerant inlet pipe 30 through the narrow channel i1 are joined, a speed component that moves the refrigerant in the lateral direction is generated. As a result, the refrigerant easily flows into the flat heat transfer tube 1 whose height position is near the middle.

Further, according to the thirteenth embodiment, a relatively large amount of refrigerant is supplied to the upper flat heat transfer tube 1 through the refrigerant inlet tube 30 while guiding the refrigerant to the flat heat transfer tube 1 near the middle of the height position or the lower flat heat transfer tube 1. It can be circulated. Therefore, when the wind speed of the air flowing through the upper part of the heat exchanger 10D is relatively high, the configuration of the thirteenth embodiment is particularly effective.

In addition, the connection position of the downstream end of the bypass pipe 40D is not limited to the example of FIG. For example, the bypass pipe 40D may be connected to the intermediate part of the header 3c so that the refrigerant flowing through the bypass pipe 40D is guided to the intermediate part of the narrow channel i1 in the height direction.

In addition, although not shown, instead of the configuration of FIG. 26, one end is connected to the refrigerant inlet pipe 30, and the other end side is provided with a bypass pipe that is branched into a plurality so as to have different height positions. May be. In the above-described bypass pipe, the flow paths on the other end side branched into a plurality are each in communication with the narrow flow path i1. For example, a part of the refrigerant flowing through the refrigerant inlet pipe 30 connected to the upper part of the header 3c is divided into two via the bypass pipe and guided to the lower part and the middle part of the narrow channel i1. You may be allowed to be. According to such a configuration, the refrigerant is appropriately distributed in the height direction based on the wind speed distribution and the like of the air flowing through the gaps of the fins 2.

(Example 14)
FIG. 27A is a longitudinal sectional view in the vicinity of the header 3E in the heat exchanger 10E of Example 14 according to the third embodiment.
As shown in FIG. 27A, the heat exchanger 10E includes a plate-like partition member 45 that partitions the space in the header 3E into a narrow channel i1 and a bypass channel i2. The partition member 45 is an elongated rectangular plate, and is disposed in the header 3E so that the plate surface is parallel to the vertical direction.

27A, of the two spaces partitioned by the partition member 45, the space on the flat heat transfer tube 1 side functions as the narrow flow path i1, and the space on the opposite side functions as the bypass flow path i2. In the partition member 45, a hole h31 (first hole) is provided at a position (lower part) corresponding to the connection location of the refrigerant inlet pipe 30. A refrigerant inlet pipe 30 is inserted into the hole 31. The refrigerant is guided to the narrow flow path i1 through the refrigerant inlet pipe 30.

Further, a hole h32 for guiding the refrigerant to the bypass flow path i2 is provided on the upper surface near the downstream end of the refrigerant inlet pipe 30. In addition, a hole h4 (second hole) is provided in the upper part of the partition member 45. The narrow channel i1 and the bypass channel i2 communicate with each other through the hole h4.

As described above, in the partition member 45, the hole h31 (first hole) is provided at the connection point with the refrigerant inlet pipe 30 that guides the refrigerant to the narrow flow path i1, and the hole h31 has a height different from that of the hole h31. h4 (second hole) is provided. A part of the refrigerant flowing through the refrigerant inlet pipe 30 is led to the flat heat transfer pipe 1 through the hole h32, the bypass flow path i2, the hole h4, and the narrow flow path i1 sequentially. .

According to such a configuration, the diameters of the holes 31 and the holes h4 of the partition member 45 are appropriately adjusted at the design stage based on pressure loss and the like when the refrigerant flows through the holes h31 and h4. Has been. Thereby, the flow rate of the refrigerant flowing through the narrow channel i1 and the flow rate of the refrigerant flowing through the bypass channel i2 can be adjusted. Further, the structure of the heat exchanger 10E can be simplified and made compact.

FIG. 27B is a cross-sectional view of the vicinity of the header 3E in the heat exchanger 10E of Example 14 according to the third embodiment. 27B is a cross-sectional view taken along the line VII-VII in FIG. 27A.
In the example shown in FIG. 27B, each of the narrow channel i1 and the bypass channel i2 has a rectangular shape in a cross-sectional view. Moreover, although the cross-sectional area of the narrow flow path i1 is larger than the bypass flow path i2, this magnitude relationship may be reversed.

In addition to the configuration shown in FIGS. 27A and 27B, for example, the refrigerant inlet pipe 30 may be connected to the top of the header 3E. And the hole h31 may be provided in the position corresponding to the connection location of the refrigerant inlet pipe 30 in the partition member 45, and the hole h4 may be provided in the lower part (or intermediate part) of the partition member 45.

(Example 15)
FIG. 28A is an exploded perspective view of the header 3F included in the heat exchanger of Example 15 according to the third embodiment when viewed from the opposite side of the refrigerant inlet pipe 30. FIG.
In addition, the side to which the refrigerant inlet pipe 30 is connected in the header 3F is referred to as “one side”, and the opposite side is referred to as “the other side”. As shown in FIG. 28A, the header 3F includes a first plate 31F (entrance side plate), a second plate 32F (second member), a third plate 33F (first member), and a first plate. The four plate-like bodies 34F are sequentially stacked. These plate-like bodies 31F to 34F are elongated rectangular metal plates provided with predetermined refrigerant flow paths.

The first plate-like body 31F is a plate-like body in which a first refrigerant flow hole h7 is provided at a location corresponding to the refrigerant inlet pipe 30. A refrigerant inlet pipe 30 is connected to one side of the first plate-like body 31F (see also FIG. 28B). In the vicinity of the upper and lower ends of the first plate-like body 31F, horizontally long insertion holes h5 and h6 into which the partition plates 35 and 36 are inserted are provided.

The second plate-like body 32F forms a bypass channel (not shown) between itself and the first plate-like body 31F, and a narrow channel (not shown) between itself and the third plate-like body 33F. It is a plate-shaped body for forming (not shown). The second plate-like body 32F is stacked on the other side of the first plate-like body 31F.

As shown in FIG. 28A, the second plate-like body 32F includes a flat plate portion 321, a first convex portion 322, a pair of second convex portions 323 and 323, and a pair of engaging portions 324 and 324. These are integrally formed.
The flat plate portion 321 is an elongated rectangular thin plate portion having a flat plate surface.
The 1st convex part 322 is a part abutted by the end surface of one side of the flat heat exchanger tube 1 (refer FIG. 28C), and protrudes from the flat plate part 321 to the other side. This 1st convex part 322 is provided in the center of the width direction of the 2nd plate-shaped body 32F, and is extended in the height direction.

FIG. 28B is an exploded perspective view of the header 3F included in the heat exchanger of Example 15 according to the third embodiment when viewed from the refrigerant inlet pipe 30 side.
As shown in FIG. 28B, the pair of second convex portions 323 and 323 protrude from the flat plate portion 321 to one side and extend in the height direction. Moreover, the front-end | tip of the 2nd convex part 323,323 is abutted on the surface of the other side of the 1st plate-shaped body 31F (entrance side plate-shaped body). That is, the pair of second convex portions 323 and 323 has a function of forming the above-described “bypass channel” while keeping the distance between the first plate-like body 31F and the second plate-like body 32F constant. is doing.

Between the pair of second convex portions 323 and 323, a second refrigerant flow hole h <b> 8 through which the refrigerant flows is provided on the upper portion of the flat plate portion 321. In addition, another second refrigerant flow hole h9 through which the refrigerant flows is provided between the pair of second convex portions 323 and 323 at the lower portion of the flat plate portion 321. Note that a configuration in which a “second refrigerant flow hole” is provided in at least one of the upper part and the lower part of the flat plate part 321 may be employed.

And the refrigerant | coolant which flows through the clearance gap between the groove | channel u1 (refer FIG. 28C) between a pair of 2nd convex parts 323 and 323, and the other side surface of the 1st plate-shaped body 31F is 2nd refrigerant | coolant. It is led to the “narrow channel” through the flow holes h8 and h9. The above-mentioned “narrow channel” is a gap between the second plate-like body 32F and the third plate-like body 33F.

The pair of engaging portions 324 and 324 included in the second plate-like body 32F are portions that engage with the step portions t1 and t1 of the third plate-like body 33F, and protrude from the flat plate portion 321 to the other side. The pair of engaging portions 324 and 324 are provided at one end at both ends in the width direction of the second plate-like body 32F and extend in the height direction.

FIG. 28C is an exploded view of the header 3 </ b> F cut in a cross section including the flat heat transfer tube 1 in the header 3 </ b> F included in the heat exchanger of Example 15 according to the third embodiment when viewed from directly above.
As shown in FIG. 28C, the first convex portion 322 is provided between the pair of engaging portions 324 and 324 in the width direction (up and down direction in FIG. 28C), and has a triangular shape in plan view. And the front-end | tip of the 1st convex part 322 is abutted by the end surface of the one side of the flat heat exchanger tube 1. FIG.

If it demonstrates from another viewpoint, two groove | channels u2 and u2 are formed between a pair of engaging parts 324,324 and the 1st convex part 322. FIG. And the clearance gap between the 3rd plate-shaped body 33F and groove | channel u2, u2 functions as a narrow flow path (not shown) for guiding a refrigerant | coolant. As described above, the gap between the one side surface of the third plate-like body 33F (first member) and the other side surface of the second plate-like body 32F (second member) is “a narrow channel”. "(: Not shown).

Also, a projection surface M1 (FIG. 28B) when the first refrigerant flow hole h7 (see FIG. 28A) of the first plate-like body 31F (inlet side plate-like body) is projected onto the second plate-like body 32F (second member). Reference) has a plate surface on one side of the second plate-like body 32F. As a result, the refrigerant traveling toward the second plate-like body 32F through the first refrigerant flow hole h7 collides with the plate surface on one side of the second plate-like body 32F and diffuses. Therefore, the refrigerant is easily distributed evenly in the height direction.
The above-mentioned “projection” means that the region of the first refrigerant flow hole h7 is moved (projected) on the plate surface of the second plate-like body 32F in the axial direction of the refrigerant inlet pipe 30. .

The third plate-like body 33F (first member) is a plate-like body laminated on the other side of the second plate-like body 32F (second member). The third plate 33F is provided with eight holes h10 through which the flat heat transfer tubes 1 are inserted at predetermined intervals in the height direction. Similarly, eight holes h11 through which the flat heat transfer tubes 1 are inserted are also provided in the fourth plate-like body 34F.

As shown by the arrows in FIGS. 28A and 28B, the refrigerant that has collided and diffused on the projection surface M1 of the second plate-like body 32F is divided into upper and lower parts, and the first plate-like body 31F and the second plate-like body are separated. It flows through a gap (bypass channel: not shown) between the body 32F. The refrigerant flowing upward through the bypass channel flows into the upper flat heat transfer tube 1 (see FIG. 28C) through the second refrigerant flow hole h8 on the upper side of the second plate-like body 32F.

On the other hand, the refrigerant flowing downward through the bypass channel (not shown) passes through the second plate 32F and the third plate through the second refrigerant flow hole h9 on the lower side of the second plate 32F. It flows into a gap (narrow channel: not shown) between the cylindrical bodies 33F. In the process of ascending the narrow channel having a relatively small channel cross-sectional area, the refrigerant is appropriately distributed to the lower, middle, and upper flat heat transfer tubes 1. As described above, according to the fifteenth embodiment, the drift of the refrigerant in the height direction is improved, and the refrigerant is distributed substantially evenly to the plurality of flat heat transfer tubes 1.

Further, according to the fifteenth embodiment, since the first plate-like body 31F, the second plate-like body 32F, the third plate-like body 33F, and the fourth plate-like body 34F are sequentially laminated, the lamination The thickness of the header 3F in the direction becomes relatively thin. Therefore, the header 3F can be made compact. In addition, since the four plate-like bodies described above may be laminated and brazed together, labor and cost required for manufacturing the header 3F can be reduced.

(Example 16)
FIG. 29A is an exploded perspective view of the header 3G included in the heat exchanger of Example 16 according to the third embodiment when viewed from the opposite side of the refrigerant inlet pipe 30. FIG.
The header 3G shown in FIG. 29A includes a first plate 31G (inlet side plate), a second plate 32G (second member), a third plate 33G (first member), and a fourth plate. 34G and the 5th plate-shaped body 35G are the structures laminated | stacked sequentially. These plate-like bodies 31G to 35G are elongated rectangular metal plates provided with predetermined refrigerant flow paths.

The configurations of the first plate-like body 31G, the fourth plate-like body 34G, and the fifth plate-like body 35G in Example 16 are in this order, and the first plate-like body 31F in Example 15 (see FIG. 28A). The third plate-like body 33F and the fourth plate-like body 34F are the same. Therefore, in Example 16, description of the first plate-like body 31G, the fourth plate-like body 34G, and the fifth plate-like body 35G is omitted, and the remaining second plate-like body 32G and third plate-like body 33G are omitted. explain.

As shown in FIG. 29A, the second plate-like body 32G includes a flat plate portion 321, a first convex portion 322, and a pair of engaging portions 324, 324, which are integrally formed. Since the flat plate portion 321, the first convex portion 322, and the pair of engaging portions 324 and 324 are the same as those in the fifteenth embodiment (see FIG. 28A), the description thereof is omitted.

As shown in FIG. 29A, the surface on one side of the second plate-like body 32G is flat. That is, in the sixteenth embodiment, the pair of second convex portions 323 and 323 (see FIG. 28A) described in the fifteenth embodiment is not provided. Then, the other plate surface of the first plate-like body 31G and the one plate surface of the second plate-like body 32G are brazed.

In the second plate-like body 32G, a hole h12 is provided at a location corresponding to the first refrigerant flow hole h7 of the first plate-like body 31G. The hole h12 allows the refrigerant flowing from the refrigerant inlet pipe 30 via the first refrigerant flow hole h7 to pass through the second plate body 32G (second member) and the third plate body 33G (first member). It is a hole for leading to a gap (narrow channel) between the two.

FIG. 29B is an exploded perspective view of the header 3G included in the heat exchanger of Example 16 according to the third embodiment when viewed from the refrigerant inlet pipe 30 side.
As shown in FIG. 29B, in the third plate-like body 33G, projection surfaces corresponding to the first refrigerant flow holes h7 (see FIG. 29A) of the first plate-like body 31G and the holes h12 of the second plate-like body 32G. M2 has a plate surface on one side of the third plate-like body 33G. And the refrigerant | coolant which flows through the 1st refrigerant | coolant flow hole h7 (refer FIG. 29A) and the hole h12 sequentially collides with the above-mentioned projection surface M2, and is spread | diffused.

In the third plate 33G, flat holes h13 are provided at locations corresponding to the upper six of the eight flat heat transfer tubes 1 (see FIG. 29C). In addition, in the third plate-like body 33G, a rectangular recess u3 (see FIG. 29A) that is recessed on one side when viewed from the other side is provided at a location corresponding to the two lower flat heat transfer tubes 1 (see FIG. 29C). Reference) is provided. The projection surface M2 (see FIG. 29B) exists on the back surface (one surface) of the recess u3.

And the refrigerant | coolant which flows through the clearance gap (narrow channel) between the 2nd plate-shaped body 32G and the 3rd plate-shaped body 33G passes through the upper six holes h13, and the one part is recessed part u3 and 4th. It descends through a gap between the plate-like body 34G. Further, the refrigerant flowing into the gap between the recess u3 and the fourth plate-like body 34G is guided to the two lower flat heat transfer tubes 1.

FIG. 29C is an exploded view of the header 3 </ b> G provided in the heat exchanger of Example 16 according to the third embodiment when the header 3 </ b> G cut along the cross section including the flat heat transfer tube 1 is viewed from directly above.
As shown in FIG. 29C, the first convex portion 322 has a tip abutted against one end face of the flat heat transfer tube 1. As in the fifteenth embodiment, a pair of grooves u2 and u2 through which the refrigerant flows are formed between the first convex portion 322 and the pair of engaging portions 324 and 324.

According to the sixteenth embodiment, in the configuration in which the first plate-like body 31G and the second plate-like body 32G are in close contact, the refrigerant collides with the projection surface M2 (see FIG. 29B) of the third plate-like body 33G. The refrigerant after diffusion can be appropriately distributed to each flat heat transfer tube 1.

(Example 17)
FIG. 30 is a front view of the heat exchanger 10H of Example 17 according to the third embodiment.
In the example shown in FIG. 30, the header 3H has a configuration in which two headers 3c (see FIG. 21) of the tenth embodiment are stacked and integrated in the vertical direction. And the partition plate N which partitions the narrow flow path i1 inside the header 3H up and down is provided in the intermediate position of the header 3H in the height direction.

Further, the refrigerant inlet pipe 30 and the bypass pipe 40A similar to those of the tenth embodiment are connected to the upper side of the partition plate N in the header 3H. Similarly, the refrigerant inlet pipe 30 and the bypass pipe 40A are also connected to the lower side of the partition plate N in the header 3H. And the refrigerant | coolant guide | induced to the flat heat exchanger tube 1 via the header 3H is guide | induced to the refrigerant | coolant exit pipe | tube 33 via the downstream header 3H and the connecting pipe 46 sequentially.

According to such a configuration, by integrally forming the header 3H, the number of parts can be reduced as compared with the tenth embodiment (see FIG. 21), and the rigidity of the heat exchanger 10H can be increased. Moreover, since the vertically long fins 2 are integrally formed, there is almost no possibility of impairing the drainage of condensed water.

(Example 18)
FIG. 31 is a perspective view showing an external configuration of a heat exchanger K3 of Example 18 according to the third embodiment.
A heat exchanger K3 shown in FIG. 31 includes a plurality of flat heat transfer tubes 1, a plurality of fins 2, headers 3x and 3y, and a bypass tube 40A. This heat exchanger K3 has a configuration in which the bypass pipe 40A of Example 10 (see FIG. 21) of the third embodiment is connected to the header 3y of the first embodiment (see FIG. 1).

That is, the refrigerant is placed below the narrow channel 38 (see FIG. 5) between the flat tube side header member 31x (first member: see FIG. 5) and the combined header member 34x (second member: see FIG. 5). A bypass pipe 40A is connected to the refrigerant inlet pipe 30 that guides the refrigerant. The bypass pipe 40A has a function of guiding the refrigerant that is branched to itself through the refrigerant inlet pipe 30 to the upper part (or intermediate part) of the narrow channel 38 in the height direction. According to such a configuration, the refrigerant can be distributed substantially uniformly to each of the plurality of flat heat transfer tubes 1 arranged in the vertical direction.

In addition to Example 10, the configurations of Examples 11 to 14 and 17 are applicable to the first embodiment (see FIG. 1), and also applicable to the second embodiment (see FIG. 11B and the like). Is possible. For example, a plate-like partition that applies Example 14 to the first embodiment and divides the space between the “first member” and the “second member” into a narrow channel i1 and a bypass channel i2. The member 45 may be provided.

Further, the wall surface of the flat tube side header member 31x (first member: see FIG. 5) constituting the narrow flow path 38 (see FIG. 5) of the heat exchanger K3, and the combined header member 34x (second member: FIG. 5). It is preferable that the following relationship is established on the wall surface of (see). That is, the distance between the pair of first wall surfaces perpendicular to the direction in which the flat heat transfer tube 1 extends is 1 mm or more and 3 mm or less, and the distance between the remaining pair of second wall surfaces is 10 mm or more and It is preferable that it is 20 mm or less. According to such a configuration, it is possible to increase the flow rate of the refrigerant that rises through the narrow channel 38 having a relatively small channel cross-sectional area.

<< First Reference Form >>
FIG. 32 is a perspective view of the heat exchanger K according to the first reference embodiment.
The heat exchanger K is a parallel flow type heat exchanger. The heat exchanger K includes headers 5x and 5y, a plurality of flat heat transfer tubes 1, and a large number of fins 2.

That is, the heat exchanger K includes a heat exchanger core portion Kc having a plurality of flat heat transfer tubes 1 and a large number of fins 2 and headers 5x and 5y.
A plurality of flat heat transfer tubes 1 are provided in the vertical direction.

The headers 5x and 5y are members for distributing the refrigerant flowing into the flat heat transfer tubes 1 arranged in the vertical direction, or for joining the refrigerant flowing out from the flat heat transfer tubes 1, and have a vertically long shape. ing.

For example, as shown by the arrows in FIG. 32, when the refrigerant is flowing into one header 5y, the refrigerant is distributed from the header 5y to each flat heat transfer tube 1. And the refrigerant | coolant which flows out from each flat heat exchanger tube 1 merges by the other header 5x. Alternatively, when the refrigerant flows into the other header 5x, the refrigerant is distributed from the header 5x to each flat heat transfer tube 1, and the refrigerant flowing out from each flat heat transfer tube 1 merges in one header 5y.

<Configuration of header 5x>
Since the header 5x and the header 5y are symmetrical and have the same configuration, the configuration of the header 5x will be described, and the description of the configuration of the header 5y will be omitted.

FIG. 33 is a perspective view of the vicinity of the header 5x of the heat exchanger K according to the first reference embodiment as viewed obliquely from above.
The header 5 x includes a duct 51, a uchi header 52, and a soto header 53.

< Partition plates 14a and 14b>
A partition plate 14a is provided above the uppermost flat heat transfer tube 1 among the plurality of flat heat transfer tubes 1 of the header 5x. Moreover, the partition plate 14b is provided below the lowest flat heat exchanger tube 1 among the several flat heat exchanger tubes 1 of the header 5x.

34A is an exploded perspective view of the header 5x of the heat exchanger according to the first reference embodiment, and FIG. 34B is a view in the direction of arrow VII of the duct 51 in FIG. 34A.
Each of the partition plates 14a and 14b is formed in a plate shape with a sheet metal.

The partition plate 14a has a rectangular insertion portion 14a1 and a stopper portion 14a2 protruding outward. Similarly, the partition plate 14b has a rectangular insertion portion 14b1 and a stopper portion 14b2 protruding outward.
The insertion portions 14a1 and 14b1 contact and seal the inner surface of the soto header 53, the inner surface of the duct 51, and the inner surface of the uchi header 52, respectively.

Thereby, the partition plates 14a and 14b suppress the outflow of the refrigerant inside each of the duct 51, the uchi header 52, and the soto header 53 to the outside. In addition, the partition plates 14 a and 14 b suppress external air from flowing into the duct 51, the uchi header 52, and the soto header 53.

<Duct 51>
The duct 51 shown in FIGS. 33 and 34A is a refrigerant distribution member through which the refrigerant flows into the flat heat transfer tube 1 or from which the refrigerant flows out.
The duct 51 has a shape that is long in the vertical direction and has a flat cross section. The duct 51 is formed by sheet metal or extrusion using, for example, an aluminum or aluminum alloy plate.

35A is a view taken in the direction of arrow VIII in FIG. 32, FIG. 35B is a cross-sectional view taken along the line IX-IX in FIG. 35A, and FIG. 35C is an enlarged view of a portion Q1 in FIG.

36A is a top view of the heat exchanger K according to the first reference embodiment, FIG. 36B is a cross-sectional view taken along the line XI-XI in FIG. 36A, and FIG. 36C is an enlarged view of the Q2 part in FIG. 36B.

As shown in FIGS. 35C and 36B, the duct 51 is formed with a flow passage hole 51a through which a refrigerant flows in the vertical direction.
The channel hole 51a has a flat rectangular cross section (FIGS. 35C and 36A) so that the cross-sectional area becomes small in order to form a narrow channel part.

When the refrigerant passes through the channel hole 51a inside the duct 51, the channel hole 51a is a narrow channel and has a small cross-sectional area, so that the volume in the length direction is large and the flow velocity is large.

As shown in FIG. 36C, the duct 51 is continuous with the flow path hole 51a through the opening 51b with respect to the refrigerant flow path 12 (also referred to as a through hole) of each flat heat transfer tube 1. As shown in FIG. 36B, the duct 51 has the same number of openings 51 b as the flat heat transfer tubes 1.
35C, the width dimension s2 of the opening 51b of the duct 51 is set to be less than the width dimension s1 of the flat heat transfer tube 1.

As shown in FIG. 36C, the opening 51b has a height dimension s4 that is smaller than the thickness dimension s3 of the flat heat transfer tube 1. Then, as shown in FIGS. 35C and 36C, the flat heat transfer tube 1 is applied to the opening 51 b of the duct 51 to position the flat heat transfer tube 1 with respect to the duct 51.

As shown in FIGS. 34A and 34B, insertion holes 51c1 and 51c2 through which the insertion portions 14a1 of the upper partition plate 14a pass are formed in the upper portion of the duct 51. In the lower part of the duct 51, insertion holes 51c3 and 51c4 through which the insertion part 14b1 of the lower partition plate 14b passes are formed. Accordingly, the partition plates 14 a and 14 b can be inserted into the soto header 53 and the duct 51.

<Ouchi Header 52>
33 is a member for fixing a plurality of flat heat transfer tubes 1 to the duct 51.

As shown in FIG. 34A, the pouch header 52 is a member having a flat, substantially U-shaped cross section and a shape that is long in the vertical direction. The pouch header 52 is formed of sheet metal using, for example, aluminum or an aluminum alloy plate.
The pouch header 52 has a center plate 52c and a side plate 52a and a side plate 52b continuous to the side edges of the center plate 52c.

An insertion hole 52 d through which each flat heat transfer tube 1 is inserted is formed in the central plate 52 c of the header header 52. That is, the same number of insertion holes 52 d as the flat heat transfer tubes 1 are formed in the center plate 52 c of the uchi header 52.
Since the flat heat transfer tube 1 is inserted, the insertion hole 52d has a size slightly larger than the outer diameter of the flat heat transfer tube 1. The insertion hole 52d is formed, for example, such that the direction of the burr is directed to the direction in which the flat heat transfer tube 1 is inserted by burring.

The width dimension s5 of the header header 52 (FIG. 34A) is formed to be substantially the same as the width dimension s6 of the duct 51 (FIG. 34A). Thereby, as shown in FIG. 35C, the header header 52 and the duct 51 can be fixed by the soto header 53.

<Soto Header 53>
As shown in FIGS. 33 and 35C, the soto header 53 is a member for abutting and fixing the flat heat transfer tube 1 to the duct 51 together with the uchi header 52.

As shown in FIG. 34A, the soto header 53 is a member that has a substantially M-shaped cross section and is long in the vertical direction. The soto header 53 is formed of sheet metal using, for example, an aluminum or aluminum alloy plate.
The soto header 53 has a center plate 53a having a recessed center and a pair of flat side plates 53b and 53c that are continuous with both side ends of the center plate 53a. The center plate 53a has a bent portion 53am formed at the center, and a top line 53a1 (see FIG. 35C) that forms the apex of a recess having a substantially M-shaped cross section extends in the vertical direction and is formed in a straight line. Yes.

As shown in FIG. 34A, the dimension s7 between the side plates 53b and 53c of the soto header 53 is set slightly larger than the width dimension s6 of the duct 51 (FIG. 34A) and the width dimension s5 of the uchi header 52 (FIG. 34A).
In this way, the soto header 53 does not have a simple rectangular structure, but has a substantially M-shaped cross section, is in contact with both the short side surfaces 51s1 and 51s2 (FIG. 34A) of the duct 51, and the long side surface 51s3 (see FIG. 34A) is a configuration (FIG. 35C) in which at least one point (the top line 53a1) is in contact with the cross section.

Thus, as shown in FIG. 35C, when the duct 51 and the soto header 53 are assembled, the duct 51 does not contact the bent R portions 53r1 and 53r2 of the soto header 53. Therefore, the duct 51 and the soto header 53 can be accurately positioned.

As shown in FIG. 34A, the soto header 53 is formed with a partition plate insertion hole 53d into which the partition plate 14a is inserted in order to partition the header in the vertical direction to determine the flow path pattern of the specific refrigerant and to form a space. ing. The stopper portion 14a2 of the partition plate 14a is fitted into the partition plate insertion hole 53d. In addition, a partition plate insertion hole 53e into which the partition plate 14b is inserted is formed in the lower portion of the soto header 53. The stopper part 14b2 of the partition plate 14b is fitted into the partition plate insertion hole 53e.

It is desirable that the duct 51, the uchi header 52, and the soto header 53 have the same material or substantially the same thermal conductivity. This is to prevent brazing defects caused by uneven heating due to differences in thermal conductivity and heat capacity when brazing in a furnace is performed during manufacturing. Therefore, as described above, the duct 51, the uchi header 52, and the soto header 53 are formed using aluminum or an aluminum alloy. In addition, you may form the duct 51, the uchi header 52, and the soto header 53 with another metal.

<Example of manufacturing method of heat exchanger K>
Next, an example of the manufacturing method of the heat exchanger K is demonstrated. In addition, you may assemble by methods other than the following.

A brazing material is applied to the outer surface 52a1 of the side plate 52a and the outer surface 52b1 of the side plate 52b of the edge header 52 shown in FIG. 34A. Further, the inner surface 53b1 of the side plate 53b of the soto header 53 and the inner surface 53c1 of the side plate 53c are joined by welding such as brazing.
Further, the plurality of flat heat transfer tubes 1 and a large number of fins 2 are joined by welding such as brazing. For these joining, it is preferable to select a brazing material layer on the surface of one member because brazing in the furnace can be selected.

The flat heat transfer tube 1 and the insertion holes 52d of the header header 52 on the header 5x side and the flat heat transfer tube 1 are joined by welding such as brazing. It is desirable to select aluminum or aluminum alloy having a brazing material layer on the outer surface side of the center header 52c or the side plate 52b when the edge header 52 is processed from a plate material. Here, since no brazing material is attached to the duct 51, it is possible to avoid the wax from closing the opening 51b of the duct 51 and the hole h of the flat heat transfer tube 1.

Then, the uchi header 52 and the duct 51 are brought into contact with each other, and the soto header 53 is brought into contact with the uchi header 52 and the duct 51 from the outside.
Then, the flat heat transfer tubes 1 through which a large number of fins 2 are inserted are inserted into the respective insertion holes 52d of the uchi header 52, and are brought into contact with the openings 51b of the duct 51 so that the refrigerant flows (FIG. 36C).

As with the header 5x, the header 5y and the flat heat transfer tube 1 through which a large number of fins 2 are inserted are assembled.
In this way, the heat exchanger is assembled in the state of the heat exchanger K shown in FIG. 32, placed in a furnace, heated and brazed.
Thereafter, the upper partition plate 14a and the lower partition plate 14b are inserted into the insertion holes 51c1 and 51c2 and the insertion holes 51c3 and 51c4 on the header 5x side and the header 5y side, whereby the heat exchanger K shown in FIG. Is completed.

According to the above configuration, the number of parts of the headers 5x and 5y can be configured by four types including the partition plates 14a and 14b, the duct 51, the uchi header 52, and the soto header 53. That is, the number of parts is hardly increased to improve refrigerant distribution.

By increasing the refrigerant flow rate by the duct 51 having the channel hole 51a of the narrow channel part, the refrigerant can smoothly flow to the upper part even when gravity works, so that the distribution of the refrigerant can be improved. The duct 51 comes into contact with the bent R portions 53r1 and 53r2 of the soto header 53 by adopting a configuration in which the shape of the M-shaped soto header 53 is made substantially M-shaped on the duct 51 and the top line 53a1 abuts against the duct 51. This can avoid the positioning of the header header 52, the duct 51, the soto header 53, and the flat heat transfer tube 1.

That is, the header 5x, 5y can be positioned by making the Soto header 53 M-shaped. With this configuration, it is possible to obtain the positional accuracy of the headers 5x and 5y without increasing extra space in the headers 5x and 5y.
Further, since the flat heat transfer tube 1 is used as the heat transfer tube, the heat exchange efficiency can be increased.

From the above, it is possible to provide the headers 5x and 5y which are refrigerant distributors that are excellent in refrigerant distribution and save the members and have assemblability.
Therefore, it is possible to realize a heat exchanger K (FIG. 31) having a header type refrigerant distributor ( headers 5x, 5y) having a simple structure and cost-saving and having good distribution, and an air conditioner including the same.

<< Modification of the first reference form >>
FIG. 37 is a perspective view showing a heat exchanger K10 according to a modification of the first reference embodiment.
The heat exchanger K10 according to the modified example includes two heat exchangers K described in the first reference embodiment.

Since the configuration other than this is the same as that of the first reference embodiment, the same components are denoted by the same reference numerals, and detailed description thereof is omitted.
The heat exchanger K10 includes a first heat exchanger K11 and a second heat exchanger K12 having the same configuration as the heat exchanger K of the first reference embodiment.

The first heat exchanger K11 includes a header 5x1 having the same configuration as the header 5x and a header (not shown) having the same configuration as the header 5y.
The header 5 x 1 includes a duct 51, a uchi header 52, and a soto header 53. Partition plates 14a and 14b are inserted and sealed in the upper and lower portions of the header 5x1, respectively.

The flat heat transfer tube 1 including a large number of fins 2 is abutted against an opening (not shown) of a duct 51. As a result, the refrigerant can travel to the duct 51 through the flat heat transfer tube 1.
The second heat exchanger K12 includes a header 5x2 having the same configuration as the header 5x and a header (not shown) having the same configuration as the header 5y.

The header 5x2 includes a duct 51, a bead header 52, and a soto header 53. Partition plates 14a and 14b are inserted into the upper and lower portions of the header 5x2 for sealing.
The flat heat transfer tube 1 including a large number of fins 2 is abutted against an opening (not shown) of a duct 51. As a result, the refrigerant can travel to the duct 51 through the flat heat transfer tube 1.

The first heat exchanger K11 and the second heat exchanger K12 may be connected to each other.
According to the above configuration, since the first heat exchanger K11 and the second heat exchanger K12 are arranged side by side, refrigerant distribution can be performed more satisfactorily. In addition, the amount of heat exchange is improved.

In addition, although the case where two 1st heat exchangers K11 and 2nd heat exchangers K12 were arranged was demonstrated in the modification, you may arrange 3 or more. The amount of heat exchange increases as the number of heat exchangers K arranged in parallel increases.
In the first reference embodiment, the configuration in which the edge header 52 and the soto header 53 are separated from each other has been described. However, the edge header 52 and the soto header 53 may be integrally formed.

As described in the first reference embodiment, the heat exchanger has the following configuration.
That is, the heat exchanger
A heat exchanger core having fins that expand the heat transfer area on the air side, and a heat transfer tube through which the refrigerant passes,
An inner header member in contact with the heat transfer tube, a duct having a duct flow path through which the refrigerant flows and having an opening for communicating the flow path of the heat transfer tube and the duct flow path; and the duct and the inner header member And a header having an outer header member in contact with the header.
According to such a configuration, it is possible to provide a heat exchanger including a header that can appropriately distribute the refrigerant and has a small number of parts.

Moreover, in the heat exchanger, it is preferable that the opening has a width equal to or less than a width of the heat transfer tube.
According to such a structure, a heat exchanger tube can be positioned with respect to a duct by making a heat exchanger tube contact | abut to the opening part of a duct.

In the heat exchanger, it is preferable that the opening has a height dimension that is equal to or less than a thickness dimension of the heat transfer tube.
According to such a structure, a heat exchanger tube can be positioned with respect to a duct by making a heat exchanger tube contact | abut to the opening part of a duct.

Moreover, it is preferable that the outer header member and the duct are in contact with each other at one or more points on a surface excluding a side surface of the duct.
According to such a configuration, the outer header member can be easily positioned with respect to the duct.

Moreover, it is preferable that the said outer header member has the bending that the said duct does not contact the corner | angular part of the said outer header member.
According to such a configuration, the outer header member can be accurately positioned with respect to the duct.

Moreover, it is preferable that the said duct has an insertion part for inserting a partition plate in the said outer side header member.
According to such a structure, a partition plate can be inserted in an outer side header member via an insertion part.

Moreover, it is preferable that the width | variety of the said inner header member and the width | variety of the said duct are substantially the same.
According to such a configuration, both sides of the inner header member and the duct can be sandwiched by the outer header member.

Further, the heat transfer tube is in contact with the duct so as to communicate with the opening,
The inner header member is fixed to the heat transfer tube;
The outer header member is preferably fixed to the inner header member and the duct on the outside.
According to such a configuration, the inner header member and the duct can be firmly fixed by the outer header member.

The duct is directly fixed to the outer header member,
The inner header member is directly fixed to the outer header member;
It is preferable that the duct and the inner header member are in contact with each other without being directly fixed.
According to such a structure, manufacture of a heat exchanger becomes easy.

Moreover, it is good also as an air conditioner which comprises the heat exchanger of an above-described structure.
According to such a configuration, it is possible to provide an air conditioner including a header that can appropriately distribute the refrigerant and has a small number of parts.

<< Second Reference Form >>
FIG. 38 is a perspective view of the heat exchanger K2 according to the second reference embodiment.
As shown in FIG. 38, the heat exchanger K2 includes a plurality of flat heat transfer tubes 1, a plurality of fins 2, and headers 7x and 7y.

The flat heat transfer tube 1 is a heat transfer tube through which a refrigerant flows. The flat heat transfer tube 1 has a flat shape in a longitudinal sectional view, and extends in the left-right direction in the example shown in FIG. The flat heat transfer tube 1 has one end connected to the header 7x and the other end connected to another header 7y. And a refrigerant | coolant flows through the some refrigerant | coolant flow path 12 (refer FIG. 42) provided in the inside of the flat heat exchanger tube 1 side by side.

The plurality of fins 2 are metal thin plates for securing a heat transfer area between the refrigerant and the air, and are arranged at predetermined intervals. In the example shown in FIG. 38, a plate fin whose plate surface is an elongated rectangular shape is used as the fin 2. Each fin 2 is arranged so that each plate surface becomes parallel and a predetermined fin pitch is secured between adjacent fins 2.

Each of the plurality of fins 2 includes an opening h15 (see FIG. 43) that is a U-shaped notch for inserting the flat heat transfer tube 1 from the side (front side). The plurality of openings h15 are provided at equal intervals in the height direction so as to correspond to the plurality of flat heat transfer tubes 1 on a one-to-one basis. Moreover, the fin 2 is provided with the fin collar 2c (refer FIG. 43) formed in the edge part of the opening part h15.

The matter that the flat heat transfer tube 1 is inserted from the side into the opening h15 of the fin 2 is included in the matter that the flat heat transfer tube 1 (heat transfer tube) is “inserted” into the fin 2.

The headers 7x and 7y are refrigerant distributors connected to the plurality of flat heat transfer tubes 1. The headers 7x and 7y have a cylindrical shape whose outer shape is elongated in the height direction. And the refrigerant | coolant distributed to the flat heat exchanger tube 1 from one of the headers 7x and 7y is guide | induced to the other via the flat heat exchanger tube 1, and merges.

In the example shown in FIG. 38, the refrigerant inlet pipe 30 and the refrigerant outlet pipe 33 for introducing / deriving the refrigerant to / from the heat exchanger K2 are connected to the header 7x. Next, the configuration of the header 7x will be described, but the same applies to the other header 7y.

In FIG. 39, in order to facilitate understanding of the structure of the header 7x of the heat exchanger according to the second reference embodiment, the inner cylinder 72 and the intermediate cylinders 73, 74, 75 are pulled up from the outer cylinder 71, and a part thereof is exposed. FIG.
As shown in FIG. 39, the header 7x includes an outer cylinder 71 (cylindrical body), an inner cylinder 72 (cylindrical body), and intermediate cylinders 73, 74, and 75 (cylindrical body).

The outer cylinder 71 is a cylinder connected to the plurality of flat heat transfer tubes 1 (see FIG. 40), and has an elongated cylindrical shape. The outer cylinder 71 is provided with an insertion hole h16 into which the plurality of flat heat transfer tubes 1 are inserted. Although not visible in FIG. 39, the outer cylinder 71 has a hole (not shown) into which the refrigerant inlet pipe 30 and the refrigerant outlet pipe 33 (see FIG. 38) are inserted, on the opposite side (right side) of the insertion hole h16. ).

The inner cylinder 72 has an elongated cylindrical shape, is coaxial with the outer cylinder 71, and is disposed in the outer cylinder 71. Further, the inner cylinder 72 is configured not to have a hole so that the refrigerant does not leak into the inner side of the inner cylinder 72 in the radial direction.

Intermediate cylinders 73, 74, and 75 are cylinders that guide the refrigerant in a predetermined direction, and each has an elongated cylindrical shape. The intermediate cylinders 73, 74, and 75 are coaxial with the outer cylinder 71 and the inner cylinder 72 and are disposed between the outer cylinder 71 and the inner cylinder 72.

In the example shown in FIG. 39, three intermediate cylinders 73, 74, and 75 having different outer diameters and inner diameters and having substantially the same length in the height direction are arranged coaxially. In the outermost intermediate cylinder 73, another insertion hole h17 is provided at a position corresponding to the insertion hole h16 of the outer cylinder 71. That is, the number of insertion holes h17 included in the intermediate cylinder 73 is the same as the number of insertion holes h16 included in the outer cylinder 71, and the position of the insertion hole h17 in the height direction is the same as that of the insertion hole h16. It is the same as the position in the height direction (see FIGS. 40 and 41). And the flat heat exchanger tube 1 is inserted in the header 7x through the insertion holes h16 and h17 in order.

Further, although not visible in FIG. 39, an elongated hole h18 (see FIGS. 40 and 41) is provided in the height direction on the opposite side (right side) of the insertion hole h17 in the intermediate cylinder 73. A first flow path hg elongated in the height direction is formed by a hole h18 of the intermediate cylinder 73 and a hole h19 of the intermediate cylinder 75 described below (see FIGS. 40 and 41).

Among the three intermediate cylinders 73, 74, and 75, the innermost intermediate cylinder 74 is provided with an elongated hole h20 (see also FIG. 40) in the circumferential direction. The hole h20 is a hole for communicating the flat heat transfer tubes 1 arranged at equal intervals in the height direction and the first flow path hg (see FIGS. 40 and 41) elongated in the vertical direction. In other words, the hole h20 is a cross flow path that connects the flat heat transfer tube 1 and the first flow path hg. And the refrigerant | coolant which flows in from the flat heat exchanger tube 1 turns around from the front side via this hole h20, and is guide | induced to the 1st flow path hg (refer FIG. 40, FIG. 41). Depending on the mode of air conditioning operation (heating operation or cooling operation), the direction of refrigerant flow may be reversed.

Another intermediate cylinder 75 is disposed between the outer intermediate cylinder 73 and the inner intermediate cylinder 74. The intermediate cylinder 75 has a function of adjusting the cross-sectional area of the refrigerant flow path together with the other intermediate cylinders 73 and 74.

39, in the intermediate cylinder 75, a predetermined hole h21 is provided at a position corresponding to the insertion holes h16 and h17. The hole h21 has a function of guiding the refrigerant flowing from the flat heat transfer tube 1 to the hole h20 of the intermediate cylinder 74 (or vice versa). The hole h21 has a slightly larger width in the circumferential direction and the height direction than the insertion holes h16 and h17, and communicates with the hole h20 and also communicates with the first flow path hg through the hole h20. (See FIG. 40).

Further, although not visible in FIG. 39, a hole h19 (see FIGS. 40 and 41) elongated in the height direction is provided on the opposite side (right side) of the hole h21 in the intermediate cylinder 75. The position in the circumferential direction of the hole h19 (see FIG. 40) and the range in the height direction (see FIG. 41) are the same as those of the hole h18 in the intermediate cylinder 73.

FIG. 40 is a cross-sectional view of the flat heat transfer tube 1 and the header 7x of the heat exchanger K2 according to the second reference embodiment.
That is, in a state where the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are positioned in the height direction and the circumferential direction, the header 7x is formed on a predetermined plane that crosses the refrigerant flow path 12 of the flat heat transfer tube 1. FIG. 40 shows a cross section when cut.

40, a plurality of “cylinders” including the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are in close contact with other “cylinders” that are adjacent in the radial direction. For example, the outer cylinder 71 and the intermediate cylinder 73 that are adjacent in the radial direction are brazed and are in close contact with each other. Moreover, the inner cylinder 72 and the intermediate cylinder 74 that are adjacent in the radial direction are brazed and are in close contact with each other. Similarly, the intermediate cylinders 73 and 75 are also in close contact, and the intermediate cylinders 74 and 75 are also in close contact.

It should be noted that that the cylinders are “closely attached” means that there are almost no gaps between the cylinders adjacent in the radial direction at portions other than the holes h20, h21, h18, and h19. For example, a state where the inner peripheral surface of a predetermined cylindrical body and the outer peripheral surface of another cylindrical body inside the predetermined cylindrical body are brazed and there is almost no gap therebetween is also included in the above-mentioned “contact”.

In the example shown in FIG. 40, the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 have substantially the same thickness. When the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are made of aluminum or an aluminum alloy, these thicknesses are 0.5 mm to 3 mm in order to ensure the strength of the header 7x. It is preferable to be within the range.

In addition, the constituent material and thickness of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are not limited to those described above. Moreover, the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 may have different thicknesses.

As described above, the flat heat transfer tube 1 is inserted into the insertion hole h16 of the outer cylinder 71 and the insertion hole h17 of the intermediate cylinder 73. Further, the hole h18 of the intermediate cylinder 73, the hole h20 of the intermediate cylinder 74, and the holes h21 and h19 of the intermediate cylinder 75 are all in communication with the refrigerant flow path 12 of the flat heat transfer tube 1. The “refrigerant channel” of the intermediate cylinders 73, 74, 75 includes holes h20, h21, h18, h19.

40, the flat heat transfer tube 1 has its tip facing the inner cylinder 72, and it is preferable that the horizontal width L of the flat heat transfer tube 1 is narrower than the outer diameter of the inner cylinder 72. As a result, most of the refrigerant from the flat heat transfer tube 1 toward the header 7x collides with the outer peripheral surface of the inner cylinder 72, and thus the gas-liquid two-phase refrigerant is agitated. Therefore, it becomes difficult for the refrigerant to be separated into a gas phase and a liquid phase. The refrigerant that has collided with the outer peripheral surface of the inner cylinder 72 goes through the hole h20 of the intermediate cylinder 74 and is guided to the first flow path hg (see FIG. 41) that is elongated in the height direction.

FIG. 41 is a longitudinal sectional view of the heat exchanger K2 according to the second reference embodiment.
As described above, the hole h18 elongated in the height direction is provided in the intermediate cylinder 73, and the hole h19 elongated in the height direction is provided in the intermediate cylinder 75. The “first flow path hg” that guides the refrigerant in the direction parallel to the central axis R of the plurality of “cylinders” including the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 includes holes h18, h19 is included.

The first flow path hg described above is provided at a position (right side) that is separated from the insertion hole h16 of the outer cylinder 71 in the cross-sectional view of the header 7x (see FIG. 40). Therefore, when the refrigerant inlet pipe 30 and the refrigerant outlet pipe 33 (see FIG. 38) are inserted into the header 7x, the flat heat transfer pipe 1 and the fin 2 do not interfere with the refrigerant inlet pipe 30 and the refrigerant outlet pipe 33. The operation of connecting the inlet pipe 30 and the refrigerant outlet pipe 33 to the header 7x is facilitated.

In a predetermined operation mode (for example, heating operation), the refrigerant flows upward through the first flow path hg. Thus, even when the refrigerant flows upward through the first flow path hg, by appropriately adjusting the cross-sectional area of the first flow path hg at the design stage (for example, narrowing the cross-sectional area), The refrigerant flows at a relatively high flow rate through the first flow path hg. Thereby, since a refrigerant | coolant reaches the flat heat exchanger tube 1 provided with two or more in the height direction substantially equally, the heat exchange performance of the heat exchanger K2 can be improved rather than before.

FIG. 42 is a partially enlarged view in which a part of the heat exchanger K2 according to the second reference embodiment is cut out.
In the example shown in FIG. 42, after the refrigerant flowing out from the flat heat transfer tube 1 collides with the outer peripheral surface of the inner cylinder 72, the circumferential direction of the intermediate cylinder 74 is indicated by a broken curve arrow or a solid curve arrow below it. Through the hole h20 (see also FIG. 40), and further flows downward through the first flow path hg.

As described above, the holes h20, h21, h18, and h19 function as refrigerant flow paths in the header 7x. Therefore, according to the second reference embodiment, there is no need to provide a partition plate (not shown) conventionally used for forming the refrigerant flow path or adjusting the flow rate of the refrigerant in the header 7x. . For example, the refrigerant guided in the vertical direction through the first flow path hg (holes h18, h19) collides with the upper end or lower end of the first flow path hg without providing a partition plate (not shown). This is because the flow direction changes. Thus, since it is not necessary to provide a partition plate (not shown) in the header 7x, the number of parts of the heat exchanger K2 can be reduced, and the number of manufacturing steps and the manufacturing cost can be reduced.

FIG. 43 is a perspective view of the vicinity of the upper portion of the header 7x included in the heat exchanger K2 according to the second reference embodiment.
As shown in FIG. 43, the upper end surfaces of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are substantially flush. Further, the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are positioned in the circumferential direction at an end portion (upper end portion in FIG. 43) in a direction parallel to the central axis R (see FIG. 41). Has a concave portion v. That is, in the upper end portions of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75, the vicinity of the center in the left-right direction is cut out to form a recess v.

Then, in the manufacturing stage of the heat exchanger K2, the operator aligns the positions of the recesses v in the circumferential direction, whereby the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, 75 are positioned in the circumferential direction. The For example, when an operator inserts a positioning plate material (not shown) having a thickness corresponding to the recess v into the recess v, the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are circumferential. Positioned with. In the second reference embodiment, a similar concave portion v is provided at the lower end portion of the header 7x (see FIG. 41), but the concave portion v may be provided only at one of the upper end portion and the lower end portion of the header 7x. Good.

Also, a brazing material for bonding is appropriately applied to the peripheral wall surfaces (outer peripheral surface and inner peripheral surface) of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75. Then, when heated in a heating furnace (not shown) in the above-described positioning state, the brazing material is melted, and the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, 75 are joined.

<Effect>
According to the second reference embodiment, in manufacturing the header 7x, if the operator inserts the inner cylinder 72 and the intermediate cylinders 73, 74, 75 into the outer cylinder 71, the respective cylinders are naturally coaxial, so that the radial direction Positioning with is easy. Moreover, since the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 have substantially the same length in the height direction, positioning in the height direction is easy.

Furthermore, since the positioning cylinder recesses v (see FIG. 43) are formed in the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, 75, positioning in the circumferential direction is easy. Therefore, an operator can easily perform the assembly work of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75.

Further, at the design stage of the header 7x, the designer can appropriately adjust the number (three in the second reference embodiment) and the thickness of the intermediate cylinders 73, 74, and 75 so that the designer can adjust the first flow path hg (FIG. 40). , See FIG. 41). Thereby, the designer can easily perform the design in consideration of the flow rate of the refrigerant flowing through the header 7x. For example, when the designer reduces the number of intermediate cylinders or reduces the thickness thereof, the cross-sectional area of the first flow path hg is reduced. As a result, the flow rate at which a predetermined flow rate of refrigerant flows through the header 7x can be increased. The same can be said when the design of the header 7x is appropriately changed based on the use condition of the air conditioner.

Moreover, since each hole of the intermediate | middle cylinders 73, 74, and 75 functions as a refrigerant | coolant flow path, it is not necessary to provide the partition plate (not shown) for forming a refrigerant | coolant flow path in the header 7x. Thereby, the manufacturing man-hour and manufacturing cost of the heat exchanger K2 can be reduced more than before.
Further, since the inner side in the radial direction of the inner cylinder 72 is hollow, the cost (volume) of the material required for the header 7x can be reduced as compared with the conventional case.

Moreover, since the cylindrical outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are not complicated, it is not necessary to mold them using a core. Therefore, the manufacturing cost of the header 7x and the like can be reduced as compared with the conventional case.
Further, in the header 7x, the first flow path hg in the height direction (see FIG. 41) is provided at a position away from the connection location of the flat heat transfer tube 1 (see FIG. 40). This facilitates the work of connecting the refrigerant inlet pipe 30 and the refrigerant outlet pipe 33 (see FIG. 38) to the header 7x.

Further, the configuration of the header 7x can be applied to the indoor heat exchanger 101 in addition to the outdoor heat exchanger 106 (see FIG. 44). As described above, according to the second reference embodiment, it is possible to provide an air conditioner including the heat exchanger K2 (that is, the outdoor heat exchanger 106 and the indoor heat exchanger 101) that can be easily manufactured.

<< Modification of the second reference form >>
As described above, the heat exchanger K2 and the like have been described in the second reference embodiment, but various other changes can be made.
For example, in the second reference embodiment, the configuration in which the header 7x of the heat exchanger K2 includes the three intermediate cylinders 73, 74, and 75 (see FIG. 40) has been described, but the number of intermediate cylinders may be two or less. It may be four or more. That is, any configuration is possible as long as it is coaxial with the outer cylinder 71 and the inner cylinder 72 and at least one intermediate cylinder is disposed between the outer cylinder 71 and the inner cylinder 72.

In the second reference embodiment, the configuration in which the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are provided with the positioning recesses v (see FIG. 43) is not limited thereto. For example, the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 are circumferentially positioned at ends (upper and lower ends) in a direction parallel to the central axis R (see FIG. 41). The structure which has a convex part (not shown) for use may be sufficient.

In the second reference embodiment, the number of first flow paths hg parallel to the central axis R (see FIG. 41) of the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 is one. Although explained, it is not limited to this. For example, the first flow path hg may be provided at the front part of the intermediate cylinders 73 and 75, and another first flow path hg may be provided at the rear part of the intermediate cylinders 73 and 75. In such a configuration, the refrigerant flowing from the flat heat transfer tube 1 is divided into front and rear through two holes (not shown) of the intermediate cylinder 74, and a part of the refrigerant flows through the front hole h20. Guided to the path hg, the remainder is guided to the rear first flow path hg through a rear hole (not shown). According to such a configuration, there is no bias in the front-rear direction in the flow of the refrigerant through the flat heat transfer tube 1, so that the heat exchange performance of the heat exchanger K2 can be further enhanced.

In the second reference embodiment, the configuration in which each cylindrical body including the outer cylinder 71, the inner cylinder 72, and the intermediate cylinders 73, 74, and 75 is cylindrical (see FIG. 39) is described, but the present invention is not limited to this. That is, the cross section of each cylinder described above may be a square frame shape or a polygonal frame shape. In such a configuration, “coaxial” means that the positions of the centers of gravity when the cylinders are cut along a predetermined cross section are substantially the same. The “radial direction” means a direction perpendicular to a straight line (center axis) passing through the center of gravity.

As described in the second reference embodiment, the heat exchanger has the following configuration.
That is, the heat exchanger
A plurality of fins arranged at predetermined intervals;
A plurality of heat transfer tubes inserted through the plurality of fins;
A refrigerant distributor connected to a plurality of the heat transfer tubes,
The refrigerant distributor is
An outer cylinder provided with an insertion hole into which a plurality of the heat transfer tubes are inserted;
An inner cylinder that is coaxial with the outer cylinder and disposed in the outer cylinder;
Having at least one intermediate cylinder that is coaxial with the outer cylinder and the inner cylinder and is disposed between the outer cylinder and the inner cylinder;
The plurality of cylinders including the outer cylinder, the inner cylinder, and the intermediate cylinder are in close contact with other cylinders adjacent in the radial direction,
The intermediate cylinder has a refrigerant flow path through which a refrigerant flows,
The intermediate cylinder is in close contact with the other cylindrical body adjacent in the radial direction at a portion other than the refrigerant flow path.
According to such a configuration, a heat exchanger that is easy to manufacture can be provided.

The refrigerant flow path has a first flow path for guiding the refrigerant in a direction parallel to the central axis of the cylindrical body,
In the cross-sectional view of the refrigerant distributor, it is preferable that the first flow path is provided at a position away from the insertion hole of the outer cylinder.
According to such a configuration, when the refrigerant inlet pipe and the refrigerant outlet pipe are inserted into the refrigerant distributor, it is possible to prevent the heat transfer pipe and the fin from interfering with the refrigerant inlet pipe and the refrigerant outlet pipe.

Moreover, it is preferable that the said outer cylinder, the said inner cylinder, and the said intermediate | middle cylinder have the recessed part or convex part for the positioning in the circumferential direction in the edge part of the direction parallel to the center axis line.
According to such a configuration, the outer cylinder, the inner cylinder, and the intermediate cylinder can be easily positioned.

Moreover, it is preferable that the front-end | tip of the said heat exchanger tube has faced the said inner cylinder, and the lateral width of the said heat exchanger tube is narrower than the outer diameter of the said inner cylinder.
According to such a configuration, most of the refrigerant traveling from the heat transfer tube to the refrigerant distributor collides with the outer peripheral surface of the inner cylinder, and thus the gas-liquid two-phase refrigerant is agitated.

The air conditioner may have the following configuration.
That is, the air conditioner
A refrigerant circuit in which the refrigerant circulates through the compressor, the condenser, the expansion valve, and the evaporator sequentially,
At least one of the condenser and the evaporator is
A plurality of fins arranged at predetermined intervals;
A plurality of heat transfer tubes inserted through the plurality of fins;
A refrigerant distributor connected to a plurality of the heat transfer tubes,
The refrigerant distributor is
An outer cylinder provided with an insertion hole into which a plurality of the heat transfer tubes are inserted;
An inner cylinder that is coaxial with the outer cylinder and disposed in the outer cylinder;
Having at least one intermediate cylinder that is coaxial with the outer cylinder and the inner cylinder and is disposed between the outer cylinder and the inner cylinder;
The plurality of cylinders including the outer cylinder, the inner cylinder, and the intermediate cylinder are in close contact with other cylinders adjacent in the radial direction,
The intermediate cylinder has a refrigerant flow path through which the refrigerant flows.
According to such a configuration, an air conditioner including a heat exchanger that can be easily manufactured can be provided.

<< other variations >>
In addition, this invention is not limited to above-described embodiment etc., Various modifications are included. For example, in the embodiments and the like, the case where the heat exchanger (that is, the outdoor heat exchanger 106 and the indoor heat exchanger 101) is a parallel flow heat exchanger has been described, but the present invention is not limited thereto. For example, the heat exchanger may be a finned tube heat exchanger or other types of heat exchangers.

In the embodiments and the like, the air conditioner is described in which the configuration of the heat exchanger is applied to both the outdoor heat exchanger 106 and the indoor heat exchanger 101. However, the present invention is not limited to this. That is, the embodiment or the like may be applied to one of the outdoor heat exchanger 106 and the indoor heat exchanger 101. In other words, in the refrigerant circuit Q in which the refrigerant circulates sequentially through the compressor 8, the “condenser”, the “expansion valve”, and the “evaporator”, the “condenser” and “evaporator” At least one may have the configuration of the header (for example, the headers 3x and 3y in FIG. 1) described in the embodiment and the like.

In the embodiments and the like, the configuration in which the air conditioner AC (see FIG. 44) includes one outdoor unit 105 and one indoor unit 100 has been described, but the present invention is not limited thereto. For example, the embodiment can be applied to a multi-type air conditioner in which a plurality of indoor units are connected to one outdoor unit. Further, the embodiment and the like can be applied to an air conditioner having a configuration in which a plurality of outdoor units are connected in parallel.

In addition, the configuration described in the embodiments and the like can be applied to various types of air conditioners (refrigeration cycle devices) such as packaged air conditioners, multi air conditioners for buildings, room air conditioners, and integrated air conditioners.

Further, the above-described embodiments and the like have been described in detail for easy understanding, and are not necessarily limited to those having all the configurations described. In addition, a part of the configuration of an embodiment or the like can be replaced with the configuration of another embodiment or the like, and the configuration of another embodiment or the like can be added to the configuration of an embodiment or the like. .

1 Flat heat transfer tube (heat transfer tube)
2 Fin 3a, 3b, 3c, 3d, 3d1, 3E, 3F, 3G, 3H, 3x, 3y, 5x, 5x1, 5x2, 5y, 7x, 7y Header (refrigerant distributor)
8 Compressor 9 Four- way valve 10A, 10B, 10C, 10D, 10E, 10H, K, K2, K3, K10 Heat exchanger 12 Refrigerant flow path 30 Refrigerant inlet pipe 33 Refrigerant outlet pipe 31F First plate (inlet side plate) body)
32F second plate (second member)
33F Third plate (first member)
34F 4th plate-like body 321 Flat plate part 322 1st convex part 323 2nd convex part 324 Engagement part 31G 1st plate-like body (inlet side plate-like body)
32G second plate (second member)
33G Third plate (first member)
34G Fourth plate 35G Fifth plate 31a, 31b Header base member (first member)
31x Flat tube side header member (first member)
34a, 34b Header insertion member (second member)
34x combination header member (second member)
31x3, 34x3 opening 35a, 35b, 35x partition plate 36a perforated partition plate (partition plate with hole)
38 Narrow channel 39 Separation part (separation part)
40A, 40B, 40C, 40D Bypass pipe (refrigerant distributor)
90 Two-phase region 91 Superheated region 100 Indoor unit 101 Indoor heat exchanger (heat exchanger)
102 Indoor Blower 103 Expansion Valve 105 Outdoor Unit 106 Outdoor Heat Exchanger (Heat Exchanger)
107 Outdoor blower 131 Connection surface 132 Perforated plate 133 Hole 318 Mounting bracket 319 Case 360, 360a Hole 411C Bending portion AC Air conditioner h7 First refrigerant flow hole h8, h9 Second refrigerant flow hole h31 hole (first Hole)
h4 hole (second hole)
i1 Narrow channel i2 Bypass channel M1, M2 Projection surface n1 First wall surface n2 Second wall surface u1 Groove u3 Recess

Claims (19)

1. Refrigerant distributors that connect to ends of a plurality of heat transfer tubes that form a refrigerant flow path, communicate the plurality of heat transfer tubes, and distribute the refrigerant,
   The refrigerant distributor includes a first member and a second member combined with each other,
   The refrigerant distributor which forms the narrow flow path which narrowed the cross-sectional area of the part used as the flow path of a refrigerant | coolant by combining the said 1st member and the said 2nd member.
2. The first member and the second member are formed of a plate material,
   The first member and the second member have a D-shaped cross-sectional shape formed by bending the plate material, and have a separation portion in a part of the D-shaped linear portion,
   The first member and the second member are combined through the spacing portion,
   The refrigerant distributor according to claim 1, wherein the narrow channel is formed between the D-shaped linear portions of the first member and the second member facing each other.
3. The refrigerant distributor according to claim 1, wherein a cross-sectional shape of a member obtained by combining the first member and the second member is a point-symmetric shape.
4. The refrigerant distributor according to claim 1, wherein the first member and the second member have an opening to which the same heat transfer tube is connected.
5. The first member and the second member each have a parallel surface parallel to the end surface of the heat transfer tube,
   The refrigerant distributor according to claim 1, further comprising at least one bent portion for forming the parallel surface.
6. The first member has a concave cross section,
   The refrigerant distributor according to claim 1, wherein the second member is fitted to an inner surface of the first member to form the narrow channel.
7. The refrigerant distributor according to claim 6, wherein one end of the open end of the concave member of the first member extends beyond the other end.
8. The refrigerant distributor according to claim 6, wherein the second member changes an insertion length in the first member.
9. A refrigerant that is connected to a refrigerant inlet pipe that guides a refrigerant to a lower part of the narrow flow path between the first member and the second member, and that diverts to the refrigerant through the refrigerant inlet pipe, is narrowed in the height direction. The refrigerant distributor according to claim 1, further comprising a bypass pipe that leads to an upper part or an intermediate part of the flow path.
10. A refrigerant that is connected to a refrigerant inlet pipe that guides the refrigerant to an upper portion of the narrow flow path between the first member and the second member, and that diverts to the refrigerant through the refrigerant inlet pipe in the height direction. The refrigerant distributor according to claim 1, further comprising a bypass pipe that leads to a lower part or an intermediate part of the flow path.
11. One end is connected to a refrigerant inlet pipe that guides the refrigerant to the narrow channel between the first member and the second member, and the other end is branched into a plurality so that the height positions thereof are different. With a tube,
    2. The refrigerant distributor according to claim 1, wherein in the bypass pipe, each of the flow paths on the other end side that is branched into a plurality communicates with the narrow flow path.
12. The narrow channel between the first member and the second member has a rectangular cross section,
    In the wall surfaces of the first member and the second member constituting the narrow channel, the distance between a pair of first wall surfaces perpendicular to the direction in which the heat transfer tube extends is 1 mm or more and 3 mm or less. The distance between the pair of remaining second wall surfaces is 10 mm or more and 20 mm or less. The refrigerant distributor according to claim 1, wherein:
13. The bypass pipe has a U-shaped bent portion in the vicinity of a connection portion with the refrigerant inlet pipe,
    The refrigerant distributor according to claim 9, wherein the bent portion includes a portion whose height is lower than the refrigerant inlet pipe, and is connected to a lower surface of the refrigerant inlet pipe.
14. A plate-shaped partition member that partitions the space between the first member and the second member into the narrow channel and the bypass channel;
    The partition member has a plate surface parallel to the vertical direction,
    In the partition member, a first hole is provided at a connection position with a refrigerant inlet pipe that guides the refrigerant to the narrow channel, and a second hole is provided at a position different from the height of the first hole,
    The refrigerant distributor according to claim 1, wherein the narrow channel and the bypass channel communicate with each other through the second hole.
15. A refrigerant inlet pipe is connected to one side, and includes an inlet side plate-like body provided with a first refrigerant flow hole at a location corresponding to the refrigerant inlet pipe,
    The second member is a plate-like body stacked on the other side of the inlet-side plate-like body,
    The first member is a plate-like body laminated on the other side of the second member,
    The second member is
    A flat plate portion having a flat plate surface;
    A first protrusion protruding from the flat plate to the other side and extending in the height direction,
    The tip of the first convex part is abutted against the one end face of the heat transfer tube,
    The refrigerant distribution according to claim 1, wherein a gap between the one side surface of the first member and the other side surface of the second member functions as the narrow channel. vessel.
16. The projection surface when the first refrigerant flow hole of the inlet side plate-like body is projected onto the second member has the plate surface on the one side of the second member. Item 16. The refrigerant distributor according to Item 15.
17. The second member is
    A pair of second protrusions protruding from the flat plate portion to the one side and extending in the height direction;
    Between the pair of second convex portions, at least one of the upper portion and the lower portion of the flat plate portion is provided with a second refrigerant flow hole through which the refrigerant flows,
    The ends of the pair of second convex portions are abutted against the other side surface of the inlet side plate-like body,
    Refrigerant flowing through the gap between the groove between the pair of second convex portions and the other side surface of the inlet side plate-like body is narrowed via the second refrigerant flow hole. The refrigerant distributor according to claim 15, wherein the refrigerant distributor is guided to a flow path.
18. A plurality of heat transfer tubes in which a refrigerant flows and extends in a lateral direction;
    A plurality of heat transfer tubes inserted therein, and heat radiating fins for heat exchange between the refrigerant and the fluid;
    A refrigerant distributor that is coupled to one of the plurality of heat transfer tubes and extends in the vertical direction so that the refrigerant is distributed to the plurality of heat transfer tubes;
    The said refrigerant | coolant divider | distributor is a heat exchanger which is a refrigerant | coolant divider | distributor of any one of Claims 1-17.
19. An air conditioner comprising the heat exchanger according to claim 18.

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