Heat exchanger and air conditioning apparatus

CROSS-REFERENCE TO RELATED APPLICATIONS

This U.S. National stage application claims priority under 35 U.S.C. §119(a) to Japanese Patent Application No. 2013-273267, filed in Japan on Dec. 27, 2013, the entire contents of which are hereby incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to a heat exchanger and an air conditioning apparatus.

BACKGROUND ART

Heat exchangers having a plurality of flat tubes, fins which are joined to the plurality of flat tubes, and header collecting tubes which are coupled respectively to the plurality of flat tubes at a first end side and another end side thereof, for bringing about heat exchange between a refrigerant flowing through the interior the flat tubes and air flowing to the outside of the flat tubes, are known in the prior art.

For example, the heat exchanger disclosed in Japanese Laid-open Patent No. H02-219966 is configured such that a plurality of outflow tubes extending in a horizontal direction are connected at either end to header collecting tubes that respectively extend in a vertical direction.

The heat exchanger disclosed in Japanese Laid-open Patent No. H02-219966 is directed to the problem that, in the interior of the header collecting tubes that extend in the vertical direction, liquid phase refrigerant of high specific gravity collects towards the bottom while gas phase refrigerant of low specific gravity collects towards the top, thereby giving rise to eccentric flow; in order to solve this problem, the feature of forming a throttle inside the header collecting tubes is proposed.

Passing the refrigerant through the throttle formed in this manner facilitates mixing of the gas phase refrigerant and the liquid phase refrigerant, while at the same time improves the flow velocity, making it easy for the refrigerant to reach the top within the header collecting tubes, thereby suppressing eccentric flow of the refrigerant.

SUMMARY
Technical Problem

However, the heat exchanger presented in Japanese Laid-open Patent No. H02-219966 as described above was not at all expected to be used in situations in which the refrigerant circulation rate varies, and there were no examinations of structures that yield the effect of suppressing eccentric flow in any sort of case, whether the circulation rate be low or the circulation rate be high.

Specifically, in the case of a low circulation rate, a throttle is formed, thereby raising flow velocity and enabling eccentric flow to be suppressed by allowing refrigerant to reach the tops of the header collecting tube interiors, but in the case of a high circulation rate, the throttle causes the flow velocity to be too high and too much refrigerant of high specific gravity to collect at the tops, giving rise to eccentric flow.

On the other hand, even if suppressing eccentric flow is made possible by providing a degree-adjusted throttle so that flow velocity will not be too high in the case of a high circulation rate, it is difficult to allow refrigerant to reach the tops in the case of a low circulation rate, giving rise to eccentric flow.

As a countermeasure, the spaces on the sides of the header collecting tubes to which the flat tubes are connected and the spaces on the opposite sides thereof are partitioned by partition members, whereby the spaces on the sides where the flat tubes are provided can be narrowed, and it is therefore possible to make it easier for refrigerant to reach the top ends. Furthermore, if refrigerant that has passed the partition members can be returned via underneath he partition members to the spaces on the sides where the flat tubes are provided, it is possible to avoid situations in which too much refrigerant of high specific gravity collects in the tops of the header collecting tubes, even when the refrigerant circulation rate is too high. Thus, eccentric flow of the refrigerant can be suppressed by causing the refrigerant to loop.

In this case, refrigerant inflowing to the header collecting tubes is made to flow upwards in the spaces on the sides to which the flat tubes are connected, causing the refrigerant to be distributed as evenly as possible to the flat tubes at each heightwise location, but when refrigerant flows toward a specific flat tube immediately after having flowed into a header collecting tube, there is a risk of eccentric flow due to the refrigerant amount passing through the specific flat tube being greater than the refrigerant amount flowing through other flat tubes.

With the foregoing in view, it is an object of the present invention to provide a heat exchanger and an air conditioning apparatus, with which it is possible to suppress eccentric flow of the refrigerant, even when employed under conditions in which the circulation rate varies.

Solution to Problem

The heat exchanger according to a first aspect of the present invention is provided with a plurality of flat tubes, a header collecting tube, and a plurality of fins. Each of the flat tubes has a plurality of refrigerant passage extending in the longitudinal direction. The plurality of flat tubes is arranged mutually side by side. The header collecting tube has one end of the flat tubes connected thereto, and extends in a vertical direction. The plurality of fins is joined to the flat tubes. The header collecting tube has a loop structure. The loop structure includes a first partition member and a second partition member, an inflow port, an upper communicating passage, and a lower communicating passage. The first partition member partition the internal space of the header collecting tube into upper internal space and lower internal space. The second partition member partitions upper internal space into first space that is space to the side where the flat tubes are connected, and second space that is space to the side opposite from the side where the flat tubes are connected to the first space. The inflow port is formed on the first partition member at the bottom part of the first space, and the inflow port allow refrigerant to pass from the lower internal space to the upper internal space so that an ascending flow arises in the first space when the heat exchanger is functioning as an evaporator of refrigerant. The upper communicating passage is located in upper part of the first space and the second space, and provide communication between the upper part of the first space and the second space, thereby guiding the refrigerant that has ascended within the first space into the second space. The lower communicating passage, which is located in lower part of the first space and the second space, provide communication between the lower part of the first space and the second space and guide the refrigerant from the second space to the first space, thereby returning the refrigerant from the second space to the first space, which has been guided from the first space to the second space and has descended within the second space. The header collecting tube has a third partition member and lower communicating port. The third partition member partitions the lower internal space into ascension space which is space to the side where the flat tubes are connected, and inflow space which is space to the side opposite from the side where the flat tubes are connected to the ascension space, and into which the refrigerant flows when the heat exchanger is functioning as an evaporator of refrigerant. The lower communicating port allow the refrigerant to pass from the inflow space to the ascension space. The lower communicating port and the refrigerant passage of the flat tubes that are connected to the lower internal space are arranged so as to not overlap each other as seen from the longitudinal direction of the flat tubes connected to the lower internal space.

With this heat exchanger, the internal space of the header collecting tube is partitioned by the partition member into the first space and the second space, whereby the area through which the refrigerant having flowed into the first space from the inflow port pass while ascending in the first space is made smaller, as compared with the case in which the first space and the second space are not partitioned by partition member. For this reason, even when the circulation rate of the refrigerant is a low circulation rate, the refrigerant having flowed into the first space from the inflow port is made to ascend in the narrow space of the first space only, whereby the refrigerant can easily reach the upper part of the internal space of the header collecting tube without experiencing any significant drop in the velocity of ascension of the refrigerant through the first space. For this reason, even when the circulation rate of the refrigerant is a low circulation rate, sufficient flow of the refrigerant to the flat tubes arranged towards the top is possible.

Moreover, in this heat exchanger, the header collecting tube has a loop structure that includes the inflow port, the partition member, the upper communicating passage, and the lower communicating passage. For this reason, even when the flow velocity of the refrigerant inflowing to the first space from the inflow port is fast, such as may be encountered at high circulation rates, and the high-specific gravity refrigerant passes forcefully while traversing the flat tubes located towards the bottom leading to a tendency to collect in upper part of the first space, it is possible for the high-specific gravity refrigerant having reached upper section of the first space to be returned back to the lower part of the first space by means of the loop structure. Specifically, with this loop structure, it is possible for the refrigerant having reached upper section of the first space to pass through the upper communicating passage and be fed to the second space side, and to then descend in the second space and flow through the lower communicating passage into lower part of the first space, and thereby guided into the flat tubes that are present at the lower part of the first space. For this reason, even when the flow velocity of the refrigerant inflowing to the first space is fast, such as may be encountered at high circulation rates, and the high-specific gravity refrigerant passes forcefully while traversing the flat tubes located towards the bottom leading to a tendency to collect in upper part of the first space, sufficient flow of the refrigerant to the flat tubes at the bottom is possible.

A structure in which lower internal space is disposed below the first partition member and inflow port is formed on the first partition member below the first space of the upper internal space is adopted as the structure for creating an ascending flow of refrigerant in the first space in order to achieve a looping flow of refrigerant which suppresses eccentric flow of the refrigerant as described above. While allowing the passage of refrigerant through the lower communicating port, the lower internal space is also partitioned by the third partition member into ascension space and inflow space. Because flat tubes are also connected to the lower internal space and heat exchange can be conducted with the refrigerant flowing through these flat tubes as well, heat exchange can be conducted with the air traversing through the lower internal space. In the aforedescribed structure, after the refrigerant inflowing to the inflow space of the lower internal space has flowed into the ascension space via the lower communicating port, the refrigerant will continue to ascend toward the first space of the upper internal space via the inflow port of the first partition member. In this aspect, because the lower communicating port and the refrigerant passage of the flat tubes that are connected to the lower internal space are arranged so as to not overlap each other as seen from the longitudinal direction of the flat tubes connected to the lower internal space, it is possible to suppress the collective flow of refrigerant passing through the lower communicating port to the flat tubes connected to the lower internal space.

In so doing, it is possible to suppress the collective flow of refrigerant passing through the lower communicating port to the flat tubes connected to the lower internal space and to keep eccentric flow of the refrigerant to flat tubes located at different heights to be kept to a minimum, even at times of a high circulation rate or at times of a low circulation rate.

A heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect, wherein the lower communicating port, as seen from the longitudinal direction of the flat tubes connected to the lower internal space, is located even lower than lowest part of the flat tubes connected to the lower internal space.

With this heat exchanger, all of the refrigerant passage entrances in the flat tubes connected to the lower internal space are positioned in the middle where refrigerant passing through the lower communicating port flows toward the inflow port of the first partition member, and the lower communicating port and the inflow port of the first partition member are vertically separated from each other. Therefore, the refrigerant passing through the lower communicating port has sufficient force in the ascending flow direction during passing through the inflow port of the first partition member. Therefore, it is possible to facilitate an ascending flow when the refrigerant passes through the inflow port of the first partition member.

A heat exchanger according to a third aspect of the present invention is the heat exchanger according to the first or second aspect, wherein the distal end of inflow pipeline for allowing refrigerant to flow into the inflow space is arranged so as to overlap at least part of the refrigerant passage of the flat tubes connected to the lower internal space, as seen from the longitudinal direction of the flat tubes connected to the lower internal space.

With this heat exchanger, the distal end of the inflow pipeline and the refrigerant passage of the flat tubes connected to the lower internal space at least partially overlap. Therefore, refrigerant inflowing to the lower internal space through the distal end of the inflow pipeline attempts to flow toward the refrigerant passage of the flat tubes connected to the lower internal space. In this aspect, even if the refrigerant passing through the inflow pipeline attempts to flow toward the refrigerant passage of specific flat tubes in this manner, the flow can be blocked by third partition member. Therefore, it is possible to more effectively suppress the collective flow of refrigerant passing through the lower communicating port to specific flat tubes.

A heat exchanger according to the fourth aspect of the present invention is the heat exchanger according to any one of the first through third aspects, wherein the lower communicating port is located between the lower end of the third partition member and the bottom section of the internal space of the header collecting tube.

With this heat exchanger, the need to furnish the third partition member with communicating port in order to furnish lower communicating port can be eliminated.

A heat exchanger according to the fifth aspect of the present invention is the heat exchanger according to any one of the first through fourth aspects, wherein the lower internal space is located so as to span below both the first space and the second space.

With this heat exchanger, a structure for changing the direction of refrigerant flow to an ascending flow immediately after the refrigerant has flowed into the inflow space can be achieved using the space below the first space and the space below the second space.

An air conditioning apparatus according to a sixth aspect of the present invention is provided with a refrigerant circuit. The refrigerant circuit is constituted by connecting the heat exchanger according to any one of the first to fifth aspects of the present invention, and a variable-capacity compressor.

With this air conditioning apparatus, driving by the variable-capacity compressor causes the rate at which the refrigerant flowing circulates through the refrigerant circuit to fluctuate, and the amount of refrigerant passing through the heat exchanger to fluctuate. In cases in which the heat exchanger functions as an evaporator, it will be possible to keep eccentric flow of the refrigerant within the heat exchanger to a minimum, even when the amount of the refrigerant passing therethrough increases and the mixture ratio of liquid phase refrigerant increases, or the flow velocity increases.

Advantageous Effects of Invention

With the heat exchanger according to the first aspect, it is possible to suppress the collective flow of refrigerant passing through the lower communicating port to the flat tubes connected to the lower internal space, and to keep eccentric flow of the refrigerant to flat tubes located at different heights to be kept to a minimum, even at times of a high circulation rate or at times of a low circulation rate.

With the heat exchanger according to the second aspect, it is possible to facilitate an ascending flow when the refrigerant passes through the inflow port of the first partition member.

With the heat exchanger according to the third aspect, it is possible to more effectively suppress the collective flow of refrigerant passing through the lower communicating port to specific flat tubes.

With the heat exchanger according to the fourth aspect, the need to furnish the third partition members with communicating port in order to furnish lower communicating port can be eliminated.

With the heat exchanger according to the fifth aspect, a structure for changing the direction of refrigerant flow to an ascending flow immediately after the refrigerant has flowed into the inflow space can be achieved using the space below the first space and the space below the second space.

With the air conditioning apparatus according to the sixth aspect of the present invention, in cases in which the heat exchanger functions as an evaporator, it is possible to keep eccentric flow of the refrigerant within the heat exchanger to a minimum, even when the amount of the refrigerant passing therethrough increases and the mixture ratio of liquid phase refrigerant increases, or the flow velocity increases.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a circuit diagram of overview of the scheme of an air conditioning apparatus according to a first embodiment;

FIG. 2 is a perspective view of the exterior of an air conditioning outdoor unit;

FIG. 3 is a schematic cross sectional view of an overview of placement of machinery of an air conditioning outdoor unit;

FIG. 4 is an exterior simplified perspective view of an outdoor heat exchanger, a gas refrigerant pipeline, and a liquid refrigerant pipeline;

FIG. 5 is a schematic rear view of a simplified configuration of an outdoor heat exchanger;

FIG. 6 is a simplified rear view of a configuration of an outdoor heat exchanger;

FIG. 7 is a fragmentary enlarged cross sectional view of a configuration of a heat exchange part of an outdoor heat exchanger;

FIG. 8 is a simplified perspective view of heat transfer fins attached to an outdoor heat exchanger;

FIG. 9 is a simplified configuration perspective view of a section near the upper part of a doubled-back header collecting tube;

FIG. 10 is a simplified cross sectional view of the vicinity of a first internal space of a doubled-back header collecting tube;

FIG. 11 is a simplified top view of the vicinity of a first internal space of a doubled-back header collecting tube;

FIG. 12 is a simplified cross sectional view of the vicinity of a second internal space of a doubled-back header collecting tube;

FIG. 13 is a simplified cross sectional view of the vicinity of a third internal space of a doubled-back header collecting tube;

FIG. 14 is a descriptive diagram for reference purposes, showing a condition of refrigerant distribution at a low circulation rate;

FIG. 15 is a descriptive diagram for reference purposes, showing a condition of refrigerant distribution at a medium circulation rate;

FIG. 16 is a descriptive diagram for reference purposes, showing a condition of refrigerant distribution at a high circulation rate;

FIG. 17 is a simplified configuration perspective view of a section near the upper part of a doubled-back header collecting tube according to another embodiment B;

FIG. 18 is a simplified configuration perspective view of a section near the upper part of a doubled-back header collecting tube according to another embodiment C.

DESCRIPTION OF EMBODIMENTS

(1) Overall Configuration of Air Conditioning Apparatus 1

FIG. 1 is a circuit diagram describing in overview a configuration of an air conditioning apparatus 1 according to a first embodiment of the present invention.

This air conditioning apparatus 1 is a device used for cooling and heating, through vapor compression refrigerating cycle operation, of a building interior in which an air conditioning indoor unit 3 has been installed, and is constituted by an air conditioning outdoor unit 2 as a heat source-side unit and the air conditioning indoor unit 3 as a usage-side unit, which are connected by refrigerant interconnecting pipelines 6, 7.

The refrigerant circuit constituted by connection of the air conditioning outdoor unit 2, the air conditioning indoor unit 3, and the refrigerant interconnecting pipelines 6, 7 is further constituted by connecting a compressor 91, a four-way switching valve 92, an outdoor heat exchanger 20, an expansion valve 33, an indoor heat exchanger 4, an accumulator 93, and the like, through refrigerant pipelines. A refrigerant is sealed within this refrigerant circuit, and refrigerating cycle operation involving compression, cooling, depressurization, and heating/evaporation of the refrigerant, followed by re-compression, is carried out. As the refrigerant, there may be employed one selected, for example, from R410A, R32, R407C, R22, R134a, carbon dioxide, and the like.

(2) Detailed Configuration of Air Conditioning Apparatus 1

(2-1) Air Conditioning Indoor Unit 3

The air conditioning indoor unit 3 is installed by being wall-mounted on an indoor wall or the like, or by being recessed within or suspended from an indoor ceiling of a building or the like. The air conditioning indoor unit 3 includes the indoor heat exchanger 4 and an indoor fan 5. The indoor heat exchanger 4 is, for example, a fin-and-tube heat exchanger of cross fin type, constituted by a heat transfer tube and a multitude of fins. In cooling mode, the heat exchanger functions as an evaporator for the refrigerant to cool the indoor air, and in heating mode functions as a condenser for the refrigerant to heat the indoor air.

(2-2) Air Conditioning Outdoor Unit 2

The air conditioning outdoor unit 2 is installed outside a building or the like, and is connected to the air conditioning indoor unit 3 by the refrigerant interconnecting pipelines 6, 7. As shown in FIG. 2 and FIG. 3, the air conditioning outdoor unit 2 has a unit casing 10 of substantially cuboid shape.

As shown in FIG. 3, the air conditioning outdoor unit 2 has a structure (a so-called “trunk” type structure) in which a blower chamber S1 and a machinery chamber S2 are formed by dividing an internal space of the unit casing 10 into two by a partition panel 18 that extends in a vertical direction. The air conditioning outdoor unit 2 includes an outdoor heat exchanger 20 and an outdoor fan 95 which are arranged within the blower chamber S1 of the unit casing 10, and also includes the compressor 91, the four-way switching valve 92, the accumulator 93, the expansion valve 33, a gas refrigerant pipeline 31, and a liquid refrigerant pipeline 32 which are arranged within the machinery chamber S2 of the unit casing 10.

The unit casing 10 constitutes a chassis and is provided with a bottom panel 12, a top panel 11, a side panel 13 at the blower chamber side, a side panel 14 at the machinery chamber side, a blower chamber-side front panel 15, and a machinery chamber-side front panel 16.

The air conditioning outdoor unit 2 is configured in such a way that outdoor air is drawn into the blower chamber S1 within the unit casing 10 from parts of the rear surface and the side surface of the unit casing 10, and the sucked in outdoor air is vented from the front surface of the unit casing 10. In specific terms, an intake port 10a and an intake port 10b facing the blower chamber S1 within the unit casing 10 are formed between the rear face-side end of the side panel 13 on the blower chamber side and the blower chamber S1-side end of the side panel 14 at the machinery chamber side. The blower chamber-side front panel 15 is furnished with a vent 10c, the front side thereof being covered by a fan grill 15a.

The compressor 91 is, for example, a sealed compressor driven by a compressor motor, and is configured such that the operating capacity can be varied through inverter control.

The four-way switching valve 92 is a mechanism for switching the direction of flow of the refrigerant. In cooling mode, the four-way switching valve 92 connects a refrigerant pipeline from the discharge side of the compressor 91 and the gas refrigerant pipeline 31 which extends from a first end (the gas-side end) of the outdoor heat exchanger 20, as well as connecting, via the accumulator 93, the refrigerant interconnecting pipeline 7 for the gas refrigerant and the refrigerant pipeline at the intake side of the compressor 91 (see the solid lines of the four-way switching valve 92 in FIG. 1). In heating mode, the four-way switching valve 92 connects the refrigerant pipeline from the discharge side of the compressor 91 and the refrigerant interconnecting pipeline 7 for the gas refrigerant, as well as connecting, via the accumulator 93, the intake side of the compressor 91 and the gas refrigerant pipeline 31 which extends from the first end (the gas-side end) of the outdoor heat exchanger 20 (see the broken lines of the four-way switching valve 92 in FIG. 1).

The outdoor heat exchanger 20 is arranged upright in a vertical direction (plumb vertical direction) in the blower chamber S1, and faces the intake ports 10a, 10b. The outdoor heat exchanger 20 is a heat exchanger made of aluminum; in the present embodiment, one having design pressure of about 3-4 MPa is employed. The gas refrigerant pipeline 31 extends from the first end (the gas-side end) of the outdoor heat exchanger 20, so as to connect to the four-way switching valve 92. The liquid refrigerant pipeline 32 extends from the other end (the liquid-side end) of the outdoor heat exchanger 20, so as to connect to the expansion valve 33.

The accumulator 93 is connected between the four-way switching valve 92 and the compressor 91. The accumulator 93 is equipped with a gas-liquid separation function for separating the refrigerant into a gas phase and a liquid phase. Refrigerant inflowing to the accumulator 93 is separated into the gas phase and the liquid phase, and the gas phase refrigerant which collects in the upper spaces is supplied to the compressor 91.

The outdoor fan 95 supplies the outdoor heat exchanger 20 with outdoor air for heat exchange with the refrigerant flowing through the outdoor heat exchanger 20.

The expansion valve 33 is a mechanism for depressurizing the refrigerant in the refrigerant circuit, and is an electrically operated valve, the opening degree of which is adjustable. In order to make adjustments to the refrigerant pressure and the refrigerant flow rate, the expansion valve 33 is disposed between the outdoor heat exchanger 20 and the refrigerant interconnecting pipeline 6 for the liquid refrigerant, and has the function of expanding the refrigerant, both in air-cooling operation and air-warming operation.

The outdoor fan 95 is arranged facing the outdoor heat exchanger 20 in the blower chamber S1. The outdoor fan 95 sucks outdoor air into the unit, and after heat exchange between the outdoor air and the refrigerant has taken place in the outdoor heat exchanger 20, discharges the heat-exchanged air to the outdoors. This outdoor fan 95 is a fan in which it is possible to adjust the airflow volume of the air supplied to the outdoor heat exchanger 20, and could be, for example, a propeller fan driven by a motor, such as a DC fan motor, or the like.

(3) Operation of Air Conditioning Apparatus 1

(3-1) Cooling Mode

In cooling mode, the four-way switching valve 92 enters the state shown by the solid lines in FIG. 1, i.e., a state in which the discharge side of the compressor 91 is connected to the gas side of the outdoor heat exchanger 20 via the gas refrigerant pipeline 31, and the intake side of the compressor 91 is connected to the gas side of the indoor heat exchanger 4 via the accumulator 93 and the refrigerant interconnecting pipeline 7. The design of the expansion valve 33 is such that opening degree adjustments are made to maintain a constant degree of superheat (degree of superheat control) of the refrigerant at the outlet of the indoor heat exchanger 4 (i.e., the gas side of the indoor heat exchanger 4). With the refrigerant circuit in this state, when the compressor 91, the outdoor fan 95, and the indoor fan 5 are run, low-pressure gas refrigerant is compressed by the compressor 91 to become high-pressure gas refrigerant. This high-pressure gas refrigerant is fed to the outdoor heat exchanger 20 through the four-way switching valve 92. Subsequently, the high-pressure gas refrigerant undergoes heat exchange in the outdoor heat exchanger 20 with outdoor air supplied by the outdoor fan 95, and is condensed to become high-pressure liquid refrigerant. The high-pressure liquid refrigerant, now in a supercooled state, is fed to the expansion valve 33 from the outdoor heat exchanger 20. Refrigerant having been depressurized almost to the intake pressure of the compressor 91 by the expansion valve 33 and entered a low-pressure, gas-liquid two-phase state is fed to the indoor heat exchanger 4, and undergoes heat exchange with indoor air in the indoor heat exchanger 4, evaporating to become low-pressure gas refrigerant.

This low-pressure gas refrigerant is fed to the air conditioning outdoor unit 2 through the refrigerant interconnecting pipeline 7, and is again sucked into the compressor 91. In this cooling mode, the air conditioning apparatus 1 prompts the outdoor heat exchanger 20 to function as a condenser for the refrigerant compressed in the compressor 91, and the indoor heat exchanger 4 to function as an evaporator for the refrigerant condensed in the outdoor heat exchanger 20.

In the refrigerant circuit during cooling mode, while degree of superheat control by the expansion valve 33 is taking place, the compressor 91 is inverter-controlled to a set temperature (such that the cooling load can be processed), and therefore the circulation rate of the refrigerant may be a high circulation rate in some cases, and a low circulation rate in others.

(3-2) Heating Mode

In heating mode, the four-way switching valve 92 enters the state shown by broken lines in FIG. 1, i.e., a state in which the discharge side of the compressor 91 is connected to the gas side of the indoor heat exchanger 4 via the refrigerant interconnecting pipeline 7, and the intake side of the compressor 91 is connected to the gas side of the outdoor heat exchanger 20 via the gas refrigerant pipeline 31. The design of the expansion valve 33 is such that opening degree adjustments are made to maintain the degree of supercooling of the refrigerant at the outlet of the indoor heat exchanger 4 at a target degree of supercooling value (degree of supercooling control). With the refrigerant circuit in this state, when the compressor 91, the outdoor fan 95, and the indoor fan 5 are run, low-pressure gas refrigerant is compressed by the compressor 91 to become high-pressure gas refrigerant, and is fed to the air conditioning indoor unit 3 through the four-way switching valve 92 and the refrigerant interconnecting pipeline 7.

The high-pressure gas refrigerant fed to the air conditioning indoor unit 3 then undergoes heat exchange with indoor air in the indoor heat exchanger 4, and is condensed to become high-pressure liquid refrigerant, then while passing through the expansion valve 33 is depressurized to an extent commensurate with the opening degree of the expansion valve 33. The refrigerant having passed through the expansion valve 33 flows into the outdoor heat exchanger 20. The refrigerant in a low-pressure, gas-liquid two-phase state having flowed into the outdoor heat exchanger 20 undergoes heat exchange with outdoor air supplied by the outdoor fan 95, evaporates to become low-pressure gas refrigerant, and is again sucked into the compressor 91 through the four-way switching valve 92. In this heating mode, the air conditioning apparatus 1 prompts the indoor heat exchanger 4 to function as a condenser for the refrigerant compressed in the compressor 91, and the outdoor heat exchanger 20 to function as an evaporator for the refrigerant condensed in the indoor heat exchanger 4.

In the refrigerant circuit during heating mode, while degree of supercooling control by the expansion valve 33 is taking place, the compressor 91 is inverter-controlled to a set temperature (such that the heating load can be processed), and therefore the circulation rate of the refrigerant may be a high circulation rate in some cases, and a low circulation rate in others.

(4) Detailed Configuration of the Outdoor Heat Exchanger 20

(4-1) Overall Configuration of the Outdoor Heat Exchanger 20

Next, the configuration of the outdoor heat exchanger 20 is described in detail, using FIG. 4 which shows an exterior simplified perspective view of the outdoor heat exchanger 20, FIG. 5 which shows a schematic rear view of the outdoor heat exchanger, and FIG. 6 which is a simplified rear view.

The outdoor heat exchanger 20 is provided with a heat exchange part 21 where heat exchange takes place between outdoor air and the refrigerant, an outlet/inlet header collecting tube 22 disposed at a first end of this heat exchange part 21, and a doubled-back header collecting tube 23 disposed at the other end of this heat exchange part 21.

(4-2) Heat Exchange Part 21

FIG. 7 is a fragmentary enlarged cross sectional view of a cross sectional structure of the heat exchange part 21 of the outdoor heat exchanger 20, in a plane perpendicular to the direction of flattening of flat multi-perforated tubes 21b thereof. FIG. 8 is a simplified perspective view of heat transfer fins 21a attached in the outdoor heat exchanger 20.

The heat exchange part 21 has an upper-side heat exchange area X positioned on the upper side, and a lower-side heat exchange area Y positioned below the upper-side heat exchange area X. Of these areas, the upper-side heat exchange area X has a first upper-side heat exchange part X1, a second upper-side heat exchange part X2, and a third upper-side heat exchange part X3, arranged side by side in that order from the top. The lower-side heat exchange area Y has a first lower-side heat exchange part Y1, a second lower-side heat exchange part Y2, and a third lower-side heat exchange part Y3, arranged side by side in that order from the top.

This heat exchange part 21 is constituted by a multitude of the heat transfer fins 21a and a multitude of the flat multi-perforated tubes 21b. The heat transfer fins 21a and the flat multi-perforated tubes 21b are both fabricated from aluminum or aluminum alloy.

The heat transfer fins 21a are flat members, and a plurality of cutouts 21aa extending in a horizontal direction for insertion of flattened tubes are formed side by side in a vertical direction in the heat transfer fins 21a. The heat transfer fins 21a are attached so as to have innumerable sections protruding towards the upstream side of the air flow.

The flat multi-perforated tubes 21b function as heat transfer tubes for transferring heat moving between the heat transfer fins 21a and the outside air to the refrigerant flowing through the interior. The flat multi-perforated tubes 21b have upper and lower flat surfaces serving as heat transfer surfaces, and a plurality of internal channels 21ba through which the refrigerant flows. The flat multi-perforated tubes 21b, which are slightly thicker in vertical breadth than the cutouts 21aa, are arrayed spaced apart in a plurality of tiers with the heat transfer surfaces facing up and down, and are temporarily fastened by being fitted into the cutouts 21aa. With the flat multi-perforated tubes 21b temporarily fastened by being fitted into the cutouts 21aa of the heat transfer fins 21a in this manner, the heat transfer fins 21a and the flat multi-perforated tubes 21b are brazed. The flat multi-perforated tubes 21b are fitted at either end into the outlet/inlet header collecting tube 22 and the doubled-back header collecting tube 23, respectively, and brazed. In so doing, an upper outlet/inlet internal space 22a and a lower outlet/inlet internal space 22b in the outlet/inlet header collecting tube 22, discussed below, and/or first to sixth internal spaces 23a, 23b, 23c, 23d, 23e, 23f of the doubled-back header collecting tube 23, and internal flow channels 21ba of the flat multi-perforated tubes 21b, discussed below, are linked.

The features pertaining to the flat multi-perforated tubes 21b described above are the same in a flat multi-perforated tube 121b connected to a first ascension space 61a.

As shown in FIG. 7, the heat transfer fins 21a link up on the vertical, and therefore any dew condensation occurring on the heat transfer fins 21a and/or the flat multi-perforated tubes 21b will drip down along the heat transfer fins 21a and drain to the outside through a path formed in the bottom panel 12.

(4-3) Outlet/Inlet Header Collecting Tube 22

The outlet/inlet header collecting tube 22 is a cylindrical member made of aluminum or aluminum alloy, disposed at a first end of the heat exchange part 21, and extending in the vertical direction.

The outlet/inlet header collecting tube 22 includes the upper outlet/inlet internal space 22a and the lower outlet/inlet internal space 22b which are partitioned off in the vertical direction by a first baffle 22c. The gas refrigerant pipeline 31 is connected to the upper outlet/inlet internal space 22a in a top part, and the liquid refrigerant pipeline 32 is connected to the lower outlet/inlet internal space 22b in a bottom part.

Both the upper outlet/inlet internal space 22a in the top part of the outlet/inlet header collecting tube 22 and the lower outlet/inlet internal space 22b in the bottom part are connected to first ends of the plurality of flat multi-perforated tubes 21b. More specifically, the first upper-side heat exchange part X1, the second upper-side heat exchange part X2, and the third upper-side heat exchange part X3 of the upper-side heat exchange area X are disposed in such a way as to correspond to the upper outlet/inlet internal space 22a in the top part of the outlet/inlet header collecting tube 22. The first lower-side heat exchange part Y1, the second lower-side heat exchange part Y2, and the third lower-side heat exchange part Y3 of the lower-side heat exchange area Y are disposed in such a way as to correspond to the lower outlet/inlet internal space 22b in the bottom part of the outlet/inlet header collecting tube 22.

(4-4) Doubled-Back Header Collecting Tube 23

The doubled-back header collecting tube 23 is a cylindrical member made of aluminum or aluminum alloy, disposed at the other end of the heat exchange part 21, and extending in the vertical direction.

The interior of the doubled-back header collecting tube 23 is partitioned in the vertical direction by a second baffle 23g, a third baffle 23h, a third flow regulation plate 43, a fourth baffle 23i, and a fifth baffle 23j, forming the first to sixth internal spaces 23a, 23b, 23c, 23d, 23e, 23f.

Of these, the three first to third internal spaces 23a, 23b, 23c of the doubled-back header collecting tube 23 are connected to the other ends of a multitude of the flat multi-perforated tubes 21b which are connected at their first ends to the upper outlet/inlet internal space 22a at the upper part of the outlet/inlet header collecting tube 22. Specifically, the first upper-side heat exchange part X1 of the upper-side heat exchange area X is disposed in such a way as to correspond to the first internal space 23a of the doubled-back header collecting tube 23, the second upper-side heat exchange part X2 of the upper-side heat exchange area X in such a way as to correspond to the second internal space 23b of the doubled-back header collecting tube 23, and the third upper-side heat exchange part X3 of the upper-side heat exchange area X in such a way as to correspond to the third internal space 23c of the doubled-back header collecting tube 23, respectively.

The multitude of flat multi-perforated tubes 21b connected at their first ends to the lower outlet/inlet internal space 22b in the bottom part of the outlet/inlet header collecting tube 22 connect at their other ends to the three fourth internal spaces 23d, 23e, 23f of the doubled-back header collecting tube 23. Specifically, the first lower-side heat exchange part Y1 of the lower-side heat exchange area Y is disposed in such a way as to correspond to the fourth internal space 23d of the doubled-back header collecting tube 23, the second lower-side heat exchange part Y2 of the lower-side heat exchange area Y in such a way as to correspond to the fifth internal space 23e of the doubled-back header collecting tube 23, and the third lower-side heat exchange part Y3 of the lower-side heat exchange area Y in such a way as to correspond to the sixth internal space 23f of the doubled-back header collecting tube 23, respectively.

The first internal space 23a of the topmost tier and the internal space 23f of the bottommost tier of the doubled-back header collecting tube 23 are connected by an interconnecting pipeline 24.

The second internal space 23b of the second tier from the top and the fifth internal space 23e of the second tier from the bottom are connected by an interconnecting pipeline 25.

The third internal space 23c of the third tier from the top and the fourth internal space 23d of the third tier from the bottom are partitioned apart by the third flow regulation plate 43, but have sections that communicate vertically via a third inflow port 43x disposed in the flow regulation plate 43.

The design is such that the number of flat multi-perforated tubes 21b into which refrigerant flowing in from the interconnecting pipeline 24 branches in the first internal space 23a of the doubled-back header collecting tube 23 is greater than the number of flat multi-perforated tubes 21b into which the refrigerant flowing from the liquid refrigerant pipeline 32 branches in the lower outlet/inlet internal space 22b of the outlet/inlet header collecting tube 22 as the refrigerant advances to the sixth internal space 23f (the same holds for the relationship of the numbers of the flat multi-perforated tubes 21b of the second internal space 23b and the fifth internal space 23e, and/or the relationship of the numbers of the flat multi-perforated tubes 21b of the third internal space 23c and the fourth internal space 23d). While different arrangements may be employed in order to optimize distribution of the refrigerant, in the present embodiment, the number of the flat multi-perforated tubes 21b connected to the first internal space 23a, the number of the flat multi-perforated tubes 21b connected to the second internal space 23b, and the number of the flat multi-perforated tubes 21b connected to the third internal space 23c are substantially equal. Likewise, while different arrangements may be employed in order to optimize distribution of the refrigerant, in the present embodiment, the number of the flat multi-perforated tubes 21b connected to the fourth internal space 23d, the number of the flat multi-perforated tubes 21b connected to the fifth internal space 23e, and the number of the flat multi-perforated tubes 21b connected to the sixth internal space 23f are substantially equal.

(4-5) Loop Structure of Doubled-Back Header Collecting Tube 23

In the doubled-back header collecting tube 23, the upper three first to third internal spaces 23a, 23b, 23c are furnished with a loop structure and with a flow regulating structure.

The loop structure and a flow regulating structure of the first to third internal spaces 23a, 23b, 23c, respectively, are described below.

(4-5-1) First Internal Space 23a

The highest first internal space 23a of the doubled-back header collecting tube 23 is provided with a first flow regulation plate 41, a first partition plate 51, and a first blocking plate 61, as shown in FIG. 6, the simplified perspective view of FIG. 9, the simplified cross-sectional view of FIG. 10, and the simplified top view of FIG. 11.

The first flow regulation plate 41 is a substantially discoidal plate-shaped member that partitions the first internal space 23a into a first ascension space 61a and a first inflow space 61b below, and a first outflow space 51a and a first loop space 51b above. The first ascension space 61a and the first inflow space 61b are spaces that are above the second baffle 23g partitioning the first internal space 23a and the second main heat exchange part 23b, and below the first flow regulation plate 41 provided to a higher position than the flat multi-perforated tube 121b directly above the second baffle 23g. The interconnecting pipeline 24, which extends from the lowest sixth internal space 23f of the doubled-back header collecting tube 23, is communicated with the first inflow space 61b. The flat multi-perforated tube 121b is connected to the first ascension space 61a. The flat multi-perforated tubes 21b and the flat multi-perforated tube 121b have the same configuration, and the only difference is connecting positions.

The first partition plate 51 is a substantially square plate-shaped member, partitioning the space in the first internal space 23a that is higher than the first ascension space 61a and the first inflow space 61b into the first outflow space 51a and the first loop space 51b. Though not particularly limited, the first partition plate 51 in the present embodiment is provided in the center of the first internal space 23a, thereby partitioning the space above the first ascension space 61a and the first inflow space 61b so that the first outflow space 51a and the first loop space 51b have the same width in a top view. The first partition plate 51 is fastened such that side surfaces thereof contact an inner peripheral surface of the doubled-back header collecting tube 23. The first outflow space 51a is a space situated on the side at which the flat multi-perforated tubes 21b connect at their first ends in the first internal space 23a. The first loop space 51b is a space situated on the opposite side of the first partition plate 51 from the first outflow space 51a in the first internal space 23a.

At the upper part of the first internal space 23a is disposed a first upper communicating passage 51x constituted by a vertical gap between the inside of the top end of the doubled-back header collecting tube 23, and a top end section of the first partition plate 51.

At the lower part of the first internal space 23a is disposed a first lower communicating passage 51y constituted by a vertical gap between the top surface of the first flow regulation plate 41 and a bottom end section of the first partition plate 51. In the present embodiment, the first lower communicating passage 51y extends in a horizontal direction from the first loop space 51b side towards the first outflow space 51a side. An outlet at the first outflow space 51a side of this first lower communicating passage 51y is located further below the location of the bottommost of the flat multi-perforated tubes 21b connected to the first outflow space 51a.

As shown in FIG. 9, the first flow regulation plate 41 is furnished with two first inflow ports 41x; these are openings which are disposed in the first outflow space 51a and the first ascension space 61a constituting the space at the side at which the flat multi-perforated tubes 21b extend in the first internal space 23a, and which provide communication in the vertical direction. The two inflow ports 41x are disposed away to the upstream side and the downstream side in the air flow direction, i.e., the direction of inflow of air with respect to the outdoor heat exchanger 20. The first inflow ports 41x are formed so as to be greater in width closer towards the first partition plate 51 side in the direction of air flow, and narrower in width closer towards the flat multi-perforated tube 21b side in the direction of air flow. The first inflow ports 41x have shapes conforming to the inner peripheral surface of the doubled-back header collecting tube 23.

The first internal space 23a has a flow regulating structure in which the refrigerant passage area (the area of a horizontal plane) in the first inflow ports 41x is sufficiently less than the refrigerant passage area of the first ascension space 61a and the first inflow space 61b (the area of the horizontal plane of the first ascension space 61a and the first inflow space 61b). This flow regulating structure can sufficiently throttle the refrigerant flow from the first ascension space 61a toward the first outflow space 51a, and can increase the refrigerant flow velocity upward on the vertical.

By partitioning off the space above the first flow regulation plate 41 within the first internal space 23a by means of the first partition plate 51, the refrigerant passage area at the first outflow space 51a side (the passage area of the ascending refrigerant flow within the first outflow space 51a) can be made smaller than the total horizontal area of the first outflow space 51a and the first loop space 51b. In so doing, it is easy to maintain the ascension velocity of refrigerant inflowing to the first outflow space 51a via the first inflow ports 41x, making it easy for the refrigerant to reach the upper section of the first outflow space 51a, even at a low circulation rate.

As shown in the simplified top view of FIG. 11, the flat multi-perforated tubes 21b are embedded within the first outflow space 51a, in such a way as to fill in half or more of the horizontal area at heightwise locations in the first outflow space 51a where the flat multi-perforated tubes 21b are absent.

This arrangement is such that when “the horizontal area of sections of flat multi-perforated tubes 21b extending into the first outflow space 51a” is subtracted from “the horizontal area at heightwise locations within the first outflow space 51a where no flat multi-perforated tube 21b is present,” the remaining area (the area of sections in which the refrigerant bypasses the flat multi-perforated tubes 21b in the first outflow space 51a) is greater than the refrigerant passage area of the first lower communicating passage 51y. In so doing, it is possible for refrigerant inflowing to the first outflow space 51a via the first inflow ports 41x to not be passed towards the first loop space 51b side through the first lower communicating passage 51y, which is narrower and difficult to pass through, but to instead be guided so as to ascend through sections excluding the flat multi-perforated tubes 21b in the first outflow space 51a, which are wider and easier to pass through.

The first internal space 23a has a loop structure that includes the first inflow ports 41x, the first partition plate 51, the first upper communicating passage 51x, and the first lower communicating passage 51y. For this reason, as shown by arrows in FIG. 10, refrigerant that reaches the top in the first outflow space 51a without inflowing to the flat multi-perforated tubes 21b is guided into the first loop space 51b via the first upper communicating passage 51x above the first partition plate 51, descends by gravity in the first loop space 51b, and returns to the bottom of the first outflow space 51a via the first lower communicating passage 51y below the first partition plate 51. In so doing, it is possible for the refrigerant reaching the upper part of the first outflow space 51a to be looped around within the first internal space 23a.

In the middle vicinity of the first flow regulation plate 41, the first blocking plate 61 partitions the first ascension space 61a to which the flat multi-perforated tube 121b is connected and the first inflow space 61b to which the interconnecting pipeline 24 is connected, while allowing these two spaces to be communicated through a first lower communicating port 61x at the bottom. The top end of the first blocking plate 61 extends to the bottom surface of the first flow regulation plate 41. The first lower communicating port 61x is disposed between the bottom end of the first blocking plate 61 and the top surface of the second baffle 23g. In the present embodiment, an example is presented of a case in which there is only one flat multi-perforated tube 121b connected to the first ascension space 61a, but a plurality of flat multi-perforated tubes 121b arranged side by side in the vertical direction may be connected to the first ascension space 61a.

In the present embodiment, as seen from the direction in which the flat multi-perforated tube 121b extends, the flat multi-perforated tube 121b is situated so that the opening in the end of the internal flow channel 21ba overlaps the opening in the end of the interconnecting pipeline 24 on the side connected to the first inflow space 61b.

In the present embodiment, as seen from the direction in which the flat multi-perforated tube 121b extends, the first blocking plate 61 is disposed so as to extend even lower than the bottom end portion of the opening in the end of the interconnecting pipeline 24 connected to the first inflow space 61b. Specifically, the first lower communicating port 61x and the opening in the end of the interconnecting pipeline 24 are positioned so as not to overlap.

In the present embodiment, as seen from the direction in which the flat multi-perforated tube 121b extends, the first blocking plate 61 is disposed so as to extend even lower than the bottom end portion of the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the first inflow space 61b. Specifically, the first lower communicating port 61x and the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b are positioned so as not to overlap.

Though not particularly limited, in the present embodiment, the arrangement is such that when “the horizontal area of the section of the flat multi-perforated tube 121b that extends into the first ascension space 61a” is subtracted from “the horizontal area at heightwise locations within the first ascension space 61a where the flat multi-perforated tube 121b is not present,” the remaining area (the area of sections in which the refrigerant bypasses the flat multi-perforated tube 121b in the first ascension space 61a) is greater than the refrigerant passage area of the first lower communicating port 61x.

(4-5-2) Second Internal Space 23b

The second internal space 23b, which is the second space down from the upper part of the doubled-back header collecting tube 23, has the same configuration as the highest first internal space 23a, and inside the second internal space are furnished a second flow regulation plate 42 a second partition plate 52, and a second blocking plate 62, as shown in FIG. 6 and the simplified cross-sectional view of FIG. 12.

The second flow regulation plate 42 is a substantially discoidal plate-shaped member that partitions the second internal space 23b into a second ascension space 62a and a second inflow space 62b below, and a second outflow space 52a and a second loop space 52b above. The second ascension space 62a and the second inflow space 62b are spaces that are above the third baffle 23h partitioning the second internal space 23b and the third internal space 23c, and below the second flow regulation plate 42 provided to a higher position than a flat multi-perforated tube 121b directly above the third baffle 23h. The interconnecting pipeline 25, extending from the fifth internal space 23e which is second from the bottom of the doubled-back header collecting tube 23, is communicated with the second inflow space 62b. The flat multi-perforated tube 121b is connected to the second ascension space 62a. The flat multi-perforated tubes 21b and the flat multi-perforated tube 121b have the same configuration, and only connect to different things.

The second partition plate 52 is a substantially square plate-shaped member, partitioning the space in the second internal space 23b that is higher than the second ascension space 62a and the second inflow space 62b into the second outflow space 52a and the second loop space 52b. The second outflow space 52a is a space situated on the side at which the flat multi-perforated tubes 21b connect at their first ends, in the second internal space 23b. The second loop space 52b is a space situated on the opposite side of the second partition plate 52 from the second outflow space 52a in the second internal space 23b.

At the upper part of the second internal space 23b is disposed a second upper communicating passage 52x constituted by a vertical gap between the bottom surface of the second baffle 23g and a top end section of the second partition plate 52.

At the bottom of the second internal space 23b is disposed a second lower communicating passage 52y constituted by a vertical gap between the top surface of the second flow regulation plate 42 and a bottom end section of the second partition plate 52. In the present embodiment, the second lower communicating passage 52y extends in a horizontal direction from the second loop space 52b side towards the second outflow space 52a side. An outlet at the second outflow space 52a side of this second lower communicating passage 52y is located further below the location of the bottommost of the flat multi-perforated tubes 21b connected to the second outflow space 52a.

Like the first flow regulation plate 41, the second flow regulation plate 42 is furnished with two second inflow ports 42x, which are vertically communicating openings disposed at the side from which the flat multi-perforated tubes 21b extend in the second internal space 23b.

Like the first internal space 23a, the second internal space 23b also has a flow regulating structure in which the refrigerant passage area (the area of a horizontal plane) in the second inflow ports 42x is sufficiently less than the refrigerant passage area of the second ascension space 62a and the second inflow space 62b (the area of a horizontal plane of the second ascension space 62a and the second inflow space 62b).

Further, like the first internal space 23a, the second internal space 23b has a loop structure that includes the second inflow ports 42x, the second partition plate 52, the second upper communicating passage 52x, and the second lower communicating passage 52y.

In the middle vicinity of the second flow regulation plate 42, the second blocking plate 62 partitions the second ascension space 62a to which the flat multi-perforated tube 121b is connected and the second inflow space 62b to which the interconnecting pipeline 24 is connected, while allowing these two spaces to be communicated through a second lower communicating port 62x at the bottom. The top end of the second blocking plate 62 extends to the bottom surface of the second flow regulation plate 42. The second lower communicating port 62x is disposed between the bottom end of the second blocking plate 62 and the top surface of the third baffle 23h.

In the present embodiment, as seen from the direction in which the flat multi-perforated tube 121b extends, the flat multi-perforated tube 121b is situated so that the opening in the end of the internal flow channel 21ba overlaps the opening in the end of the interconnecting pipeline 25 on the side connected to the second inflow space 62b.

In the present embodiment, as seen from the direction in which the flat multi-perforated tube 121b extends, the second blocking plate 62 is disposed so as to extend even lower than the bottom end portion of the opening in the end of the interconnecting pipeline 25 connected to the second inflow space 62b. Also as seen from the direction in which the flat multi-perforated tube 121b extends, the second blocking plate 62 is disposed so as to extend even lower than the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the second inflow space 62b. This arrangement is, though not particularly limited, such that when “the horizontal area of the section of the flat multi-perforated tube 121b that extends into the second ascension space 62a” is subtracted from “the horizontal area at heightwise locations within the second ascension space 62a where the flat multi-perforated tube 121b is not present,” the remaining area (the area of sections in which the refrigerant bypasses the flat multi-perforated tube 121b in the second ascension space 62a) is greater than the refrigerant passage area of the second lower communicating port 62x.

The details of the configuration of arrangement are otherwise the same as with the first internal space 23a, and accordingly are omitted here.

(4-5-3) Third Internal Space 23c

The third internal space 23c, which is third from the upper part of the doubled-back header collecting tube 23, is furnished with a third flow regulation plate 43 and a third partition plate 53, as shown in FIG. 6, and in simplified cross sectional view in FIG. 13, respectively.

The third flow regulation plate 43 is a generally disk-shaped plate member that partitions the third internal space 23c into a fourth internal space 23d (space located below) that is third from the bottom of the doubled-back header collecting tube 23, and a third outflow space 53a and a third loop space 53b which are located above.

The third partition plate 53 is a generally square plate member that partitions a space above the fourth internal space 23d in the third internal space 23c into a third outflow space 53a and a third loop space 53b. The third outflow space 53a is a space situated on the side at which the flat multi-perforated tubes 21b connect at their first ends in the third internal space 23c. The third loop space 53b is a space situated on the opposite side of the third partition plate 53 from the third outflow space 53a in the third internal space 23c.

At the upper part of the third internal space 23c is disposed a third upper communicating passage 53x constituted by a vertical gap between the bottom surface of the third baffle plate 23h and a top end section of the third partition plate 53.

At the lower part of the third internal space 23c is disposed a third lower communicating passage 53y constituted by a vertical gap between the top surface of the third flow regulation plate 43 and a bottom end section of the third partition plate 53. In the present embodiment, the third lower communicating passage 53y extends in a horizontal direction from the third loop space 53b side towards the third outflow space 53a side. An outlet at the third outflow space 53a side of this third lower communicating passage 53y is located further below the location of the bottommost of the flat multi-perforated tubes 21b connected to the third outflow space 53a.

Like the first flow regulation plate 41 and the second flow regulation plate 42, the third flow regulation plate 43 is furnished with two third inflow ports 43x, openings which are disposed at the side from which the flat multi-perforated tubes 21b extend in the third internal space 23c, and which provide communication in the vertical direction.

Also, like the first internal space 23a and the second internal space 23b, the third internal space 23c has a flow regulating structure in which the refrigerant passage area (the area of a horizontal plane) in the third inflow ports 43x is sufficiently smaller than the refrigerant passage area of the fourth internal space 23d (the area of the horizontal plane of the fourth internal space 23d).

Further, like the first internal space 23a and the second internal space 23b, the third internal space 23c has a loop structure that includes the third inflow ports 43x, the third partition plate 53, the third upper communicating passage 53x, and the third lower communicating passage 53y.

In this structure, the third internal space 23c is not connected to any interconnecting pipeline such as the interconnecting pipeline 24 connected to the first internal space 23a or the interconnecting pipeline 25 connected to the second internal space 23b, and refrigerant supplied from the fourth internal space 23d side below is supplied directly to the third internal space 23c without passing through an interconnecting pipeline or the like; therefore, there are no structures furnished that correspond to the first blocking plate 61, the first ascension space 61a, the first inflow space 61b, the first lower communicating port 61x, the second blocking plate 62, the second ascension space 62a, the second inflow space 62b, or the second lower communicating port 62x.

The details of the configuration of arrangement are otherwise the same as with the first internal space 23a and the second internal space 23b, and accordingly are omitted here.

(5) Overview of Flow of Refrigerant in Outdoor Heat Exchanger 20 During Heating Mode

The flow of refrigerant in the outdoor heat exchanger 20 constituted as shown above is described below, mainly in terms of the flow during heating mode.

As shown by an arrow in FIG. 5, during heating mode, refrigerant in a gas-liquid two-phase state is supplied to the lower outlet/inlet internal space 22b in the bottom part of the outlet/inlet header collecting tube 22 via the liquid refrigerant pipeline 32. In the description of the present embodiment, the state of the refrigerant inflowing to this lower outlet/inlet internal space 22b is assumed to be a gas-liquid two-phase state; however, depending on the outdoor temperature and/or the indoor temperature and/or the operational state, the inflowing refrigerant may be in a substantially single-phase liquid state.

The refrigerant supplied to the lower outlet/inlet internal space 22b in the bottom part of the outlet/inlet header collecting tube 22 passes through the plurality of flat multi-perforated tubes 21b in the bottom part of the heat exchange part 21 connected to the lower outlet/inlet internal space 22b, and is supplied respectively to the three fourth through sixth internal spaces 23d, 23e, 23f in the bottom part of the doubled-back header collecting tube 23. As the refrigerant supplied to the three fourth to sixth internal spaces 23d, 23e, 23f in the bottom part of the doubled-back header collecting tube 23 passes through the flat multi-perforated tubes 21b in the bottom part of the heat exchange part 21, a portion of the liquid phase component of the refrigerant in the gas-liquid two-phase state evaporates, thereby leading to a state in which the gas phase component is increased.

The refrigerant supplied to the sixth internal space 23f at the bottom of the doubled-back header collecting tube 23 passes through the interconnecting pipeline 24, and is supplied to the first internal space 23a (first to the first inflow space 61b) in the top part of the doubled-back header collecting tube 23. The refrigerant supplied to the first internal space 23a inflows respectively to the plurality of flat multi-perforated tubes 21b connected to the first internal space 23a (the flow of refrigerant within the first internal space 23a will be discussed below). The refrigerant flowing through the plurality of flat multi-perforated tubes 21b further evaporates into a gas phase state, and is supplied to the upper outlet/inlet internal space 22a at the upper part of the outlet/inlet header collecting tube 22.

The refrigerant supplied to the fifth internal space 23e in the bottom part of the doubled-back header collecting tube 23 passes through the interconnecting pipeline 25 to be supplied to the second internal space 23b (first to the second inflow space 62b) in the top part of the doubled-back header collecting tube 23. The refrigerant supplied to the second internal space 23b inflows respectively to the plurality of flat multi-perforated tubes 21b connected to the second internal space 23b (the flow of refrigerant within the second internal space 23b will be discussed below). The refrigerant flowing through the plurality of flat multi-perforated tubes 21b further evaporates into a gas phase state, and is supplied to the upper outlet/inlet internal space 22a at the upper part of the outlet/inlet header collecting tube 22.

The refrigerant supplied to the fourth internal space 23d in the bottom part of the doubled-back header collecting tube 23 passes upward on the vertical through the third inflow ports 43x furnished to the third flow regulation plate 43, and is supplied to the internal space of the third internal space 23c in the top part of the doubled-back header collecting tube 23. The refrigerant supplied to the third internal space 23c inflows respectively to the plurality of flat multi-perforated tubes 21b connected to the third internal space 23c (the flow of refrigerant within the third internal space 23c will be discussed below). The refrigerant flowing through the plurality of flat multi-perforated tubes 21b further evaporates into a gas phase state, and is supplied to the upper outlet/inlet internal space 22a at the upper part of the outlet/inlet header collecting tube 22.

The refrigerant which has flowed from the first to third internal spaces 23a, 23b, 23c in the top part of the doubled-back header collecting tube 23 through the flat multi-perforated tubes 21b and been supplied to the upper outlet/inlet internal space 22a at the upper part of the outlet/inlet header collecting tube 22 converges in the upper outlet/inlet internal space 22a, and flows out from the gas refrigerant pipeline 31.

In cooling mode, the refrigerant flow is the reverse of the flow indicated by arrows in FIG. 5.

(6) Flow of Refrigerant in Outdoor Heat Exchanger 20 in a Case of a Low Circulation Rate During Heating Mode

The flow of refrigerant in the outdoor heat exchanger 20 in a case of a low circulation rate during heating mode will be described below, taking the example of the first internal space 23a of the doubled-back header collecting tube 23.

The refrigerant inflowing to the lower outlet/inlet internal space 22b of the outlet/inlet header collecting tube 22 is depressurized in the expansion valve 33, and thereby enters a gas-liquid two-phase state. A portion of the liquid phase component in the refrigerant in the gas-liquid two-phase state that has flowed into to the first internal space 23a of the doubled-back header collecting tube 23 evaporates in the course of passage through the flat multi-perforated tubes 21b from the lower outlet/inlet internal space 22b of the outlet/inlet header collecting tube 22 towards the sixth internal space 23f of the doubled-back header collecting tube 23. Therefore, the state of the refrigerant inflowing through the interconnecting pipeline 24 to the first internal space 23a (first to the first inflow space 61b) of the doubled-back header collecting tube 23 is one of admixture of a gas phase component and a liquid phase component differing in specific gravity.

When the circulation rate is low, a small refrigerant amount per unit time flows into the first ascension space 61a through the first inflow space 61b and the first lower communicating port 61x, and the flow velocity of refrigerant inflowing to the first ascension space 61a is relatively slow. For this reason, as long as this flow velocity remains unchanged, the high-specific gravity liquid phase component in the refrigerant ascends with difficulty, and only with difficulty can reach the tubes at the upper part among the plurality of flat multi-perforated tubes 21b connected to the first internal space 23a, which can in some cases lead to uneven rates of passage through the plurality of flat multi-perforated tubes 21b, depending on their heightwise locations, and pose a risk of eccentric flow. Accordingly, as shown in the descriptive diagram of FIG. 14 which depicts a reference example during a low circulation rate, when the low-specific gravity gas phase component in the refrigerant flows mainly to the first end side of the flat multi-perforated tubes 21b that are situated relatively towards the top part, the degree of superheat of the refrigerant flowing out from the other end side of these flat multi-perforated tubes 21b becomes too great, phase change no longer occurs during passage through the flat multi-perforated tubes 21b, and heat exchange capability cannot be sufficiently achieved. Meanwhile, when the high-specific gravity liquid phase component in the refrigerant flows mainly into the first end side of the flat multi-perforated tubes 21b that are situated relatively towards the bottom, the refrigerant flowing out from the other end side of these flat multi-perforated tubes 21b does not easily reach superheat, and in some instances will reach the other end side of the flat multi-perforated tubes 21b without evaporating, so that ultimately heat exchange capability cannot be sufficiently achieved.

In contrast to this, with the outdoor heat exchanger 20 of the present embodiment, when the refrigerant supplied to the first ascension space 61a passes through the first inflow ports 41x of the first flow regulation plate 41, the first inflow ports having a throttling function, the flow velocity of the refrigerant flow on the vertical is increased. Moreover, because the space above the first flow regulation plate 41 in the first internal space 23a is furnished with the first partition plate 51, the refrigerant passage area of the space on the side where the first inflow ports 41x are disposed (the first outflow space 51a) is constituted so as to be narrower as compared to the case where the first partition plate 51 is absent, and therefore the ascending flow velocity does not readily decline. For this reason, even in cases of a low circulation rate, the high-specific gravity liquid phase component in the refrigerant can be easily guided to the upper part within the first outflow space 51a.

As the refrigerant inflowing to the first outflow space 51a via the first inflow ports 41x ascends within the first outflow space 51a, the flow is divided among the flat multi-perforated tubes 21b, but a small portion of the refrigerant is guided to the top end of the first outflow space 51a without flowing into the flat multi-perforated tubes 21b.

The refrigerant having reached the top end of the first outflow space 51a in this manner is guided into the first loop space 51b via the first upper communicating passage 51x, and through gravity descends in the first loop space 51b. The refrigerant having descended in the first loop space 51b flows in a horizontal direction while passing through the first lower communicating passage 51y which extends in the horizontal direction, and again returns to the lower part of the first outflow space 51a.

The refrigerant that has returned to the first outflow space 51a via the lower communicating passage 51y is entrained by the ascending flow of the refrigerant passing through the first inflow ports 41x and again ascends within the first outflow space 51a, and according to circumstances can be made to inflow to the flat multi-perforated tubes 21b after being recirculated through the first internal space 23a.

In so doing, in the outdoor heat exchanger 20 of the present embodiment, even at times of a low circulation rate, it is possible for the state of the refrigerant flowing into the plurality of flat multi-perforated tubes 21b arranged at sections of different heights to be brought into approximation with the state depicted in the descriptive diagram of FIG. 15, which shows a reference example during a medium circulation rate, and rendered as uniform as possible.

As seen from the longitudinal direction of the flat multi-perforated tube 121b connected to the first inflow space 61b, the first lower communicating port 61x and the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b are arranged so as to not overlap. Therefore, after the refrigerant has passed through the first lower communicating port 61x from the first inflow space 61b side to the first ascension space 61a side, the collective flow of refrigerant to the flat multi-perforated tube 121b can be suppressed.

The flat multi-perforated tube 121b connected to the first ascension space 61a is disposed so that the opening in the end of the internal flow channel 21ba thereof is at the same heightwise location as the opening in the end of the interconnecting pipeline 24, but because the first blocking plate 61 is located between the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b and the opening in the end of the interconnecting pipeline 24, the refrigerant flow that has passed through the end of the interconnecting pipeline 24 does not proceed directly to the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b, but is blocked by the first blocking plate 61. Therefore, the collective flow of refrigerant to the flat multi-perforated tube 121b disposed at the same height as the interconnecting pipeline 24 can be suppressed.

The second internal space 23b of the doubled-back header collecting tube 23 is the same as the first internal space 23a and is therefore not described.

The third internal space 23c of the doubled-back header collecting tube 23, unlike the first internal space 23a and the second internal space 23b described above, is not furnished with structures corresponding to the first blocking plate 61, the first ascension space 61a, the first inflow space 61b, the first lower communicating port 61x, the second blocking plate 62, the second ascension space 62a, the second inflow space 62b, and the second lower communicating port 62x; therefore, the effects provided by these structures do not occur, but other features are the same and are therefore not described.

(7) Flow of Refrigerant in Outdoor Heat Exchanger 20 in a Case of a High Circulation Rate During Heating Mode

The flow of refrigerant in the outdoor heat exchanger 20 in a case of a high circulation rate during heating mode will be described below, taking the example of the first internal space 23a of the doubled-back header collecting tube 23.

Here, just as in the case of a low circulation rate, the state of the refrigerant inflowing to the first internal space 23a of the doubled-back header collecting tube 23 is one of admixture of a gas phase component and a liquid phase component differing in specific gravity.

When the circulation rate is high, a large refrigerant amount per unit time flows into the first ascension space 61a through the interconnecting pipeline 24, the first inflow space 61b, and the first lower communicating port 61x, and the flow velocity of refrigerant inflowing to the first ascension space 61a is relatively fast. Moreover, the flow velocity is increased even further by the adoption of the throttling function of the first inflow ports 41x as the low circulation flow countermeasure discussed previously. Further, due to the narrow refrigerant passage area of the first outflow space 51a, the refrigerant passage area of which is constricted by the first partition plate 51 as the low circulation flow countermeasure discussed previously, there is almost no letdown in the ascension velocity of the refrigerant. For this reason, in cases of a high circulation rate, the high-specific gravity liquid phase component of the refrigerant passing forcefully through the first inflow ports 41x tends to pass through the first outflow space 51a without inflowing to the flat multi-perforated tubes 21b, and tends to collect at the upper part. In such cases, the high-specific gravity liquid phase component tends to collect at the upper part while low-specific gravity gas phase component tends to collect at the lower part, and ultimately, eccentric flow arises as shown in the descriptive diagram of FIG. 16, showing a reference example during a high circulation rate, although the distribution differs from that at times of a low circulation rate.

In contrast to this, with the outdoor heat exchanger 20 of the present embodiment, due to the adoption of the loop structure in the first internal space 23a, the refrigerant reaching the top end of the first outflow space 51a is guided into the first loop space 51b via the first upper communicating passage 51x, and after descending in the first loop space 51b is again returned to the first outflow space 51a via the first lower communicating passage 51y, and thereby can be guided into the flat multi-perforated tubes 21b located towards the lower part of the first outflow space 51a.

In so doing, in the outdoor heat exchanger 20 of the present embodiment, even at times of a high circulation rate, it is possible for the state of the refrigerant flowing into the plurality of flat multi-perforated tubes 21b arranged at sections of different heights to be brought into approximation with the state depicted in the descriptive diagram of FIG. 15, showing a reference example during a medium circulation rate, and to be rendered as uniform as possible.

As seen from the longitudinal direction of the flat multi-perforated tube 121b connected to the first inflow space 61b, the first lower communicating port 61x and the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b are arranged so as to not overlap. Therefore, similar to when the circulation rate is low as described above, after the refrigerant has passed through the first lower communicating port 61x from the first inflow space 61b side to the first ascension space 61a side, the collective flow of refrigerant to the flat multi-perforated tube 121b can be suppressed. This suppressing effect is more apparent during times of a high circulation rate with a high flow velocity.

The flat multi-perforated tube 121b connected to the first ascension space 61a is also disposed so that the opening in the end of the internal flow channel 21ba thereof is at the same heightwise location as the opening in the end of the interconnecting pipeline 24, but similar to when the circulation rate is low as described above, because the first blocking plate 61 is located between the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b and the opening in the end of the interconnecting pipeline 24, the refrigerant flow that has passed through the end of the interconnecting pipeline 24 does not proceed directly to the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b, but is blocked by the first blocking plate 61. The blocking effect of the first blocking plate 61 is more apparent during times of a high circulation rate with a high flow velocity. It is thus possible to suppress the collective flow of refrigerant to the flat multi-perforated tube 121b disposed at the same height as the interconnecting pipeline 24 during times of a high circulation rate.

The second internal space 23b of the doubled-back header collecting tube 23 is the same as the first internal space 23a and is therefore not described.

(8) Characteristics of Outdoor Heat Exchanger 20 of Air Conditioning Apparatus 1

(8-1)

With the outdoor heat exchanger 20 of the present embodiment, even in cases of a low circulation rate, the ascent velocity of the refrigerant in the first inner space 23a of the doubled-back header collecting tube 23 is maintained by the configurations of the first inflow ports 41x and the first outflow space 51a constricted by the first partition plate 51, so that the refrigerant can more easily reach the upper part of the first outflow space 51a (the design of the second internal space 23b and the third internal space 23c is the same).

Additionally, with the outdoor heat exchanger 20 of the present embodiment, even in cases of a high circulation rate, the refrigerant loops around within the first internal space 23a due to the loop structure adopted in the first internal space 23a of the doubled-back header collecting tube 23, whereby the refrigerant can be guided into the flat multi-perforated tubes 21b.

In the above manner, with the outdoor heat exchanger 20 of the present embodiment, both in cases of a low circulation rate and cases of a high circulation rate, eccentric flow of refrigerant to the plurality of flat multi-perforated tubes 21b arranged side by side in the vertical direction can be kept to a minimum.

(8-2)

In the outdoor heat exchanger 20 of the present embodiment, the loop structure and the flow regulating structure are adopted not in the upper outlet/inlet internal space 22a and the lower outlet/inlet internal space 22b of the outlet/inlet header collecting tube 22, and not in the fourth through sixth internal spaces 23d, 23e, 23f of the doubled-back header collecting tube 23, but in the first through third internal spaces 23a, 23b, 23c of the doubled-back header collecting tube 23. Specifically, the loop structure and the flow regulating structure are adopted in the first to third internal spaces 23a, 23b, 23c of the doubled-back header collecting tube 23, in which the refrigerant flowing therethrough in heating mode contains large amounts of admixed gas phase and liquid phase components, resulting in a marked tendency for eccentric flow to arise among the flat multi-perforated tubes 21b at different heights.

Therefore, it is possible for the effect of suppressing eccentric flow of the refrigerant to be sufficiently realized.

(8-3)

The refrigerant which has passed through the first inflow ports 41x of the outdoor heat exchanger 20 of the present embodiment and just flowed into the first outflow space 51a is at maximum ascent velocity, and in some instances tends not to pass through the lower tubes among the plurality of flat multi-perforated tubes 21b connected to the first outflow space 51a.

In contrast, with the outdoor heat exchanger 20 of the present embodiment, the outlet at the first outflow space 51a side of the first lower communicating passage 51y is arranged such the refrigerant descending in the first loop space 51b in the first internal space 23a of the doubled-back header collecting tube 23 can be guided into the flat multi-perforated tubes 21b that are connected to the lower part of the first outflow space 51a.

For this reason, the flat multi-perforated tubes 21b that are located at the lower part, through which the high-flow velocity refrigerant inflowing to the first outflow space 51a via the first inflow ports 41x tends not to pass, can be easily supplied with the refrigerant that has been returned to the first outflow space 51a via the first lower communicating passage 51y.

The above feature is the same for the second internal space 23b and the third internal space 23c as well.

(8-4)

With the outdoor heat exchanger 20 of the present embodiment, not only are the flat multi-perforated tubes 21b connected to the first outflow space 51a, but the flat multi-perforated tube 121b is connected to the first ascension space 61a as well. Therefore, the area used for heat exchange in the heat exchange part 21 of the outdoor heat exchanger 20 can be enlarged.

Further, with the outdoor heat exchanger 20 of the present embodiment, as seen from the longitudinal direction of the flat multi-perforated tube 121b connected to the first inflow space 61b, the first lower communicating port 61x and the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b are arranged so as to not overlap, and it is therefore possible to suppress the collective flow of refrigerant that has passed through the first lower communicating port 61x into the flat multi-perforated tube 121b. Moreover, when the circulation rate is high with a high flow velocity, the suppressing effect can be exhibited even more apparently.

The opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the first ascension space 61a is disposed so as to face the opening in the end of the interconnecting pipeline 24 at the same heightwise location, but because the first blocking plate 61 is located between these openings, the first blocking plate 61 can block the refrigerant flow passing through the end of the interconnecting pipeline 24 and attempting to head to the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b. The collective flow of refrigerant to the flat multi-perforated tube 121b disposed at the same height as the interconnecting pipeline 24 can thereby be suppressed. Moreover, when the circulation rate is high with a high flow velocity, the suppressing effect of the first blocking plate 61 can be exhibited even more apparently.

The above feature is the same for the second internal space 23b as well.

(9) Additional Embodiments

The preceding embodiment has been described as but one example of embodiment of the present invention, but is in no way intended to limit the invention of the present application, which is not limited to the aforedescribed embodiment. The scope of the invention of the present application would as a matter of course include appropriate modifications that do not depart from the spirit thereof.

(9-1) Additional Embodiment A

In the aforedescribed embodiment, an example was described of a case in which the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the first ascension space 61a and the opening in the end of the interconnecting pipeline 24 were disposed so as to face each other while overlapping as seen from the longitudinal direction of the flat multi-perforated tube 121b (similar to the flat multi-perforated tube 121b and the interconnecting pipeline 25 in the second ascension space 62a).

Moreover, the present invention is not limited to this arrangement, and if the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the first ascension space 61a and the first lower communicating port 61x are disposed so as to not overlap as seen from the longitudinal direction of the flat multi-perforated tube 121b, the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b and the opening in the end of the interconnecting pipeline 24 may be disposed so as to not overlap, and the first lower communicating port 61x and the opening in the end of the interconnecting pipeline 24 may also be disposed so as to overlap.

The above feature is the same for the flat multi-perforated tube 121b and the interconnecting pipeline 25 in the second ascension space 62a as well.

(9-2) Additional Embodiment B

In the aforedescribed embodiment, an example was described of a doubled-back header collecting tube 23 having a first lower communicating port 61x configured by the bottom-end section of the first blocking plate 61 and the top-surface section of the second baffle 23g (the second lower communicating port 62x is the same).

However, the present invention is not limited to this arrangement; it would be acceptable to adopt, for example, a doubled-back header collecting tube 123 like that shown in FIG. 17, in place of the doubled-back header collecting tube 23 of the aforedescribed embodiment.

The doubled-back header collecting tube 123 is furnished with a first lower communicating port 161x passing through the plate thickness direction so as to link the first inflow space 61b and the first ascension space 61a, below a first blocking plate 161. The entire bottom-end section of the first blocking plate 161 is supported by being in contact with the top surface of the second baffle 23g. In this embodiment as well, as seen from the direction in which the flat multi-perforated tube 121b extends, the opening in the end of the interconnecting pipeline 24 on the side connected to the first inflow space 61b is arranged so as not to overlap the first lower communicating port 161x.

This case differs from the aforedescribed embodiment in that there is no need to adjust the heightwise location of the first blocking plate 161 in order to adjust the refrigerant passage area of the first lower communicating port 161x, and the structure can be simplified because the first lower communicating port 161x of the first blocking plate 161 may be designed so as to have a desired refrigerant flow channel area.

(9-3) Additional Embodiment C

It would be acceptable to adopt, for example, a doubled-back header collecting tube 223 like that shown in FIG. 18, in place of the doubled-back header collecting tube 23 of the aforedescribed embodiment.

The doubled-back header collecting tube 223 is configured so that part of the bottom-end section of a first blocking plate 261 is recessed upward. Therefore, with the first blocking plate 261 placed on the top surface of the second baffle 23g, a first lower communicating port 261x can be configured by the top surface (a flat surface) of the second baffle 23g and the upwardly recessed section of the bottom-end section of the first blocking plate 261.

This case differs from the aforedescribed embodiment in that there is no need to adjust the heightwise location of the first blocking plate 261 in order to adjust the refrigerant passage area of the first lower communicating port 261x, the size of the recessed section of the bottom-end section of the first blocking plate 261 may be designed in advance so as to have a desired refrigerant flow channel area, and the structure can be simplified. Moreover, the section not recessed in the bottom-end section of the first blocking plate 261 can be supported by being arranged to as to be in contact with the top surface of the second baffle 23g.

(9-4) Additional Embodiment D

In the aforedescribed embodiment, as seen from the longitudinal direction of the flat multi-perforated tube 121b, an example was described of a case in which the first lower communicating port 61x was arranged even lower than the lowest positioned section of the flat multi-perforated tube 121b connected to the first ascension space 61a (the second lower communicating port 62x is the same).

However, the present invention is not limited to this arrangement, for example, as seen in the longitudinal direction of the flat multi-perforated tube 121b, if the opening in the end of the internal flow channel 21ba of the flat multi-perforated tube 121b connected to the first ascension space 61a and the first lower communicating port 61x are disposed so as to not overlap, the flat multi-perforated tube 121b having the internal flow channel 21ba may be disposed lower than the first lower communicating port 61x.

The above feature is the same for the flat multi-perforated tube 121b and the second lower communicating port 62x in the second ascension space 62a as well.

(9-5) Additional Embodiment E

In the aforedescribed embodiment, an example was described of a case in which the first partition plate 51 and the first blocking plate 61 were disposed separately, above and below the first flow regulation plate 41 (the second partition plate 52 and the second blocking plate 62 above and below the second flow regulation plate 42 are the same).

However, the present invention is not limited to this arrangement, and, for example, the first partition plate 51 and the first blocking plate 61 may be configured integratedly so as to be continuous in the vertical direction.

This feature is the same for the second partition plate 52 and the second blocking plate 62 above and below the second flow regulation plate 42.

(9-6) Additional Embodiment F

In the aforedescribed embodiment, there was described an example of a case in which the first flow regulation plate 41, a plate-shaped member, is furnished with the first inflow ports 41x that open in the thickness direction (as do the second inflow ports 42x and the third inflow ports 43x).

However, the present invention is not limited to this arrangement, and, for example, a cylindrical inflow passage extending in the vertical direction could be furnished in place of inflow ports formed by openings in a plate-shaped member. In this case, it will be possible to further boost the velocity of the refrigerant outflowing vertically upward as the refrigerant passes through the cylindrical inflow passage.

The above feature could be implemented analogously in the second inflow ports 42x and the third inflow ports 43x as well.

(9-7) Additional Embodiment G

In the aforedescribed embodiment and additional embodiments, there were described examples of cases in which the space above the first flow regulation plate 41 of the first internal space 23a, the space above the second flow regulation plate 42 of the second internal space 23b, and the space above the third flow regulation plate 43 in the third internal space 23c are similar in form.

However, the present invention is not limited to this arrangement; it would be acceptable for the forms to differ from one another.

(9-8) Additional Embodiment H

In the aforedescribed embodiment, there was described an example of a case in which flat plate members like the heat transfer fins 21a shown in FIGS. 7 and 8 are employed as heat transfer fins.

However, the present invention is not limited to this arrangement, and application, for example, to a heat exchanger employing corrugated type heat transfer fins, such as those employed primarily in automotive heat exchangers, would also be possible.

Number	Date	Country
2-219966	Sep 1990	JP
5741680	Jul 2015	JP
2009022575	Feb 2009	WO

Heat exchanger and air conditioning apparatus

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Entry
International Preliminary Report of corresponding PCT Application No. PCT/JP2014/083944 dated Jul. 7, 2016.
International Search Report of corresponding PCT Application No. PCT/JP2014/083944 dated Apr. 7, 2015.
The extended European search report for the corresponding European application No. 14873394.2 issued on Jan. 5, 2017.