heat exchanger and air conditioner device

专利摘要:
HEAT EXCHANGER AND AIR CONDITIONER. A heat exchanger and an air conditioner capable of inhibiting irregular refrigerant flow are provided even when used under conditions when the circulation flow changes. A plurality of flat perforated tubes (21b) are connected at different heights to a first internal space (23a) of a return junction collection tube (23) of an open-air heat exchanger (20). The first internal space (23a) uses a loop structure that includes a first partition plate (51), a first entrance (41x), a first upper communication passage (51x) and a first lower communication passage (51y). The first dividing plate (51) divides the first internal space (23a) into a first outflow space (51a) and a first loop space (51b). The first inlet (41x) is provided at the bottom of the first outlet flow space (51a) in such a way that the refrigerant rises in the first outlet flow space (51a). Refrigerant that reaches the upper end of the first outlet flow space (51a) is guided to the first loop space (51b) via the first upper communication passage (51x), and the refrigerant that (...).
公开号:BR112016006545B1
申请号:R112016006545-0
申请日:2014-07-10
公开日:2020-12-01
发明作者:Satoshi Inoue；Hirokazu Fujino；Masanori Jindou；Kousuke Morimoto
申请人:Daikin Industries, Ltd.；
IPC主号:

专利说明:

[001] The present invention relates to a heat exchanger and an air conditioning device. BACKGROUND TECHNIQUE
[002] Heat exchangers of a design having a plurality of flat tubes, fins which are joined to the plurality of flat tubes and junction collection tubes which are respectively coupled to the plurality of flat tubes on one end and on the other side of the end thereof, to effect heat exchange between a refrigerant flowing through the interior of the flat tubes and air flowing outside the flat tubes, are known in the prior art.
[003] For example, the heat exchanger disclosed in Patent Literature 1 (Japanese Open Patent No. 2-219966) is configured in such a way that a plurality of outflow tubes extending in a horizontal direction is connected in a and the other end to junction collection tubes that respectively extend in a vertical direction.
[004] The heat exchanger revealed in Patent Literature 1 is directed to the problem where, inside the junction collection tubes that extend in the vertical direction, high specific gravity liquid phase refrigerant accumulates towards the bottom whereas low specific gravity gas phase refrigerant accumulates towards the top, thereby giving rise to eccentric flow; in order to solve this problem, the feature of forming a choke inside the junction collection tubes is proposed.
[005] Passing the refrigerant through the choke formed in this mode facilitates mixing of the gas phase refrigerant and the liquid phase refrigerant, while at the same time increasing the flow speed, making it easy for the refrigerant to reach the top within the junction collection tubes, thereby minimizing eccentric refrigerant flow. SUMMARY OF THE INVENTION TECHNICAL PROBLEM
[006] However, in a heat exchanger such as that disclosed in Patent Literature 1 indicated above, it has not been considered in any way to minimize eccentric flow as may occur under conditions in which the refrigerant circulation rate varies; and no consideration whatsoever has been given to a structure that would provide the effect of minimizing eccentric flow, both in cases of low circulation rate and in cases of high circulation rate.
[007] Specifically, in the case of a low circulation rate, it is possible to increase the flow speed when forming a choke, inducing the refrigerant to reach the upper part inside the junction collection tube, thereby minimizing eccentric flow; in the case of a high circulation rate, however, the flow velocity becomes very high because of the choke, and the liquid phase refrigerant of high specific gravity accumulates to an excessive extent towards the top, giving rise in some instances eccentric flow.
[008] On the other hand, although, in the case of a high circulation rate, it is possible to minimize eccentric flow by providing a choke that has been adjusted so that the flow speed does not become too high, when the choke is adjusted in this mode in the case of a low circulation rate it can be difficult for the refrigerant to reach the top, giving rise in some instances to eccentric flow.
[009] With the foregoing in view, an objective of the present invention is to provide a heat exchanger and an air conditioning device with which it is possible to minimize eccentric flow of the refrigerant, even when used in conditions in which the rate of circulation varies. SOLUTION TO THE PROBLEM
[0010] The heat exchanger according to a first aspect of the present invention is provided with a plurality of flat tubes, a junction collection tube and a plurality of fins. The plurality of flat tubes are arranged mutually. The junction collection tube has the ends of the flat tubes connected to it, and extends in a vertical direction. The plurality of fins are attached to the flat tubes. The junction collection tube has a loop structure. The loop structure includes split components, inlet flow ports, overhead passages and underpass passages. The split components divide internal spaces into first spaces that are spaces on the side where the flat tubes are connected, and second spaces that are spaces on the opposite side to the side where the flat tubes are connected to the first space. The inlet flow ports are located in the lower parts of the first spaces, and in the case of functioning as a refrigerant evaporator they stimulate the refrigerant inlet flow in order to give rise to an upward flow within the first spaces. The upper communication passages are located in the upper parts of the first spaces and the second spaces, and provide communication between the upper parts of the first spaces and the second spaces, thereby guiding the refrigerant that has risen within the first spaces to the second spaces. The lower communication passages are located in the lower parts of the first spaces and the second spaces, provide communication between the lower parts of the first spaces and the second spaces, and when guiding the refrigerant in a direction other than the vertical direction of the second spaces to spaces above the entrance flow ports in the first spaces, guide the refrigerant from the first spaces to the second spaces, and return the refrigerant having descended through the second spaces from the second spaces to the first spaces. In this document, "inlet port" is used to include not only openings that are provided for components in the form of thin plates, but also where inlet flow passages created for inlet form are provided, the outlets thereof as well. The "direction other than the vertical direction" in this document is not particularly limited as long as it is a direction from the second spaces to spaces above the inlet ports in the first spaces, and may include, for example, a horizontal direction from the second space side to first space side; an inclined direction to the first space side from the second space side would also be acceptable. A slope of 60 degrees or less with respect to the horizontal direction would be an acceptable slope, just as it would be one of 30 degrees or less; and an inclination of -60 degrees or greater with respect to the horizontal direction would be acceptable, as would an inclination of -30 degrees or greater.
[0011] With this heat exchanger, the internal spaces of the junction collection tube are divided by the dividing components in the first spaces and in the second spaces, so the area through which the refrigerant flowed to the first spaces coming from the doors of incoming flow passes while ascending through the first spaces can be made smaller, when compared to the case in which the first spaces and the second spaces are not divided by dividing components. For this reason, even when the refrigerant circulation rate is a low circulation rate, the refrigerant having flowed into the first spaces from the inlet flow ports can be induced to ascend through the reduced spaces of the first spaces only, so the refrigerant can easily reach the upper parts of the internal spaces of the junction collection tubes without experiencing any significant drop in the speed of the refrigerant rising through the first spaces. For this reason, even when the refrigerant circulation rate is a low circulation rate, sufficient flow of the refrigerant into the flat tubes arranged towards the top is possible.
[0012] In addition, in this heat exchanger, the junction collection tube has a loop structure that includes the inlet flow ports, the split components, the upper communication passages and the lower communication passages. For this reason, even when the flow rate of the refrigerant flowing into the first spaces from the inlet flow ports is high, as can be found at high circulation rates, and the high specific gravity refrigerant is forced through while crossing the flat tubes located towards the bottom resulting in a tendency to accumulate in upper parts of the first spaces, it is possible for the refrigerant of high specific gravity having reached upper sections of the first spaces to be returned to the lower parts of the first spaces by means of loop structure. Specifically, with this loop structure, it is possible for the refrigerant having reached upper sections of the first spaces to pass through the upper communication passages and be supplied to the second space side, and then descend through the second spaces and flow through the communication passages. lower to lower parts of the first spaces, and thereby guided into the flat tubes that are present in the lower parts of the first spaces. For this reason, even when the flow rate of the refrigerant flowing into the first spaces is high, as can be found at high circulation rates, and the refrigerant of high specific gravity is forced through the flat pipes located in the direction from the bottom resulting in a tendency to accumulate in the upper parts of the first spaces, sufficient flow of the refrigerant into the flat tubes at the bottom is possible.
[0013] And in so doing, it is possible that eccentric flow of the refrigerant in flat tubes located at different heights is kept to a minimum, even during periods of high circulation rate or in periods of low circulation rate.
[0014] A heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect of the present invention, in which the lower communication passages are arranged above the inlet flow ports, close to the lower flat tubes above the inlet flow ports. The lowest flat tubes above the inlet flow ports are those located in the lowest locations between the flat tubes located above the inlet flow ports. As long as the lower communication passages of this heat exchanger are located above the inlet flow ports and close to the lower flat tubes above the inlet flow ports, the passages can be arranged above the inlet flow ports at locations in the the same height as the lower flat tubes above the inlet flow ports, or in places below it. It is also acceptable that only the exits of the lower communication passages are located above the inlet flow port and close to the lower flat tubes above the inlet flow ports.
[0015] With this heat exchanger, in cases where the flow rate of the refrigerant passing through the inlet flow ports is high, as is found in the case of a high circulation rate, in some instances the velocity refrigerant particularly high, having passed exactly through the inlet flow ports, it passes through the lower flat tubes above the inlet flow ports, which of these above the inlet flow ports are located farther from the bottom, making flow entrance to the lower flat tubes above the difficult entry flow ports. With this heat exchanger, however, even in such cases, the refrigerant having been forced through the inlet flow ports is guided to the second spaces via upper communication passages in the upper parts of the first spaces, and after descending through the second spaces it crosses the lower communication passages and towards the lower parts of the first spaces, making it possible to be guided sufficiently into the lower flat tubes above the inlet flow ports.
[0016] A heat exchanger according to a third aspect of the present invention is the heat exchanger according to the first or second aspect of the present invention, in which flow regulation spaces are formed in the lower parts of the first spaces and seconds spaces between internal spaces. The first and second spaces and the flow regulation spaces are divided by flow regulation components. Inlet flow ports are provided for flow regulation components, in such a way that the cross-sectional area of refrigerant passage from the flow regulation spaces in the direction of the first spaces can be strangled.
[0017] With this heat exchanger, the refrigerant flowing from the flow regulation spaces below to the first spaces above can pass through the inlet flow ports that are arranged in order to strangle the passage cross-sectional area. And in so doing, the flow rate of the refrigerant flow from the flow regulation spaces to the first spaces through the inlet flow ports can be increased, and an upward flow of refrigerant through the first spaces can be easily produced. Additionally, because the first spaces, the second spaces and the flow regulation spaces are arranged within the junction collection tube, there is no need to provide any arrangement, except the junction collection tube, in order to produce an upward flow of the refrigerant through the first spaces.
[0018] A heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to the third aspect of the present invention, wherein the lower communication passages are constituted by means of lower sections of the dividing components and upper sections of the flow regulation components.
[0019] With this heat exchanger, because the lower communication passages are made up of lower sections of the division components and upper sections of the flow regulation components, even if liquid phase refrigerant accumulates in the second spaces, the refrigerant of liquid phase is induced to flow, due to gravity, towards the first space side along the upper sections of the flow regulation components and pass through the lower communication passages, thus making it possible to return to the first spaces easily .
[0020] A heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to anyone from the first to the fourth aspect of the present invention, wherein the loop structure is arranged in locations such that when a function such as an evaporator for the refrigerant is performed, it is possible for the refrigerant, after having passed through a part of the plurality of flat tubes, to flow in a distributed manner to another part of the plurality of flat tubes.
[0021] With this heat exchanger, when a function such as from an evaporator to the refrigerant is performed, part of the refrigerant evaporates during passage through part of the plurality of flat tubes. For this reason, the refrigerant, after having passed through the plurality of flat tubes, is a mixture of a gas phase component and a liquid phase component. In a different way to cases involving only the gas phase or only the liquid phase, when refrigerant containing a mixture like this of a gas phase component and a liquid phase component differing in specific gravity, it crosses a collection tube from a exchanger junction heat of conventional construction, when the flow rate is low, the liquid phase component tends to accumulate below and the gas phase component tends to accumulate above, while when the flow rate is high the liquid phase component tends to accumulate above and the gas phase component tends to accumulate below, making eccentric flow between the plurality of flat tubes arranged at different heights particularly prone to occur.
[0022] In contrast, with this heat exchanger, the loop structure is arranged in a location such that refrigerant containing a mixture of a gas phase component and a liquid phase component differing in specific gravity additionally experiences flow in mode distributed to another part of the flat pipe plurality, so it is possible to effectively minimize eccentric flow of refrigerant flows.
[0023] A heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to the fifth aspect of the present invention, in which the plurality of flat tubes is connected at the ends of them to a collection tube return junction that includes the junction collection tube and returns the refrigerant flow, and at the other ends is connected to a confronting junction collection tube arranged facing the return junction collection tube. The plurality of flat tubes are grouped into an upper side heat exchange area, and a lower side heat exchange area located below the upper side heat exchange area. The upper side heat exchange area consists of one or a plurality of arranged upper side heat exchange parts. The bottom side heat exchange area consists of one or a plurality of bottom side heat exchange parts arranged vertically. An internal space on the bottom facing side, corresponding to the heat exchange parts on the bottom side constituting the heat exchange area on the bottom side, is formed on the bottom side of the interior of the collating junction collection tube.
[0024] The interior of the return junction collection tube is divided vertically into internal spaces on the upper return side and internal spaces on the lower return side. The internal spaces of the upper return side correspond in number to the number of the heat exchange parts on the upper side constituting the heat exchange area on the upper side. The internal spaces on the lower side of the return correspond in number to the number of heat exchange parts on the lower side constituting the heat exchange area on the lower side. The internal spaces on the upper return side and the internal spaces on the lower return side communicate with each other. The loop structure is arranged in the internal spaces of the upper return side.
[0025] With this heat exchanger, because of a loop structure being arranged in the internal spaces of the upper return side, it is possible that eccentric flow of a two-phase liquid-gas refrigerant containing a gas phase component having evaporated in the passage path through the heat exchange area on the lower side, and which is supplied from the internal spaces on the lower return side to the internal spaces on the upper return side, is effectively minimized when the refrigerant flows towards the parts of top side heat exchange.
[0026] An air conditioning device according to a seventh aspect of the present invention is provided with a refrigerant circuit. The refrigerant circuit is formed by connecting the heat exchanger according to any one of the first to the sixth aspects of the present invention, and a variable capacity compressor.
[0027] With this air conditioning device, activation by the variable capacity compressor causes the rate at which the refrigerant flowing through the refrigerant circuit oscillates, and the amount of refrigerant passing through the heat exchanger oscillates. In cases where the heat exchanger works as an evaporator it will be possible to keep eccentric flow of the refrigerant inside the heat exchanger to a minimum, even when the amount of refrigerant passing through it increases and the liquid phase refrigerant mixing ratio increases, or the flow speed increases. ADVANTAGE EFFECTS OF THE INVENTION
[0028] With the heat exchanger according to the first aspect of the present invention, it is possible to minimize eccentric flow of the refrigerant to flat tubes located at different heights, during both periods of a low circulation rate and periods of a circulation rate high.
[0029] With the heat exchanger according to the second aspect of the present invention, it is possible for the refrigerant to be guided sufficiently to the lower flat tubes above the inlet flow ports.
[0030] With the heat exchanger according to the third aspect of the present invention, an upward flow of refrigerant in the first spaces is easily produced by the junction collection tube alone.
[0031] With the heat exchanger according to the fourth aspect of the present invention, it is possible that liquid phase refrigerant accumulating in the second spaces is easily returned to the first spaces.
[0032] With the heat exchanger according to the fifth aspect of the present invention, it is possible to effectively minimize eccentric flow of the refrigerant flow.
[0033] With the heat exchanger according to the sixth aspect of the present invention, it is possible to effectively minimize the eccentric flow of the refrigerant flow as a two-phase liquid-gas refrigerant in the first internal spaces on the upper side flows in the direction of the upper side heat exchange parts.
[0034] With the air conditioning device according to the seventh aspect of the present invention, in cases in which the heat exchanger functions as an evaporator, it is possible to maintain eccentric flow of the refrigerant within the heat exchanger to a minimum, even when the amount of refrigerant passing through it increases and the mixing ratio of liquid phase refrigerant increases, or the flow rate increases. BRIEF DESCRIPTION OF THE DRAWINGS
[0035] Figure 1 is a circuit diagram of the general view of the scheme of an air conditioning device according to a modality;
[0036] Figure 2 is a perspective view from the outside of an open air conditioning unit;
[0037] Figure 3 is a schematic cross-sectional view of an overview of placing machinery in an open air conditioning unit;
[0038] Figure 4 is a simplified external perspective view of an open-air heat exchanger, a gas refrigerant pipeline and a liquid refrigerant pipeline;
[0039] Figure 5 is a schematic rear view of a simplified configuration of an open-air heat exchanger;
[0040] Figure 6 is a simplified rear view of an open-air heat exchanger configuration;
[0041] Figure 7 is an enlarged cross-sectional view fragmented from a configuration of a heat exchange part of an open-air heat exchanger;
[0042] Figure 8 is a simplified perspective view of the heat transfer fins attached to an open-air heat exchanger;
[0043] Figure 9 is a simplified perspective view of a section near the top of a return junction collection tube;
[0044] Figure 10 is a simplified cross-sectional view of the vicinity of a first internal space of a return junction collection tube;
[0045] Figure 11 is a simplified top view of the proximity of a first internal space of a return junction collection tube;
[0046] Figure 12 is a simplified cross-sectional view of the proximity of a second internal space of a return junction collection tube;
[0047] Figure 13 is a simplified cross-sectional view of the vicinity of a third internal space of a return junction collection tube;
[0048] Figure 14 is a descriptive diagram for reference purposes, showing a refrigerant distribution condition at a low circulation rate;
[0049] Figure 15 is a descriptive diagram for reference purposes, showing a refrigerant distribution condition at an average circulation rate;
[0050] Figure 16 is a descriptive diagram for reference purposes, showing a refrigerant distribution condition at a high circulation rate;
[0051] Figure 17 is a simplified perspective view of a section near the top of a return junction collection tube according to another F mode; and
[0052] Figure 18 is a simplified configuration perspective view of a section near the top of a return junction collection tube according to another G modality. DESCRIPTION OF MODALITIES (1) Total Air Conditioning Device Configuration 1
[0053] Figure 1 is a circuit diagram describing an overview of a configuration of an air conditioning device 1 according to an embodiment of the present invention.
[0054] This air conditioning device 1 is a device used for cooling and heating, by means of vapor compression cooling cycle operation, of a building interior in which an indoor air conditioning unit 3 has been installed, and consists of an open air conditioning unit 2 as a heat source side unit and an indoor air conditioning unit 3 as a user side unit, which are connected through the refrigerant interconnection pipes 6, 7.
[0055] The refrigerant circuit consisting of the connection of the air conditioning open-air unit 2, the air conditioning closed-air unit 3 and the refrigerant interconnecting pipes 6, 7 is additionally constituted when connecting a compressor 91 , a four-way switching valve 92, an indoor heat exchanger 20, an expansion valve 33, an indoor heat exchanger 4, an accumulator 93 and more, by means of refrigerant piping. A refrigerant is sealed within this refrigerant circuit, and a cooling cycle operation involving compression, cooling, depressurization and heating / evaporation of the refrigerant, followed by further compression, is performed. As the refrigerant, one selected, for example, from R410A, R32, R407C, R22, R134a, carbon dioxide and more can be used. (2) Detailed Air Conditioning Device Configuration 1 (2-1) Indoor Air Conditioning Unit 3
[0056] The indoor air conditioning unit 3 is installed when mounted on a wall in an indoor wall or the like, or when being embedded or suspended in an indoor ceiling of a building or the like. The indoor air conditioning 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 type heat exchanger. transverse fins, consisting of a heat transfer tube and a multiplicity of fins. In cooling mode, the heat exchanger works as an evaporator for the refrigerant to cool the indoor air, and in heating mode it works as a condenser for the refrigerant to heat the indoor air. (2-2) Open Air Conditioning Unit 2
[0057] The outdoor air conditioning unit 2 is installed outside a building or the like, and is connected to the indoor air conditioning unit 3 by the refrigerant interconnecting pipes 6, 7. Such as shown in figure 2 and figure 3, the open air conditioning unit 2 has a unit wrap 10 of substantially cuboid shape.
[0058] As shown in figure 3, the open air conditioning unit 2 has a structure (a "suitcase" type structure) in which a blower chamber S1 and a machinery chamber S2 are formed at the dividing an internal space of the unit wrap 10 in two by means of a partition panel 18 which extends in a vertical direction. The air conditioning open-air unit 2 includes an open-air heat exchanger 20 and an open-air fan 95 which are arranged within the blower chamber S1 of unit wrap 10, and also includes compressor 91, the valve four-way switching system 92, the accumulator 93, the expansion valve 33, a gas refrigerant piping 31 and a liquid refrigerant piping 32 which are arranged within the machinery chamber S2 of the unit casing 10.
[0059] Unit wrap 10 constitutes a frame and is provided with a bottom panel 12, a top panel 11, a side panel 13 on the blower chamber side, a side panel 14 on the machinery chamber side, a fan chamber side panel 15 and machinery chamber side panel 16.
[0060] The open air conditioning unit 2 is configured in such a way that open air is drawn into the blower chamber S1 within the unit wrap 10 through parts of the rear surface and the side surface of the unit casing 10, and the pulled open air is vented through the front surface of unit casing 10. In specific terms, an inlet port 10a and an inlet port 10b facing the blower chamber S1 within the casing of unit 10 they are formed between the rear face side end of the side panel 13 on the blower chamber side and the blower chamber side end S1 of the side panel 14 on the machinery chamber side. The blower chamber side front panel 15 is provided with a passage 10c, the front side of which is covered by a fan grid 15a.
[0061] Compressor 91 is, for example, a sealed compressor driven by a compressor motor, and is configured in such a way that the operating capacity can be varied by means of inverter control.
[0062] The four-way switching valve 92 is a mechanism for switching the flow direction of the refrigerant. In cooling mode, the four-way switching valve 92 connects a refrigerant pipeline that extends from the discharge side of the compressor 91 and the gaseous refrigerant pipeline 31 that extends from one end (the gas side end) of the open-air heat exchanger 20, as well as connecting, via accumulator 93, the refrigerant interconnecting pipeline 7 for the gas refrigerant and the refrigerant piping on the inlet side of the compressor 91 (see full lines of the switching valve four 92 in Figure 1). In heating mode, the four-way switching valve 92 connects the refrigerant piping that extends from the discharge side of the compressor 91 and the refrigerant interconnecting pipeline 7 to the gaseous refrigerant, as well as connecting, via accumulator 93, the inlet side of compressor 91 and gaseous refrigerant piping 31 extending from one end (the gas side end) of the open-air heat exchanger 20 (see dashed lines of the four-way switching valve 92 in the figure 1).
[0063] The open-air heat exchanger 20 is arranged upright in the blower chamber S1, and confronts the inlet ports 10a, 10b. The indoor heat exchanger 20 is a heat exchanger made of aluminum; in the present modality, one having a design pressure of about 3-4 MPa is employed. The gaseous refrigerant piping 31 extends from one end (the gas side end) of the open-air heat exchanger 20 in order to connect to the four-way switching valve 92. The liquid refrigerant piping 32 extends the other end (the liquid side end) of the open-air heat exchanger 20, in order to connect to the expansion valve 33.
[0064] 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 to separate the refrigerant into a gas phase and a liquid phase. Refrigerant flowing into the accumulator 93 is separated into the gas phase and the liquid phase, and the gas phase refrigerant that accumulates in the upper spaces is supplied to the compressor 91.
[0065] The open air fan 95 supplies the open air heat exchanger with 20 open air for heat exchange with the refrigerant flowing through the open heat exchanger 20.
[0066] Expansion valve 33 is a mechanism for depressurizing the refrigerant in the refrigerant circuit, and is an electrically operated valve whose valve opening is adjustable. In order to make adjustments to the refrigerant pressure and refrigerant flow rate, the expansion valve 33 is disposed between the open-air heat exchanger 20 and the refrigerant interconnecting pipeline 6 for the refrigerant, and has the function to expand the refrigerant, both in cooling mode and in heating mode.
[0067] The open air fan 95 is arranged by confronting the open air heat exchanger 20 in the blower chamber S1. The open-air fan 95 draws open-air air into the unit and, after the heat exchange between the open-air air and the refrigerant has taken place in the open-air heat exchanger 20, it discharges the air with heat exchanged to the outside. This open-air fan 95 is a fan in which it is possible to adjust the volume of air supplied to the open-air heat exchanger 20, and can be, for example, a propeller fan driven by a motor, such as a DC fan motor or something. (3) Operation of the Air Conditioning Device 1 (3-1) Cooling Mode
[0068] In cooling mode, the four-way switching valve 92 is in the state shown by the solid lines in figure 1, that is, a state in which the discharge side of compressor 91 is connected to the gas side of the exchanger indoor heat exchanger 20 via gaseous refrigerant piping 31, and the inlet side of the compressor 91 is connected to the gas side of the indoor heat exchanger 4 via accumulator 93 and the refrigerant interconnecting pipeline 7. The Expansion valve design 33 is such that valve opening adjustments are made to maintain a constant degree of overheating (degree of overheating control) of the refrigerant at the outlet of the indoor heat exchanger 4 (ie, the side gas from the indoor heat exchanger 4). With the refrigerant circuit in this state, when compressor 91, open-air fan 95 and closed-air fan 5 are running, low pressure gas refrigerant is compressed by compressor 91 to become high pressure gas refrigerant. This high pressure gaseous refrigerant is supplied to the open air heat exchanger 20 via the four-way switching valve 92. Subsequently, the high pressure gaseous refrigerant undergoes heat exchange in the open air heat exchanger 20 with air from open room provided by open-air fan 95, and is condensed to become high-pressure liquid refrigerant. High-pressure liquid refrigerant, now in a super-cooled state, is supplied to the expansion valve 33 by the open-air heat exchanger 20. Refrigerant having been depressurized close to the compressor inlet pressure 91 by the expansion valve 33 and in a low pressure two-phase gas-liquid state it is supplied to the indoor heat exchanger 4, and undergoes heat exchange with indoor air in the indoor heat exchanger 4, evaporating to become refrigerant low pressure gas.
[0069] This low pressure gaseous refrigerant is supplied to the air conditioning open-air unit 2 via refrigerant interconnecting pipeline 7, and is pulled back into compressor 91. In this cooling mode, the device air conditioning unit 1 guides the indoor heat exchanger 20 to act as a condenser for the compressed refrigerant in the compressor 91, and the indoor heat exchanger 4 to function as an evaporator for the condensed refrigerant in the heat exchanger of open space 20.
[0070] In the refrigerant circuit during cooling mode, while condition of overheating control by the expansion valve 33 is happening, compressor 91 is inverter controlled to a set temperature (such that the cooling load can be processed), and for this reason the refrigerant circulation rate may be a high circulation rate in some cases, and a low circulation rate in others. (3-2) Heating Mode
[0071] In heating mode, the four-way switching valve 92 is in the state shown by dashed lines in figure 1, that is, a state in which the discharge side of the compressor 91 is connected to the gas side of the exchanger indoor heat exchanger 4 via refrigerant interconnecting pipeline 7, and the inlet side of compressor 91 is connected to the gas side of the indoor heat exchanger 20 via gas refrigerant piping 31. Expansion valve design 33 it is such that valve opening 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 compressor 91, open-air fan 95 and closed-belt re-fan 5 are running, low-pressure gaseous refrigerant is pulled into compressor 91 and compressed by it to become high pressure gaseous refrigerant, and is supplied to the indoor air conditioning unit 3 via the four-way switching valve 92 and the refrigerant interconnecting pipeline 7.
[0072] The high-pressure gaseous refrigerant supplied to the indoor air conditioning unit 3 then undergoes heat exchange with indoor air in the indoor heat exchanger 4, and is condensed to become liquid refrigerant of high pressure, so while passing through the expansion valve 33 it is depressurized to a extent commensurate with the expansion valve valve opening 33. The refrigerant having passed through the expansion valve 33 flows into the open-air heat exchanger 20 The refrigerant in a low-pressure, two-phase gas-liquid state having drained into the open-air heat exchanger 20 undergoes heat exchange with open-air air supplied by the open-air fan 95, evaporates to become cool. -low pressure gas stream, and is again pulled into the compressor 91 via the four-way switching valve 92. In this heating mode, the conditioning device air ionization 1 guides the indoor heat exchanger 4 to function as a condenser for the compressed refrigerant in the compressor 91, and the indoor heat exchanger 20 to function as an evaporator for the condensed refrigerant in the heat exchanger. indoor 4.
[0073] In the refrigerant circuit during heating mode, while condition of super-cooling control by the expansion valve 33 is happening, compressor 91 is controlled by an inverter for a set temperature (such that the heating load can be processed), and for this reason the refrigerant circulation rate may be a high circulation rate in some cases and a low circulation rate in others. (4) Detailed Configuration of the Indoor Heat Exchanger 20 (4-1) Total Configuration of the Indoor Heat Exchanger 20
[0074] Next, the configuration of the open-air heat exchanger 20 will be described using figure 4 showing a simplified external view in perspective of the open-air heat exchanger 20, figure 5 showing a schematic rear view of the exchanger of indoor heat, and figure 6 which is a simplified rear view.
[0075] The open air heat exchanger 20 is provided with a heat exchange part 21 where heat exchange takes place between open air and the refrigerant, an outlet / inlet junction collection tube 22 arranged in one end of this heat exchange part 21, and a return junction collection tube 23 disposed at the other end of this heat exchange part 21. (4-2) Heat exchange part 21
[0076] Figure 7 is an enlarged fragmentary cross-sectional view of a cross-sectional structure of the heat exchange part 21 of the open-air heat exchanger 20, in a plane perpendicular to the flattening direction of the flat drilled tubes 21b thereof. . Figure 8 is a simplified perspective view of the heat transfer fins 21a attached to the open-air heat exchanger 20.
[0077] The heat exchange part 21 has an upper side heat exchange area X located on the upper side, and a lower side heat exchange area Y located below the upper side heat exchange area X. Among these, the top side heat exchange area X has a first top side heat exchange part X1, a second top side heat exchange part X2 and a third top side heat exchange part X3, arranged in that order from the top. The bottom heat exchange area Y has a first bottom heat exchange part Y1, a second bottom heat exchange part Y2 and a third bottom heat exchange part Y3, arranged in that order from the top.
[0078] This heat exchange part 21 consists of a multiplicity of the heat transfer fins 21a and a multiplicity of perforated flat tubes 21b. The heat transfer fins 21a and the flat perforated tubes 21b are both made of aluminum or aluminum alloy.
[0079] The heat transfer fins 21a are flat components, and a plurality of cutouts 21aa extending in a horizontal direction for insertion of flattened tubes is formed side by side in a vertical direction in the heat transfer fins 21a. The heat transfer fins 21a are fixed in order to have innumerable sections extending towards the side upstream of the air flow.
[0080] Perforated flat tubes 21b function as heat transfer tubes to transfer heat by shifting between the heat transfer fins 21a and the external air to the refrigerant flowing through the interior. Perforated flat 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. Perforated flat tubes 21b, which are slightly thicker in vertical extension than cutouts 21aa, are arranged spaced to the side in a plurality of rows with the heat transfer surfaces facing up and down, and are temporarily fixed to the fit into cutouts 21aa. With the perforated flat tubes 21b temporarily attached when being fitted to the cutouts 21aa of the heat transfer fins 21a in this mode, the heat transfer fins 21a and the flat perforated tubes 21b are welded with strong solder. Perforated flat tubes 21b are fitted at either end to the outlet / inlet junction collection tube 22 and the return junction collection tube 23, respectively, and brazed. And in so doing, an inner outlet / upper inlet space 22a and an inner outlet / lower inlet space 22b in the outlet / inlet junction collection tube 22 discussed below, and / or the first to the sixth inner spaces 23a, 23b, 23c, 23d, 23e, 23f of the return junction collection tube 23, and the internal flow channels 21ba of the flat perforated tubes 21b, discussed below, are connected.
[0081] As shown in figure 7, the heat transfer fins 21a extend upwards vertically, and for this reason any dew condensation that occurs on the heat transfer fins 21a and / or on the perforated flat tubes 21b will drip down along the heat transfer fins 21a and flow outwards through a path formed in the bottom panel 12. (4-3) Exit / Inlet Junction Collection Tube 22
[0082] The outlet / inlet junction collection tube 22 is a cylindrical element made of aluminum or aluminum alloy, arranged at one end of the heat exchange part 21, and extending in the vertical direction.
[0083] The outlet / inlet junction collection tube 22 includes the upper and lower inlet / outlet spaces 22a, 22b which are divided in the vertical direction by a first deflector 22c. The gaseous refrigerant piping 31 is connected to the inner outlet / upper inlet 22a at an upper part, and the liquid refrigerant pipeline 32 is connected to the inner outlet / lower inlet 22b at a lower part.
[0084] Both the inner outlet / upper inlet 22a at the top of the outlet / inlet junction collection tube 22 and the inner outlet / lower inlet 22b at the bottom are connected to the ends of the plurality of flat tubes drilled 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 arranged in a manner such as to correspond to the internal upper outlet / inlet space 22a at the top of the outlet / inlet junction collection tube 22. The first lower side heat exchange part Y1, the second heat exchange part bottom side Y2 and the bottom side heat exchange part Y3 of the bottom side heat exchange area Y are arranged in a manner such as to correspond to the bottom outlet / inlet 22b at the bottom of the outlet / inlet junction collection tube 22. (4-4) Return Junction Collection tube 23
[0085] The return junction collection tube 23 is a cylindrical element made of aluminum or aluminum alloy, disposed on the other end of the heat exchange part 21, and extending in the vertical direction.
[0086] The interior of the return junction collection tube 23 is divided in the vertical direction by a second deflector 23g, a third deflector 23h, a third flow regulation plate 43, a fourth deflector 23i and by a fifth deflector 23j, forming the first to sixth internal spaces 23a, 23b, 23c, 23d, 23e, 23f.
[0087] Of these, the first three internal spaces 23a, 23b, 23c of the return junction collection tube 23 are connected to the other ends of a plurality of flat perforated tubes 21b which are connected at their ends to the internal outlet space / upper inlet 22a at the top of the outlet / inlet junction collection tube 22. Specifically, the first upper side heat exchange part X1 of the upper side heat exchange area X is arranged in a manner such as to correspond to the first inner space 23a of the return junction collection tube 23, the second upper side heat exchange portion X2 of the upper side heat exchange area X in a manner such as to correspond to the second inner space 23b of the pipe of return junction collection 23, and the third upper side heat exchange part X3 of the upper side heat exchange area X is arranged in a manner such as to correspond to the third inner space 23c of tube d and return junction collection 23, respectively.
[0088] The multiplicity of flat perforated tubes 21b connected at one end to the inner outlet / bottom inlet 22b at the bottom of the outlet / inlet junction collection tube 22 connects at its other ends to the last three internal spaces 23d, 23e, 23f of the return junction collection tube 23. Specifically, the first lower side heat exchange part Y1 of the lower side heat exchange area Y is arranged in a manner such as to correspond to the fourth internal space 23d of the return junction collection tube 23, the second lower side heat exchange part Y2 of the lower side heat exchange area Y in a manner such as to correspond to the fifth internal space 23e of the return pipe return junction collection 23, and the lower side heat exchange part Y3 of the lower side heat exchange area Y is arranged in a manner such as to correspond to the sixth inner space 23f of the return junction collection tube r etorno 23, respectively.
[0089] The first inner space 23a of the highest row and the inner space 23f of the lowest row of the return junction collection tube 23 are connected by an interconnecting pipeline 24.
[0090] The second inner space 23b of the second row from the top and the fifth inner space 23e of the second row from the bottom are connected by an interconnecting pipeline 25.
[0091] The third inner space 23c of the third row from the top and the fourth inner space 23d of the third row from the bottom are divided to the side by the third flow regulation plate 43, but have sections that communicate vertically through a third inlet flow port 43x arranged on the third flow regulation plate 43.
[0092] The design is such that the number of flat perforated tubes 21b into which refrigerant flowing from the interconnecting pipeline 24 branches into the first internal space 23a of the return junction collection tube 23 is greater than the number of tubes perforated flatfish 21b into which the refrigerant flowing from the liquid refrigerant pipeline 32 branches into the inner outlet / lower inlet 22b of the outlet / inlet junction collection tube 22 as the coolant advances to the sixth inner space 23f (the same holds for the ratio of the numbers of flat perforated tubes 21b of the second inner space 23b and the fifth inner space 23e, and / or the ratio of the numbers of perforated flat tubes 21b of the third inner space 23c and the fourth internal space 23d). Although different arrangements can be employed in order to optimize refrigerant distribution, in the present embodiment, the number of flat perforated tubes 21b connected to the first internal space 23a, the number of flat perforated tubes 21b connected to the second internal space 23b and the number of tubes perforated flats 21b connected to the third internal space 23c are substantially the same. Likewise, although different arrangements can be employed in order to optimize refrigerant distribution, in the present embodiment, the number of flat perforated tubes 21b connected to the fourth inner space 23d, the number of flat perforated tubes 21b connected to the fifth inner space 23e and the number the perforated flat tubes 21b connected to the sixth inner space 23f are substantially the same. (4-5) Return Junction Collection Tube Loop Structure 23
[0093] In the return junction collection tube 23, the first three upper inner spaces 23a, 23b, 23c are provided with a loop structure and a flow regulation structure.
[0094] The loop structure and a flow regulation structure of the first to the third internal spaces 23a, 23b, 23c, respectively, are described below. (4-5-1) First Inner Space 23a
[0095] As shown in figure 6, in a simplified perspective view in figure 9, in a simplified cross-sectional view in figure 10 and in a simplified top view in figure 11, respectively, the first highest inner space 23a in the tube return junction collection plate 23 is provided with a first flow regulation plate 41 and a first split plate 51.
[0096] The first flow regulation plate 41 is a substantially disk-shaped plate component that divides the first internal space 23a into a first flow regulation space 41a below, and a first output flow space 51a and the loop structure 51b above. The first flow regulation space 41a is a space located above the second deflector 23g dividing the first internal space 23a and the second internal space 23b, and below the first flow regulation plate 41 arranged in a lower location than the tube perforated flat 21b immediately above the second baffle 23g. The interconnecting pipeline 24 extending out of the sixth (lowest) space 23f of the return junction collection tube 23 communicates with this first flow regulation space 41a.
[0097] The first splitting plate 51 is a generally rectangular plate component that divides a space above the first flow regulation space 41a in the first internal space 23a in a first outlet flow space 51a and a first loop space 51b. Although there are no particular limitations, the first partition plate 51 in the present embodiment is arranged in the center of the first internal space 23a to divide the space above the first flow regulation space 41a in such a way that the first outflow space 51a and the first loop space 51b are equal in amplitude in top view. The first splitting plate 51 is fixed in such a way that its lateral surfaces contact an internal peripheral surface of the return junction collection tube 23. The first outlet flow space 51a is a space on the side on which the flat tubes perforated 21b connect at their ends to the first internal space 23a. The first loop space 51b is a space located on the side of the first partition plate 51 opposite that of the first outlet flow space 51a in the first internal space 23a.
[0098] In the upper part of the first internal space 23a, a first upper communication passage 51x is provided, constituted by a vertical gap between the inside of the upper end of the return junction collection tube 23 and an upper end section of the first split plate 51.
[0099] At the bottom of the first internal space 23a, a first lower communication passage 51y is provided, constituted by a vertical gap between the upper surface of the first flow regulation plate 41 and a lower end section of the first partition plate 51. In the present embodiment, the first lower communication passage 51y extends in a horizontal direction from the side of the first loop space 51b to the side of the first outflow space 51a. An outlet on the side of the first outlet flow space 51a of this first lower communication passage 51y is located lower than the location of the lower perforated flat tubes 21b connected to the first outlet flow space 51a.
[00100] As shown in figure 9, the first flow regulation plate 41 is provided with two first 41x inlet flow ports; these are openings which are arranged in the first outlet flow space 51a constituting the space on the side in which the perforated flat tubes 21b extend in the first internal space 23a, and which provide communication in the vertical direction. The two inlet flow ports 41x are disposed distant to the upstream side and the downstream side in the air flow direction, i.e., the air flow direction in relation to the open air heat exchanger 20. The first inlet flow ports 41x are formed to be larger in width closer to the side of the first split plate 51 in the direction of airflow, and narrower in width closer to the side of the perforated flat tube 21b in the air flow direction. The first 41x inlet flow ports have shapes that conform to the internal peripheral surface of the return junction collection tube 23.
[00101] The first internal space 23a has a flow regulation structure in which the refrigerant passage area (the area of a horizontal plane) in the first 41x inlet flow ports is sufficiently smaller than the refrigerant passage area of the first flow regulation space 41a (the horizontal plane area of the first flow regulation space 41a). By adopting this flow regulation structure, the refrigerant flow going from the first flow regulation space 41a to the side of the first outlet flow space 51a can be sufficiently throttled, and the refrigerant flow speed upwards in the vertical direction. can be increased.
[00102] When dividing 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 on the side of the first outlet flow space 51a (the area of passage of the rising refrigerant flow within the first outlet flow space 51a) can be made smaller than the total horizontal area of the first outlet flow space 51a and the first loop space 51b. And in so doing, it is easy to keep the refrigerant rising speed flowing into the first outlet flow space 51a via the first 41x inlet ports, making it easy for the refrigerant to reach the top section of the first outflow space 51a, even at a low circulation rate.
[00103] As shown in the simplified top view of figure 11, the perforated flat tubes 21b are embedded in the first outlet flow space 51a, in a manner such as to occupy half or more of the horizontal area in locations towards the height in the first outlet flow space 51a where flat perforated tubes 21b are absent. Perforated flat tubes 21b and the first inlet flow ports 41x of the first flow regulation plate 41 are arranged in locations overlapping partially in top view.
[00104] However, this arrangement is such that when "the horizontal area of sections of perforated flat tubes 21b extending into the first outlet flow space 51a" is subtracted from the "horizontal area in locations towards the height within of the first outlet flow space 51a where no flat perforated tubes 21b are not present ", the remaining area (the area of sections where the refrigerant passes near the flat perforated tubes 21b and ascends in the first outflow space 51a) is greater than the refrigerant passage area of the first 51y lower communication passage. And in so doing, it is possible that refrigerant flowing into the first outflow space 51a via the first inlet flow ports 41x does not pass to the side of the first loop space 51b through the first lower communication passage 51y, which is more narrow and difficult to cross, and can instead be guided in order to ascend through sections excluding the flat perforated tubes 21b in the first outlet flow space 51a, which are wider and easier to cross.
[00105] The first internal space 23a has a loop structure that includes the first inlet flow ports 41x, the first partition plate 51, the first upper communication passage 51x and the first lower communication passage 51y. For this reason, as shown by the arrows in figure 10, refrigerant reaching the top in the first outlet flow space 51a without flowing into the flat perforated tubes 21b is guided to the first loop space 51b via the first upper communication passage. 51x above the first divider plate 51, it descends by gravity into the first loop space 51b, and returns to the bottom of the first outflow space 51a via the first lower communication passage 51y below the first divider plate 51. And in so doing, it is possible for the refrigerant to reach the top of the first outlet flow space 51a to be looped within the first internal space 23a. (4-5-2) Second Internal Space 23b
[00106] The second inner space 23b, which is the second from the top of the return junction collection tube 23, is similar in configuration to the first higher inner space 23a, and as shown in figure 6, and in simplified cross-sectional view in figure 12, respectively, it is provided with a second flow regulation plate 42 and a second partition plate 52.
[00107] The second flow regulation plate 42 is a generally disk-shaped plate component that divides the second internal space 23b into a second flow regulation space 42a below, and a second output flow space 52a and the second loop space 52b above. The second flow regulation space 42a is a space located above the third deflector 23h dividing the second internal space 23b and the third internal space 23c, and below the second flow regulation plate 42 arranged in a lower location than the tube perforated flat 21b immediately above the third baffle 23h. The interconnecting pipeline 25 extending out of the fifth space 23e, the second from the bottom in the return junction collection tube 23, communicates with this second flow regulation space 42a.
[00108] The second dividing plate 52 is a generally rectangular plate component that divides a space above the second flow regulation plate 42a in the second internal space 23b in a second outlet flow space 52a and a second space 52b loop. The second outlet flow space 52a is a space located on the side to which the perforated flat tubes 21b connect at their ends, in the second internal space 23b. The second loop space 52b is a space located on the side of the second split plate 52 opposite the second outlet flow space 52a in the second inner space 23b.
[00109] In the upper part of the second internal space 23b there is arranged a second upper communication passage 52x constituted by a vertical gap between the lower surface of the second baffle 23g and an upper end section of the second partition plate 52.
[00110] At the bottom of the first internal space 23b, a second lower communication passage 52y is arranged, constituted by a vertical gap between the upper surface of the second flow regulation plate 42 and a lower end section of the second partition plate 52. In the present embodiment, the second lower communication passage 52y extends in a horizontal direction from the side of the second loop space 52b to the side of the second outflow space 52a. An outlet on the side of the second outlet flow space 52a of this second lower communication passage 52y is located lower than the location of the lower of the perforated flat tubes 21b connected to the second outlet flow space 52a.
[00111] Like the first flow regulation plate 41, the second flow regulation plate 42 is provided with two second flow ports 42x, which are communication openings vertically arranged on the side for which the flat tubes perforated 21b extend into the second internal space 23b.
[00112] Like the first inner space 23a, the second inner space 23b has a flow regulation structure in which the coolant passage area (the area of a horizontal plane) in the second inlet flow ports 42x is sufficiently smaller than the refrigerant passage area of the second flow regulation space 42a (the horizontal plane area of the second flow regulation space 42a).
[00113] Additionally, like the first inner space 23a, the second inner space 23b has a loop structure that includes the second inlet flow ports 42x, the second partition plate 52, the second upper communication passage 52x and the second 52y lower communication pass.
[00114] The details of the arrangement configuration are otherwise the same as in the first internal space 23a, and are consequently omitted here. (4-5-3) Third Inner Space 23c
[00115] The third internal space 23c, which is the third from the top of the return junction collection tube 23, is provided with a third flow regulation plate 43 and a third division plate 53, such as shown in figure 6, and in the simplified cross-sectional view in figure 13, respectively.
[00116] The third flow regulation plate 43 is a plate component in a generally disk-like manner that separates the third inner space 23c from a fourth inner space 23d (space located below) which is the third from the bottom bottom of the return junction collection tube 23, and a third outlet flow space 53a and a third loop space 53b which are located above.
[00117] The third splitting plate 53 is a generally rectangular plate component that divides a space above the fourth inner space 23d into the third inner space 23c into a third outflow space 53a and a third loop space 53b . The third outlet flow space 53a is a space located on the side in which the perforated flat tubes 21b connect at their ends to the third inner space 23c. The third loop space 53b is a space located on the side of the third partition plate 53 opposite that of the third outlet flow space 53a in the third inner space 23c.
[00118] In the upper part of the third internal space 23c there is arranged a third upper communication passage 53x constituted by a vertical gap between the lower surface of the third baffle plate 23h and an upper end section of the third partition plate 53.
[00119] At the bottom of the third internal space 23c, a third lower communication passage 53y is provided, constituted by a vertical gap between the upper surface of the third flow regulation plate 43 and a lower end section of the third dividing plate 53. In the present embodiment, the third lower communication passage 53y extends in a horizontal direction from the side of the third loop space 53b to the side of the third outflow space 53a. An outlet on the side of the third outlet flow space 53a of this third lower communication passage 53y is located lower than the location of the lower perforated flat tubes 21b connected to the third outlet flow space 53a.
[00120] Like the first flow regulation plate 41 and the second flow regulation plate 42, the third flow regulation plate 43 is provided with two third inlet flow ports 43x, which are openings arranged on the side for which the perforated flat tubes 21b extend in the third internal space 23c, and which provide communication in the vertical direction.
[00121] Like the first inner space 23a and the second inner space 23b, the third inner space 23c has a flow regulation structure in which the coolant passage area (the area of a horizontal plane) in the third flow ports inlet 43x is sufficiently smaller than the coolant passage area of the fourth inner space 23d (the horizontal plane area of the fourth inner space 23d).
[00122] Additionally, like the first inner space 23a and the second inner space 23b, the third inner space 23c has a loop structure that includes the third inlet flow ports 43x, the third partition plate 53, the third passage upper communication link 53x and the third lower communication link 53y.
[00123] The details of the arrangement configuration are otherwise the same as those of the first inner space 23a and the second inner space 23b, and are consequently omitted here. (5) Overview of Refrigerant Flow in the Open Air Heat Exchanger 20 During Heating Mode
[00124] The flow of refrigerant in the open-air heat exchanger 20 constituted as shown above is described below, mainly in terms of the flow during heating mode.
[00125] As shown by an arrow in figure 5, during heating mode, refrigerant in a two-phase gas-liquid state is supplied to the inner outlet / lower inlet 22b of the outlet / junction collection tube inlet 22 via liquid refrigerant piping 32. In the description of the present embodiment, the state of the refrigerant flowing into this internal outlet / lower inlet 22b is assumed to be a two-phase gas-liquid state; however, depending on the indoor temperature and / or the indoor temperature and / or the operational state, the inlet refrigerant may be in a substantially monophasic liquid state.
[00126] The refrigerant supplied to the inner outlet / lower inlet 22b at the bottom of the outlet / inlet junction collection tube 22 passes through the plurality of perforated flat tubes 21b at the bottom of the heat exchange part 21 connected to the inner outlet / lower inlet 22b, and is provided respectively for the last three inner spaces 23d, 23e, 23f at the bottom of the return junction collection tube 23. As the refrigerant supplied to the last three spaces internal 23d, 23e, 23f at the bottom of the return junction collection tube 23 passes through the flat perforated tubes 21b at the bottom of the heat exchange part 21, a part of the liquid phase component of the refrigerant in the gas state - two-phase liquid evaporates, thereby resulting in a state in which the gas phase component is increased.
[00127] The refrigerant provided for the sixth inner space 23f at the bottom of the return junction collection tube 23 passes through the interconnecting pipeline 24, and is provided for the first inner space 23a at the top of the junction collection tube 23 return 23. The refrigerant supplied to the first internal space 23a flows respectively into the plurality of flat 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 perforated tubes 21b further evaporates to a gas phase state, and is supplied to the inner outlet / inlet upper space 22a at the top of the outlet / inlet junction collection tube 22.
[00128] The refrigerant provided for the fifth inner space 23e at the bottom of the return junction collection tube 23 passes through the interconnecting pipeline 25 and is provided for the second inner space 23b at the top of the return junction collection tube 23. The refrigerant supplied to the second internal space 23b flows respectively into the plurality of flat 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 perforated flat tubes 21b further evaporates to a gaseous phase state, and is supplied to the inner outlet / upper inlet 22a at the top of the outlet / inlet junction collection tube 22.
[00129] The refrigerant provided for the fourth internal space 23d at the bottom of the return junction collection tube 23 passes upwards vertically through the third inlet flow ports 43x provided for the third flow regulation plate 43, and is provided for the inner space of the third inner space 23c at the top of the return junction collection tube 23. The refrigerant provided for the third inner space 23c flows respectively into the plurality of flat perforated tubes 21b connected to the third inner space 23c (the flow of refrigerant within the third internal space 23c will be discussed below). The refrigerant flowing through the plurality of flat perforated tubes 21b further evaporates to a gas phase state, and is supplied to the inner outlet / inlet upper space 22a at the top of the outlet / inlet junction collection tube 22.
[00130] The refrigerant that has drained from the first to the third internal spaces 23a, 23b, 23c in the upper part of the return junction collection tube 23 through the perforated flat tubes 21b and has been supplied to the internal space of exit / upper entrance 22a at the top of the outlet / inlet junction collection tube 22 converges into the inner outlet / top inlet space 22a, and flows out through the gas refrigerant piping 31.
[00131] In cooling mode, the refrigerant flow is the inverse of the flow indicated by the arrows in figure 5. (6) Refrigerant flow in the open-air heat exchanger 20 in a case of a low circulation rate during cooling mode Heating
[00132] The flow of refrigerant in the open-air heat exchanger 20 in a case of a low circulation rate during heating mode will be described below, considering the example of the first internal space 23a of the return junction collection tube 23 .
[00133] The refrigerant flowing into the inner outlet / lower inlet 22b of the outlet / inlet junction collection tube 22 is depressurized at the expansion valve 33, and thus passes into a two-gas-liquid state. phases. A portion of the liquid phase component in the refrigerant in the two-phase gas-liquid state that has flowed into the first inner space 23a of the return junction collection tube 23 evaporates in the passage path through the flat perforated tubes 21b of the inner space outlet / inlet bottom 22b of the outlet / inlet junction collection tube 22 to the sixth inner space 23f of the return junction collection tube 23. For this reason, the refrigerant passing through the interconnecting pipeline 24 and flowing to the first internal space 23a of the return junction collection tube 23 is a mixture of a gas phase component and a liquid phase component that differ in specific gravity.
[00134] In the case of a low circulation rate, the amount of refrigerant flowing per unit of time to the first flow regulation space 41a via interconnecting pipeline 24 is small, and the flow rate of the refrigerant flowing through the pipeline outlet interconnection number 24 is relatively low. For this reason, as long as this flow rate remains unchanged, the liquid phase component of high specific gravity in the refrigerant rises with difficulty, and only with difficulty can it reach the tubes at the top between the plurality of flat perforated tubes 21b connected to the first internal space 23a, which in some cases may result in irregular rates of passage through the plurality of flat perforated tubes 21b, depending on their locations towards the height, and present an eccentric flow risk. Therefore, as shown in the descriptive diagram of figure 14 which represents a reference example during a low circulation rate, when the gas phase component of low specific gravity in the refrigerant flows mainly to the end side of the flat perforated tubes 21b that are located relatively at the top, the degree of overheating of the refrigerant flowing out the other end of these flat perforated tubes 21b becomes very high, phase change no longer occurs during passage through the flat perforated tubes 21b, and exchange capacity heat cannot be achieved sufficiently. However, when the liquid phase component of high specific gravity in the refrigerant flows mainly to the end side of the perforated flat tubes 21b which are situated relatively at the bottom, the refrigerant flowing out of the other end side of these perforated flat tubes 21b it does not easily overheat, and in some instances it will reach the other end of the perforated flat tubes 21b without evaporating, so that in the end the heat exchange capacity cannot be sufficiently achieved.
[00135] In contrast, with the open-air heat exchanger 20 of the present embodiment, the refrigerant supplied to the first flow regulation space 41a experiences an increase in flow velocity in the vertical refrigerant flow upwards as it passes through the first inlet flow ports 41x of the first flow regulation plate 41, which have a throttling function. In addition, because the space above the first flow regulation plate 41 in the first internal space 23a is provided with the first partition plate 51, the refrigerant passage area of the space on the side where the first inlet flow ports 41x are arranged (the first outflow space 51a) is constituted in order to be narrower when compared to that where the first split plate 51 is absent, and for this reason the upward flow speed does not readily decrease. For this reason, even in the case of a low circulation rate, the liquid phase component of high specific gravity in the refrigerant can be easily guided to the upper part within the first outlet flow space 51a.
[00136] As the refrigerant flowing into the first outflow space 51a via the first inlet flow ports 41x rises into the first outflow space 51a, the flow is divided between the flat perforated tubes 21b, but a small portion of the refrigerant is guided to the upper end of the first outlet flow space 51a without flowing into the flat perforated tubes 21b.
[00137] The refrigerant having reached the upper end of the first outlet flow space 51a in this mode is guided to the first loop space 51b via the first upper communication passage 51x, and descends into the first loop space 51b by means of gravity. The refrigerant having descended through the first loop space 51b flows in a horizontal direction while passing through the first lower communication passage 51y which extends in the horizontal direction, and again returns to the bottom of the first outlet flow space 51a.
[00138] The refrigerant that has returned to the first outlet flow space 51a via the lower communication passage 51y is dragged by the upward flow of the refrigerant through the first 41x inlet ports and again rises into the first flow space outlet 51a, and according to circumstances it can flow into the perforated flat tubes 21b after being recirculated through the first internal space 23a.
[00139] And so doing, in the open space heat exchanger 20 of the present modality, even in periods of a low circulation rate, it is possible the state of the refrigerant flowing into the plurality of flat perforated tubes 21b arranged in sections of different heights be taken to approximate the state represented in the descriptive diagram of figure 15, which shows a reference example during an average circulation rate, and made as uniform as possible.
[00140] The second inner space 23b and the third inner space 23c of the return junction collection tube 23 function in the same way as the first inner space 23a, and for this reason description is omitted. (7) Flow of Refrigerant in the Open Air Heat Exchanger 20 in One Case with a High Circulation Rate During Heating Mode
[00141] The flow of refrigerant in the open-air heat exchanger 20 in a case of a high circulation rate during heating mode will be described below, considering the example of the first internal space 23a of the return junction collection tube 23 .
[00142] Here, just as in the case of a low circulation rate, the state of the refrigerant flowing into the first internal space 23a of the return junction collection tube 23 is a mixture of a gas phase component and a gas component. liquid phase differing in specific gravity.
[00143] In the case of a high circulation rate, the amount of refrigerant flowing per unit of time to the first flow regulation space 41a via interconnecting pipeline 24 is large, and the flow rate of the refrigerant flowing through the pipeline outlet interconnection number 24 is relatively high. In addition, the flow rate is further increased by adopting the throttling function of the first 41x inlet flow ports as the low flow countermeasure discussed earlier. In addition, because of the narrow refrigerant passage area of the first outlet flow space 51a, that is, the refrigerant passage area that is constricted by the first partition plate 51 as the low flow counter measure discussed earlier, almost there is no decrease in the refrigerant rising speed. For this reason, in the case of a high circulation rate, the liquid phase component of high specific gravity of the refrigerant forcibly passing through the first inlet flow ports 41x tends to pass through the first outlet flow space 51a without flow into the flat perforated tubes 21b, and tend to accumulate at the top. In such cases, the liquid phase component of high specific gravity tends to accumulate at the top while the gas phase component of low specific gravity tends to accumulate at the bottom, and at the end eccentric flow appears as shown in the descriptive diagram of the figure 16, showing a reference example during a high circulation rate, however the distribution differs from this in periods of a low circulation rate.
[00144] In contrast to this, with the open-air heat exchanger 20 of the present embodiment, because of the adoption of the loop structure in the first internal space 23a, the refrigerant that reaches the upper end of the first outlet flow space 51a is guided to the first loop space 51b via the first upper communication path 51x, and after descending through the first loop space 51b is returned to the first outgoing flow space 51a via the first lower communication path 51y, and thus can be guided into the flat perforated tubes 21b located at the bottom of the first outlet flow space 51a.
[00145] The refrigerant returning to the first outlet flow space 51a via the first lower communication passage 51y is dragged by the ascending refrigerant flow past the first inlet flow ports 41x and again rises into the first outlet flow space 51a, and according to circumstances it can flow into the flat perforated tubes 21b after being recirculated through the first internal space 23a.
[00146] And so doing, in the open space heat exchanger 20 of the present modality, even in periods of a high circulation rate, it is possible for the state of the refrigerant to flow to the plurality of flat perforated tubes 21b arranged in sections of different heights - rentes be taken to approximate the state represented in the descriptive diagram of figure 15, which shows a reference example during an average circulation rate, and be made as uniform as possible.
[00147] The second inner space 23b and the third inner space 23c of the return junction collection tube 23 function in the same way as the first inner space 23a, and for this reason description is omitted. (8) Features of the Air Conditioning Device 1 Open Air Heat Exchanger 20 (8-1)
[00148] With the open space heat exchanger 20 of the present modality, even in the case of a low circulation rate, the refrigerant rise speed in the first internal space 23a of the return junction collection tube 23 is maintained by the first 41x inlet ports and the configuration of the first outlet stream 51a constricted by the first split plate 51, so that the refrigerant can more easily reach the top of the first outlet stream 51a (the design of the second internal space 23b and the third internal space 23c is the same).
[00149] Additionally, with the open space heat exchanger 20 of the present modality, even in cases of a high circulation rate, the refrigerant circulates in a loop within the first internal space 23a because of the loop structure adopted in the first internal space 23a of the return junction collection tube 23, whereby the refrigerant can be guided into the flat perforated tubes 21b.
[00150] In the previously indicated mode, with the open space heat exchanger 20 of the present modality, both in cases of low circulation rate and in cases of high circulation rate, eccentric flow of refrigerant for the plurality of flat tubes drilled 21b arranged in the vertical direction can be kept to a minimum. (8-2)
[00151] In the open space heat exchanger 20 of the present modality, a loop structure and a flow regulation structure are adopted in the first to third inner spaces 23a, 23b, 23c of the return junction collection tube 23, but not in the upper and lower inner outlet / inlet spaces 22a, 22b of the outlet / inlet junction collection tube 22, nor in the last inner spaces 23d, 23e, 23f of the return junction collection tube 23. Specifically, the structure loop and flow regulation structure are adopted in the first to third inner spaces 23a, 23b, 23c of the return junction collection tube 23, where the refrigerant flowing through them in heating mode contains large amounts of phase components gas and liquid phase mixed, resulting in a marked tendency to emerge eccentric flow between the flat drilled tubes 21b at different heights.
[00152] Therefore, it is possible the effect of minimizing eccentric flow to be achieved sufficiently. (8-3)
[00153] The refrigerant that has passed through the first 41x inlet flow ports of the open-air heat exchanger 20 of the present modality and drained directly to the first outlet flow space 51a is at maximum ascent speed, and in some instances it tends not to enter the lower tubes between the plurality of flat perforated tubes 21b connected to the first outlet flow space 51a.
[00154] In contrast, with the open space heat exchanger 20 of the present embodiment, the outlet on the side of the first outlet flow space 51a of the first lower communication passage 51y is arranged such that the refrigerant descending through the first loop space 51b in the first internal space 23a of the return junction collection tube 23 can be guided into the flat perforated tubes 21b which are connected to the bottom of the first outlet flow space 51a.
[00155] For this reason, the flat perforated tubes 21b that are located at the bottom, through which the high-speed refrigerant flow into the first outlet flow space 51a via the first inlet flow ports 41x tend not to pass, it can be easily provided with the refrigerant that has been returned to the first outlet flow space 51a via the first lower communication passage 51y.
[00156] The resource indicated above is the same for the second internal spaces 23b, 23c also. (9) Additional Modalities
[00157] The preceding embodiment has been described as an example of the embodiment of the present invention, and is not intended to limit in any way the invention of the present application, which is not limited to the embodiment described above. The scope of the invention of the present application as a matter of course includes appropriate modifications that do not differ from the spirit of the same. (9-1) Additional Mode A
[00158] In the embodiment described above, an example of a case has been described in which the first lower communication passage 51y extends in the horizontal direction from the side of the first loop space 51b to the side of the first outflow space 51a (the the same applies to the second lower communication passage 52y and the third lower communication passage 53y equally).
[00159] However, the present invention is not limited to this arrangement; another acceptable configuration would be one in which, for example, the first lower communication passage 51y, instead of extending in the horizontal direction as in the modality described above, was tilted in order to be located more towards the bottom going from side of the first loop space 51b to the side of the first outlet flow space 51a, or that was inclined in order to be located additionally in the direction of the upper part going from the side of the first loop space 51b to the side of the first loop space outlet flow 51a. As the extent of this inclination, an inclination of 60 degrees or less with respect to the horizontal direction would be acceptable, as would be one of 30 degrees or less; and an inclination of -60 degrees or more with respect to the horizontal direction would be acceptable, as would be -30 degrees or greater, for example. In particular, from the point of view of not preventing upward flow of the refrigerant in the first outlet flow space 51a, the extent of the slope is preferably 0 to 60 degrees, and more preferably 0 to 30 degrees, with respect to horizontal direction.
[00160] With this configuration it is also possible for the refrigerant circulated through the first internal space 23a to be guided again into the flat perforated tubes 21b.
[00161] The feature indicated above can be implemented analogously in the second lower communication passage 52y and in the third lower communication passage 53y equally. (9-2) Additional Mode B
[00162] In the mode described above, an example of a case was described in which the first flow regulation plate 41, a plate-shaped element, is provided with the first 41x inlet flow doors that open in the thickness direction ( as do the second inlet flow ports 42x and the third inlet flow ports 43x).
[00163] However, the present invention is not limited to this arrangement, and, for example, a cylindrical inlet flow passage extending in the vertical direction can be provided in place of inlet flow ports formed through openings in a plate-shaped element. In this case, it will be possible to further increase the speed of the refrigerant by flowing out vertically upward as the refrigerant passes through the cylindrical inlet flow passage.
[00164] The feature indicated above can be implemented analogously on the second 42x inlet ports and the third 43x inlet ports equally. (9-3) Additional Mode C
[00165] In the modality described above, an example of a case was described in which the first 41x inlet flow ports are arranged in locations partially overlapping the flat perforated tubes 21b in top view (as are the second 42x inlet flow ports) and the third 43x inlet flow ports).
[00166] However, the present invention is not limited to this arrangement, and the locations of the first inlet flow ports 41x in top view are arbitrary, provided that the locations are on the side of the first outflow space 51a, for example .
[00167] The feature indicated above can be implemented analogously on the second 42x inlet ports and the third 43x inlet ports equally. (9-4) Additional Mode D
[00168] In the embodiment described above, an example of a case has been described in which the output of the first lower communication passage 51y on the side of the first output flow space 51a is located below the location of the lowest of the plurality of perforated flat tubes 21b connected to the first output flow space 51a (such as the outputs of the second lower communication passage 52y and the third lower communication passage 53y).
[00169] However, the present invention is not limited to this arrangement; it would be acceptable for the outlet of the first lower communication passage 51y on the side of the first outlet flow space 51a to be located close to the location of the lowest of the plurality of perforated flat tubes 21b connected to the first outlet flow space 51a such as, for example, at the same height as the lower flat perforated tube 21b.
[00170] The feature indicated above can be implemented analogously in the second lower communication passage 52y and in the third lower communication passage 53y equally. (9-5) Additional Mode E
[00171] In the modality described above and in additional modalities examples of cases have been described 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 inner space 23c are similar in shape.
[00172] However, the present invention is not limited to this arrangement; it would be acceptable for the shapes to differ from each other. (9-6) Additional Mode F
[00173] In the mode described above, an example has been described in which the return junction collection tube 23 has the first lower communication passage 51y consisting of the lower end section of the first split plate 51 and the upper surface section of the first flow regulation plate 41 (the second lower communication passage 52y and the third lower communication passage 53y are similarly formed).
[00174] However, the present invention is not limited to this arrangement; it would be acceptable to adopt, for example, a return junction collection tube 123 similar to the one shown in figure 17, in place of the return junction collection tube 23 of the previously described modality.
[00175] The return junction collection tube 123 is provided with a first lower communication passage 151y piercing the bottom of a first split plate 151 in the thickness direction in order to connect the first outlet flow space 51a and the first loop space 51b. The entire lower end section of the first partition plate 151 is supported by contact with the upper surface of the first flow regulation plate 41.
[00176] In this case, there is no need to adjust the height position of the first split plate 51 in order to adjust the refrigerant passage area of the first lower communication passage 51y as in the mode described above, and the first passage of bottom communication 151y of the first split plate 151 can be designed in advance to have the desired refrigerant passage area, so manufacturing can be simplified. (9-7) Additional Mode G
[00177] It would be acceptable to adopt, for example, a return junction collection tube 223 similar to the one shown in figure 18, in place of the return junction collection tube 23 of the modality described above.
[00178] The return junction collection tube 223 is constituted in such a way that a part of a lower end section of a first splitting plate 251 is cut out as a recess. For this reason, with the first splitting plate 251 positioned on the upper surface of the first flow regulation plate 41, it is possible that a first lower communication passage 251y is constituted by the upper surface (flat surface) of the first flow regulation plate flow 41 and by cutting out the lower end section of the first splitting plate 251.
[00179] In this case, there is no need to adjust the height position of the first split plate 51 in order to adjust the refrigerant passage area of the first lower communication passage 51y as in the mode described above, and the size of the cutout of the lower end section of the second split plate 251 can be designed in advance to have the desired refrigerant passage area, so manufacturing can be simplified. In addition, it is possible for the second splitting plate 251 to be supported by the non-recessed sections of the lower end section thereof, arranged in order to contact the upper surface of the first flow regulation plate 41. (9-8) Additional Mode H
[00180] In the embodiment described above, an example of a case has been described in which flat plate components such as the heat transfer fins 21a shown in figures 7 and 8 are employed as heat transfer fins.
[00181] 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 used primarily in automotive heat exchangers, would also be possible . LIST OF REFERENCE SYMBOLS 1 Air conditioning device 2 Air conditioning outdoor unit 3 Air conditioning indoor unit 10 Unit wrap 20 Open air heat exchanger (heat exchanger) 21 Part exchange heat 21a Heat transfer fin (fin) 21b Perforated flat tube (flat tube) 22 Outlet / inlet junction collection tube (confronting junction collection tube) 23 Return junction collection tube (junction collection tube 22a Internal outlet / upper inlet space 22b Internal outlet / lower inlet space 23a, 23b, 23c, 23d, 23e, 23f First to sixth internal spaces (internal spaces) 31 Gas refrigerant piping 32 Liquid refrigerant piping 33 Valve expansion port 41 First flow regulation plate (flow regulation component) 41a First flow regulation space (flow regulation space) 41x First entrance door (entrance door) 42 Se second flow regulation plate (flow regulation component) 42a Second flow regulation space (flow regulation space) 42x Second inlet (entrance door) 43 Third flow regulation plate (regulation component) flow connection) 43a Third flow regulation space (flow regulation space) 43x Third entrance door (entrance door) 51 First partition plate (division component) 51a First exit flow space (first space) 51b First loop space (second space) 51x First upper communication passage (upper communication passage) 51y First lower communication passage (lower communication passage) 52 Second division plate (division component) 52a Second output flow space (first space) 52b Second loop space (second space) 52x Second overpass (overpass) 52y Second overpass (overpass) 53 lower division plate (split component) 53a third outflow space (first space) 53b third loop space (second space) 53x third upper communication path (upper communication path) 53y third communication path bottom (bottom link) 91 Compressor 123 Return junction collection tube (bottom collection tube) 151 First split plate (split component) 151y First bottom link (bottom link) 223 return junction collection (junction collection tube) 251 First split plate (split component) 251y First lower communication path (lower communication path) X Top side heat exchange area X1, X2, X3 Parts Top side heat exchange Y Bottom heat exchange area Y1, Y2, Y3 Bottom heat exchange parts REFERENCE LIST PATENT LITERATURE Literature d and Patent 1 Japanese Open Patent Application No. H02- 219966.

权利要求:
Claims (6)
[0001]
1. Heat exchanger (20), comprising: a plurality of flat tubes (21b) arranged together; a junction collection tube (23) to which ends of the flat tubes (21b) are connected, and which extends in a vertical direction; and a plurality of fins (21a) joined to the flat tubes (21b), wherein the junction collection tube (23, 123, 223) has a loop structure including dividing components (51, 52, 53, 151, 251 ) that divide internal spaces (23a, 23b, 23c) into first spaces (51a, 52a, 53a), which are spaces on the side where the flat tubes (21b) are connected, and second spaces (51b, 52b, 53b), which are spaces on the opposite side to the side where the flat tubes (21b) are connected to the first space, inlet flow ports (41x, 42x, 43x), which are located in the lower parts of the first spaces (51a, 52a, 53a) and that, in the case of functioning as a refrigerant evaporator, stimulate refrigerant inlet flow in order to give rise to an upward flow within the first spaces (51a, 52a, 53a), upper communication passages (51x, 52x , 53x) located in the upper parts of the first spaces (51a, 52a, 53a) and the second spaces (51b, 52b, 53b), and providing communication between the upper parts of the first spaces (51a, 52a, 53a) and the second spaces (51b, 52b, 53b), thereby guiding the refrigerant that has risen within the first spaces (51a, 52a, 53a) to the second spaces (51b, 52b, 53b), and lower communication passages (51y, 52y, 53y, 151y, 215y) located in the lower parts of the first spaces (51a, 52a, 53a) and the second spaces (51b, 52b, 53b), providing communication between the lower parts of the first spaces (51a, 52a, 53a) and the second spaces (51b, 52b, 53b), and guiding the refrigerant in a direction other than the vertical direction of the second spaces (51b, 52b , 53b) for spaces above the inlet flow ports (41x, 42x, 43x) in the first spaces (51a, 52a, 53a), thereby guiding the refrigerant from the first spaces (51a, 52a, 53a) to the second spaces ( 51b, 52b, 53b), and returning the refrigerant having descended through the second spaces (51b, 52b, 53b) from the second spaces s (51b, 52b, 53b) for the first spaces (51a, 52a, 53a), characterized by the fact that: flow regulation spaces (41a, 42a, 43a) are formed in the lower parts of the first spaces (51a, 52a , 53a) and the second spaces (51b, 52b, 53b) between the internal spaces (23a, 23b, 23c), the first (51a, 52a, 53a) and second spaces (51b, 52b, 53b) and the regulation spaces flow (41a, 42a, 43a) are divided by flow regulation components (41, 42, 43), and inlet flow ports (41x, 42x, 43x) are provided for flow regulation components (41 , 42, 43), in such a way that a cross sectional area of passage of the refrigerant going from the flow regulation spaces (41a, 42a, 43a) to the first spaces (51a, 52a, 53a) can be strangled.
[0002]
2. Heat exchanger (20) according to claim 1, characterized in that the lower communication passages (51y, 52y, 53y, 151y, 215y) are arranged above the inlet flow ports (41x, 42x, 43x) and close to the lower flat tubes (21b) above the inlet flow ports (41x, 42x, 43x), whose tubes are those located in the lowest locations among the flat tubes (21b) located above the input stream (41x, 42x, 43x).
[0003]
3. Heat exchanger (20), according to claim 1, characterized by the fact that the lower communication passages (51y, 52y, 53y, 151y, 215y) are constituted by lower sections of the division components (51 , 52, 53, 151, 251) and upper sections of the flow regulation components (41, 42, 43).
[0004]
Heat exchanger (20) according to any one of claims 1 to 3, characterized in that the loop structure is arranged in locations (23a, 23b, 23c) in such a way that, when a function such as an evaporator for the refrigerant is made, it is possible for the refrigerant, after having passed through a part of the plurality of flat tubes (21b), to flow in a distributed way to another part of the plurality of flat tubes (21b).
[0005]
5. Heat exchanger (20) according to claim 4, characterized by the fact that the plurality of flat tubes (21b) is connected at one end of them to a return junction collection tube (23, 123, 223) which includes the junction collection tube and returns the refrigerant flow, and is connected at the other ends to a confronting junction collection tube (22) arranged facing the return junction collection tube (23, 123, 223 ), the plurality of flat tubes (21b) are grouped in an upper side heat exchange area (X) consisting of one or a plurality of upper side heat exchange parts (X1, X2, X3) arranged vertically , and in a heat exchange area on the lower side (Y) located below the heat exchange area on the upper side (X) and consisting of one or a plurality of heat exchange parts on the lower side (Y1, Y2 , Y3) positioned vertically, an internal space on the bottom facing side (22b), colored ning the lower side heat exchange parts (Y1, Y2, Y3) constituting the lower side heat exchange area (Y), it is formed on the bottom side of the interior of the collating junction collection tube (22), the The interior of the return junction collection tube (23, 123, 223) is divided vertically into internal spaces on the upper return side (23a, 23b, 23c) corresponding in number to the number of the heat exchange parts on the upper side ( X1, X2, X3) constituting the heat exchange area on the upper side (X), and in internal spaces on the lower return side (23d, 23e, 23f) corresponding in number to the number of the heat exchange parts on the lower side (Y1, Y2, Y3) constituting the heat exchange area on the lower side (Y); the internal spaces of the upper return side (23a, 23b, 23c) and the internal spaces of the lower return side (23d, 23e, 23f) communicating with each other, and the loop structure is arranged in the internal spaces (23a, 23b, 23c) of the upper return side (23a, 23b, 23c).
[0006]
6. Air conditioning device (1), characterized by the fact that it comprises a refrigerant circuit constituted by connecting the heat exchanger (20) as defined in any one of claims 1 to 5 and a variable capacity compressor (91) .

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法律状态:
2019-12-17| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|

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2020-09-08| B09A| Decision: intention to grant|

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2020-12-01| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 10/07/2014, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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JP2013205783A|JP5754490B2|2013-09-30|2013-09-30|Heat exchanger and air conditioner|

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JP2013-205783|2013-09-30|

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PCT/JP2014/068464|WO2015045564A1|2013-09-30|2014-07-10|Heat exchanger and air conditioner|

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