ES2702291T3 - Heat exchanger and heat exchange method - Google Patents

Abstract

A heat exchanger (1) comprising: a plurality of surface units of the heat exchange function; an upper collecting tube (5); and a lower header tube (7), the plurality of surface units (3) of the heat exchange function having the upper header tube (5), the lower header tube (7), and a plurality of heat exchange tubes heat exchange (9) arranged between a pair of the upper header tube (5) and the lower header tube (7); the plurality of surface units (3) of the heat exchange function having a parallel connection relationship; a plurality of lower collector tubes (7) that are connected to a lower collection tube (19) through a branch current adjusting section (17); wherein the branch current adjusting section (17) comprises a distributor (21) and at least one flow adjusting section (23); wherein the distributor (21) is arranged between the lower collection tube (19) and the plurality of the lower collector tubes (7), and equates a dryness of the refrigerant to be supplied to the plurality of the lower collector tubes (7) ; wherein the at least one flow adjustment section (23) is arranged between the distributor (21) and a corresponding one of the plurality of the lower collector tubes (7); and characterized in that each of the plurality of lower collector tubes (7) having a perforated tube (27), the perforated tube (27) includes distribution holes (29) that are arranged approximately in the lower section of the tube perforated (27).

Description

DESCRIPTION

Heat exchanger and heat exchange method

Technical field

The present invention relates to a heat exchanger and a heat exchange method.

US 5,842,351 A discloses a heat exchanger having the devices in the preamble of claim 1.

Background of the technique

A heat exchanger of a parallel flow type is given as a type of the heat exchanger. This heat exchanger includes a pair of collector tubes and a plurality of flat tubes disposed between the collector tubes. This heat exchanger is configured so that after a fluid, which has flowed in one of the collecting tubes, flows through the plurality of flat tubes, the fluid flows out towards the other of the collecting tubes.

In this parallel flow type heat exchanger when the pair of collector tubes is arranged in a vertical up and down direction, due to the influence of gravity, the refrigerant liquid in two phases coolant is capable of flowing to the flat tubes positioned on a relatively low side, it being thus difficult to equally distribute the refrigerant to the plurality of flat tubes.

Therefore, the parallel flow type heat exchanger can have a structure in which the pair of collector tubes is arranged horizontally so as to suppress the influence of gravity on each other between the plurality of flat tubes.

On the other hand, an existing outdoor unit of an air conditioner may have such a structure that the heat exchange surfaces are disposed on a plurality of surfaces of a housing of the outdoor unit. When the aforementioned parallel flow type heat exchanger having the pair of collector tubes arranged horizontally is forced to exert its function on the plurality of surfaces of the housing of the outdoor unit it is necessary to bend each of the collector pipes along of the plurality of surfaces. However, when the collector tube is curved in, for example, an L-shape or a U-shape, significant loads are applied, and therefore problems arise that the apparatus is oversized and the costs increase.

To deal with these problems, for example, there is a heat exchanger described in Literature 1 of the Patent. In the heat exchanger described in Literature 1 of the Patent, a pair of collector tubes have been prepared separately for each of a plurality of surfaces.

Appointment list

Patent Literature

[PTL 1] JP 2010-107103 A.

US5842351 A discloses an improved distribution system for an evaporator. The system comprises an evaporator having a plurality of flow paths of the heat exchanger; and an evaporator distributor that operably connects the plurality of flow paths to an inlet to the evaporator. The system includes a shock device having an output operably connected to the inlet of the evaporator and having at least one pair of fluid inlets arranged so that the fluid entering through any of the fluid inlets directly impacts. against the fluid entering through the other fluid inlet thus providing a stirred fluid at the outlet of the shock device. Additionally, the system includes an expansion device that has an inlet and an outlet; and a separator having an inlet of the separator connected to the outlet of the expansion valve and having at least one pair of outlets. The separator is arranged to divide the fluid from the expansion device into several streams and direct those currents to their outputs. The system also includes at least one pair of conduits, each having a first end connected to an outlet of the separator and a second end connected to an input of the impact device.

US4373353A discloses a refrigerant control for a one-room air conditioner that operates to reduce the charge on the compressor by throttling the flow of the refrigerant to a predetermined number of circuits in the condenser, while allowing the flow of the refrigerant to the condensers. remaining circuits is not affected. US5704221A discloses a refrigerant exchanger for a refrigeration installation such as a cold storage room or a refrigerated cabinet, which includes a refrigerant or circulating set of heat removing fluid connected to a heat exchange assembly with a large area superficial. The assemblies form a multi-layered arrangement and several rows in the form of a plurality of mutually similar parallel members separated by spacers to provide heat insulation and collect the draining thawing water. Each member comprises at least one layer as well as a respective inlet and outlet that are part of the circulation assembly. At least three members of the provision each have a cooling capacity that is a fraction of the overall rating of the exchanger so that at each time during the operation of the exchanger at least one of the members can be in defrost mode while at least two of the members are in cooling mode, the members in turn in defrost mode and in cooling mode.

EP226438A1 provides a refrigerant distribution device for a cooling system that is capable of improving the efficiency of the heat exchanger, comprising an inlet duct, a lower cover plate, a core, a hollow cylinder, a plate upper deck and multiple branch pipes. The core is disposed in the space formed by the lower cover plate, the cylinder and the upper cover layer, wherein a plurality of openings are distributed in the core. The refrigerant distribution device according to the invention is capable of carrying out the distribution and assignment of the refrigerant in the refrigeration system, and of improving the efficiency of the heat exchange of the refrigeration system.

Summary of the invention

Technical problem

However, the aforementioned heat exchanger described in Patent Literature 1 has employed such a way that after the refrigerant, which has flowed through a plurality of flat tubes on a certain surface (first surface), it is collected to the tube collector of the outflow side of the one surface (first surface), the refrigerant is guided from this collector tube to the collector tube on the inflow side of the next surface (second surface) and distributed through a plurality of flat tubes of the next surface (second surface), and subsequently, the refrigerant is likewise guided to the next surface in sequence depending on the number of surfaces.

For this reason, an upstream / downstream current relationship is generated between a plurality of surface units of the heat exchange function, and the efficiency of the heat exchange is lower on the surface of the downstream side of the current. In addition, the branch to a plurality of flat tubes and the collection following the branch are repeated, and therefore there is fear that in the second and subsequent surfaces the refrigerant after heat exchange can not be adequately branched towards the plurality. of flat tubes again.

The present invention has been made in view of the foregoing, and it is therefore an object of the present invention to provide a heat exchanger and the like, each of which is capable of suppressing, even with a plurality of surface units. of the exchange function, an influence of the gravity exerted on the refrigerant, and suppress the reduction of the heat exchange performance in each of the surfaces.

Problem solution

In order to achieve the aforementioned object, a heat exchanger defined in claim 1 is provided.

Furthermore, in order to achieve the same object, according to another embodiment of the present invention, there has been provided a method of heat exchange, defined in claim 6, of carrying out the heat exchange on a plurality of surfaces, including the heat exchange method: preparing an upper collecting tube, a lower collecting tube, and a plurality of heat exchange tubes disposed between a pair of the upper collecting tube and the lower collecting tube in each of a plurality of surface units of the heat exchange function; connecting the plurality of surface units of the heat exchange function in parallel, and connecting a plurality of the lower header tubes to a lower collection tube through a branch current adjustment section; and branching, by the branch current adjustment section, the refrigerant within the lower collection tube in parallel with the plurality of surface units of the heat exchange function, subjecting the refrigerant to heat exchange in each of the plurality of surface units of the heat exchange function, and causing the refrigerant to flow out from a plurality of the upper header tubes to be joined together to an upper side header tube.

Advantageous effects of the invention

According to an embodiment of the present invention it is possible to suppress, even with the plurality of surface units of the heat exchange function, the influence of gravity exerted on the refrigerant, and to suppress the reduction of heat exchange performance in each one of the surfaces.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure 1 is a view illustrating a structure of a heat exchanger according to a first embodiment of the present invention.

Figure 2 is a perspective view of a lower header tube, to illustrate a perforated tube.

Figure 3 is a diagram illustrating the characteristics of a liquid distribution of a lower header tube as an example for comparison.

Figure 4 is a diagram illustrating the characteristics of a liquid distribution of a perforated recessed bottom manifold tube according to the first embodiment of the present invention.

Figure 5 is a view illustrating an external appearance and a plan view of an outdoor unit of a multiple air conditioner for a building according to the first embodiment of the present invention. Figure 6 is a view illustrating an external appearance and a plan view of an outdoor unit of an outdoor air conditioner assembly according to a second embodiment of the present invention.

Description of the realizations

Now, a heat exchanger and a heat exchange method according to the embodiment of the present invention are described with reference to the accompanying drawings. It should be noted that in the drawings the same reference symbols represent the same or corresponding parts.

First realization

Figure 1 is a view illustrating a structure of a heat exchanger according to a first embodiment of the present invention. The heat exchanger of this embodiment functions as an outdoor unit of an air conditioner which is installed in a space of intended use, and performs heating and cooling. Therefore, the heat exchanger is a parallel flow type heat exchanger in which when the heat exchanger operates as a condenser in a cooling phase, the refrigerant flows from the top to the bottom as indicated by dotted line arrows in Figure 1, and when the heat exchanger operates as an evaporator in a heating phase the refrigerant flows from the bottom to the top as indicated by solid line arrows in Figure 1.

A heat exchanger 1 has a plurality of surface units 3 of the heat exchange function. It should be noted that Figure 1 illustrates an example in which three surface units 3 of the heat exchange function are arranged. Further, in the example of Figure 1 the surface units 3 of the contiguous heat exchange function are structured to be orthogonally directed to each other.

An upper collecting tube 5, a lower collecting tube 7, and a plurality of heat exchange tubes 9 disposed between the pair of upper and lower collecting tubes 5, 7 are arranged in each of the surface units 3 of the function of heat exchange. Specifically, a flat tube is used as the heat exchange tube 9. A fin 11 (specifically a corrugated fin) is disposed between the heat exchange tubes 9.

One end of an upper communication tube 13 is connected to each of the upper header pipes 5. The other end side of the upper communication pipe 13 is connected to an upper collection pipe 15. Each of the lower header pipes 7 is connected to a lower collection tube 19 through a branch current adjustment section 17 described below. In such a manner, the plurality of surface units 3 of the heat exchange function are arranged in a parallel connection relationship between the upper collection tube 15 and the lower collection tube 19. It should be noted that, although it has been omitted In an illustration, it is assumed that a pair of the surface units 3 of the heat exchange function are covered with a blocking member such as a metal plate so that the fluid to be subjected to the heat exchange is not bridged.

The branch current adjustment section 17 serves to adjust a dryness and a flow rate of the refrigerant to be supplied to the plurality of lower manifold tubes 7. Note that, as an example, this embodiment is described in the form of a configuration in the that when the refrigerant flows from the bottom to the top in the heating phase a gas-liquid two-phase refrigerant is supplied to the plurality of surface units 3 of the heat exchange function with equal dryness and flow.

As an example of a configuration for performing equalization of such dryness and flow rate, the branch current adjustment section 17 includes a manifold 21 and at least one (two in the illustration) adjustment section 23 of the flow rate. One end side of the distributor 21 is connected to the lower collection tube 19, and a plurality of connection ports on the other end side thereof are connected to the ends on one side of the corresponding lower communication tubes 25. In addition, the ends on the other side of the lower communication tubes 25 are connected to the lateral input and output ports 7a for collecting the corresponding corresponding lower header tubes 7, respectively. The distributor 21 connected in such a manner supplies the refrigerant to the plurality of lower communication tubes 25 with the same dryness. In the illustrated example, a capillary is used as flow adjustment section 23. Although the flow adjustment section 23 is disposed between the distributor 21 and the corresponding lower header pipe 7, that is, in the lower communication pipe 25, the flow adjustment section 23 is not necessarily arranged in all the communication pipes. lower 25.

In each of the surface units 3 of the heat exchange function, the side inlet and outlet port 7a of the lower collecting tube 7 and an inlet and outlet port 5a of collecting the upper collecting tube 5 are mutually positioned opposite one another in a direction in which the collecting tube extends. In other words, the inlet and outlet port 7a of the collecting side of the lower collecting tube 7 is disposed on an end side of the lower collecting tube 7, and the inlet and outlet port 5a of collecting the upper collecting tube 5 is disposed in the other end side of the upper collecting tube 5. That is, the distribution paths of the refrigerant between the lateral collecting inlet and the outlet port 5a the inlet and outlet ports 7a of the collecting side are designed to be approximately equal in the length of the flow path even through any of the heat exchange tubes 9.

As illustrated in Figure 2, a perforated tube 27 is disposed within each of the lower header tubes 7. Figure 2 is a perspective view of the lower header tube, to illustrate the perforated tube. The plurality of heat exchange tubes 9 and the communication holes with the plurality of heat exchange tubes 9, which are supposedly positioned above the lower collecting tube 7, are omitted in their illustration.

The perforated tube 27 is a block-shaped or tube-shaped member, and is disposed approximately in the vicinity of the center of the space within the lower header tube 7 in a state in which the perforated tube 27 is floated from an inner surface of the lower collecting tube 7. Furthermore, a large number of distribution holes 29 are formed in the perforated tube 27. According to the invention defined in claim 1, the distribution holes 29 are arranged approximately in the lower section of the perforated tube. 27

A double tube structure is obtained by a combination of such a perforated tube 27 and the lower collecting tube 7. Therefore, for example, in the heating phase, after the refrigerant, which flows through the lower communication tube. , temporarily flowing to the perforated tube 27, the refrigerant also flows outwardly from the large number of distribution holes 29 to the outside of the perforated tube 27 in a deep direction (in a horizontal direction of the drawing sheet of Figure 2). In addition, the refrigerant is likewise dispersed within the lower collecting tube 7 to be equally supplied from the communication holes (not shown) of the upper surface of the collecting tube 7 lower than the plurality of heat exchange tubes 9.

Next, a description of the effects of the perforated tube described above is made. Figure 3 is a diagram illustrating the characteristics of the liquid distribution of a lower collecting tube as an example for comparison, which is arranged horizontally and does not have the perforated tube. Figure 4 is a diagram illustrating the distribution characteristics of a perforated tube type lower manifold tube according to this embodiment, which is arranged horizontally.

In addition, in the parts of the graph of Figure 3 and Figure 4, an abscissa axis represents a path number, that is, the numbers of flow paths of the heat exchange tubes arranged in the direction of the depth of the lower manifold tube (flow paths of 28 flat tubes inserted vertically into the upper surface of the lower manifold tube). An ordinate represents a liquid distribution ratio for each road number. In addition, the experimental results of three cases 1, 2 and 3 are shown in which a flow rate Gr of the coolant [kg / hour] and a dryness X of the inlet port are changed with respect to the lower manifolds of the example to compare already this realization.

First, in the comparison example illustrated in Figure 3, in cases 1 and 3, in which the flow rates Gr of the refrigerant are each 90 [kg / hour] and the dryness X of the inlet port are different from one of another, the effect that the refrigerant is kept in contact with the interior of a lower collecting tube 7 ', and therefore does not bounce inside the lower collecting tube 7', has not been shown. Therefore, it is understood that the refrigerant flows directly to the heat exchange tubes 9, and therefore the liquid distribution ratio is higher in the downstream zone (the road numbers of No. 23 to 28) . In addition, in case 2 it shows the flow rate of 180 [kg / hour], which is more than that of case 1 and case 3, due to the presence of the coolant that is abundantly supplied, the effect of which the Coolant liquid bouncing inside the lower collecting tube 7 ', or that the flow is disturbed provides the tendency to relax the imbalance characteristics of the liquid to a certain extent. However, any of the cases is outside an example of an equal distribution line indicated in parallel with the abscissa axis.

On the other hand, in the perforated recessed tube type lower collecting tube of this embodiment illustrated in Figure 4, it is understood that the satisfactory liquid distribution characteristics shown approximately along the equal distribution line are obtained in all three cases 1, 2 and 3 regardless of the coolant flow and the dryness of the inlet port. This results from the following fact. That is, the perforated tube 27 is inserted into the lower collecting tube 7, and the distribution holes 29 of the perforated tube 27 are disposed in a downward direction of the perforated tube 27. In this way, an operation of removing a liquid film from the coolant, which exists in an annular zone surrounded by an inner surface of the lower collecting pipe 7, and an outer surface of the perforated pipe 27, by the bubbles expelled from the lower part of the perforated pipe 27 is desirably obtained regardless of the dryness of the inlet port and the flow rate. As a result, the equal distribution of the refrigerant is achieved.

Accordingly, a description of a specific application example of the aforementioned heat exchanger illustrated in Figure 1 is made. Although this embodiment exemplifies a way such that the refrigerant dryness and the refrigerant flow rate are likewise adjusted for the plurality of the surface units 3 of the heat exchange function, an application is given to the outdoor unit of a multiple air conditioner for a building as the specific application example. Figure 5 is a view illustrating an exterior appearance and the plan view of the outdoor unit of a multiple air conditioner for a building. The outdoor unit of a multiple air conditioner for a building is used as a high performance appliance that is larger in size than an outdoor unit for general domestic use.

As illustrated in Figure 5, in an outdoor unit 101 of a multiple air conditioner for a building, the surface units 3 of the heat exchange function are assigned to three surfaces of a housing 103, respectively. In a plan view a propeller fan 105 is disposed at the center of these surface units 3 of the heat exchange function. In addition, as indicated by the arrows 107, air is introduced into the housing 103 from three side surfaces of the housing 103 and is subjected to heat exchange in the surface units 3 of the heat exchange function. Next, as indicated by the arrows 111, air is expelled from an air outlet formed in a fan guard 109 disposed on an upper surface of the housing 103 (upper flow type).

Next, a description is given of an operation of the heat exchanger performed in such a manner and of the method of heat exchange according to this embodiment. In the phase of the heating operation, the heat exchanger 1 which serves as the outdoor unit functions as an evaporator. The gas-liquid phase refrigerant, which has entered the distributor 21, becomes a uniform mist flow when it passes through a hole (not shown) to be supplied to each of the lower communication tubes 25. Then, the uniform mist flow is adjusted in its flow rate in each of the flow adjustment sections 23 to flow to the lower header tube 7 of the corresponding surface unit 3 of the heat exchange function. The coolant, which has flowed to the lower collecting pipe 7 through the lateral collection inlet and the outlet port 7a of the lower collecting pipe 7, is expelled from the distribution holes 29 of the perforated pipe 27 to be equally distributed to the pipes heat exchange 9. In the perforated tube 27, when the dryness is large, minimal droplets are expelled from the small holes. When the dryness is small, the bubbles are expelled to the part of liquid collected in the annular section. Therefore, the distribution is made independently of the dryness and the flow rate. After the refrigerant is subjected to the exchange of heat with the air (not shown) when they have passed through the heat exchange tubes 9, the refrigerant flows into the upper collecting tube 5 and then flows out through the collecting side inlet and from the outlet port 5a on the side opposite to the side inlet and outlet port 7a of the lower header pipe 7. The refrigerant, which has flowed out through each of the inlet and outlet ports 5a, passes through the corresponding upper communication tube 13 to join another refrigerant in the upper collection tube 15. It must be taken into account that in the phase of the cooling operation the heat exchanger 1 functions as a condenser, and therefore the coolant flow.

As described so far, according to the heat exchanger and the heat exchange method using the heat exchanger of the present invention, the following advantages are obtained. First, in the surface units of the heat exchange function the collector tubes are directed in the horizontal direction and therefore the influence of gravity can be suppressed for the distribution of the refrigerant, and the refrigerant can be equally distributed to the plurality of heat exchange tubes. In addition, although the collecting tubes are horizontally distributed in such a manner, a plurality of surfaces can be controlled to show the heat exchange function without being prevented by the current situation that the curve of the collecting tube is difficult to form. In addition, although the heat exchange is performed on a plurality of surfaces, the refrigerant is branched in its distribution in parallel to the plurality of surface units of the heat exchange function. Therefore, the upstream / downstream relationship is not mutually generated between the plurality of surface units of the heat exchange function, and therefore the satisfactory heat exchange efficiency can be maintained in each of the units of surface of the heat exchange function. In particular, in this embodiment, after the dryness and the flow rate of the refrigerant have been desirably adjusted depending on the conditions of the surface units of the heat exchange function through the distributor and the flow adjustment section, the Coolant is supplied to the surface units of the heat exchange function in a distributive manner. Therefore, satisfactory heat exchange performance can be obtained in all surface units of the heat exchange function. In addition, the entire heat exchanger does not have a flow path that the refrigerant, which has been subjected to the heat exchange in the plurality of heat exchange tubes, is picked up once, and is branched back to the plurality of tubes of heat exchange. Therefore, there is no such problem that the refrigerant can not be equally supplied to the plurality of heat exchange tubes. Accordingly, in accordance with the heat exchanger and the heat exchange method of this embodiment, even with the plurality of heat exchange surface units, the influence of gravity exerted on the The coolant can be suppressed, and the reduction of the heat exchange performance on each of the surfaces can be suppressed.

In addition, in each of the surface units of the heat exchange function, the inlet and outlet port of the lower manifold tube and the inlet and outlet port of the upper manifold tube are disposed on opposite sides of one another. Therefore, even when the refrigerant passes through any of the heat exchange tubes, the pressure losses become approximately equal to each other, that is, the equal distribution of the flow in two gas-liquid phases can be done. In addition, the perforated tube is disposed within the lower manifold tube, with the result that minute droplets or bubbles are expelled from the distribution holes to the annular section of the double structure, in order to promote the equal distribution of the refrigerant in two. gas-liquid phases. Furthermore, in this embodiment the number of distributions to the heat exchange tubes is increased, and the number of times of the distribution is suppressed low (in the example described above the number of times of the distribution is only one). Therefore, although innumerable heat exchange tubes are used in order to prepare the plurality of surface units of the heat exchange function, the pressure loss of the refrigerant can be suppressed relatively low with the number of exchange tubes of heat. Therefore, in particular, the low pressure refrigerant (such as a refrigerant showing a large pressure loss of the refrigerant), for example HF01234yf, HF01234ze, or R134a can also be used effectively.

Second embodiment

A description is made of a second embodiment of the present invention with reference to Figure 6. The first embodiment described above exemplifies a mode in which the dryness of the refrigerant is adjusted equally for the plurality of the surface units of the exchange function. of heat, and the flow rate of the refrigerant is changed depending on the heat loads (mainly depend on the speed of the air passing in the heat exchange section), which are different from each other in the surface units of the function of heat exchange. However, the present invention is not limited to that mode. That is, the present invention also encompasses a mode such that the refrigerant dregs and / or the refrigerant flow rates are adjusted to be different from one another in the plurality of surface units of the heat exchange function. As an example of a specific application, an application is given to an assembly of the outdoor unit of the air conditioner. Figure 6 illustrates an external appearance and a plan view of the application to the outdoor unit of the air conditioning assembly.

As illustrated in Figure 6, in an outdoor unit 201 of the air conditioner assembly the surface units 3 of the heat exchange function are assigned to a side surface and a rear surface of a housing 203, respectively. By the rotation of a propeller fan 205, as indicated by the arrows 207, air is introduced into the housing 203 from the side surface and the rear surface of the housing 203, and is subjected to heat exchange in the units 3 of surface of the heat exchange function. Next, as indicated by the arrows 211, air is expelled from an air outlet disposed on the front surface of the housing 203.

Also according to the second embodiment, similar to the first embodiment, even with the plurality of surface units of the heat exchange function, the influence of gravity exerted on the refrigerant can be suppressed, and the reduction of heat exchange performance in each of the surfaces.

The details of the present invention have been described above specifically with reference to the preferred embodiments, but it is clear that a person skilled in the art can employ various modifications based on the thoughts and technical teachings of the present invention.

For example, although in the perforated tube described above, the large number of distribution holes have been described as being arranged in the downward direction, the mode of formation of the distribution holes is not limited thereto, and the orientation, the number, and the hole shape of the distribution holes can be changed properly. In addition, the structure of the branch current adjustment section described above is thus only one example, and therefore can be changed appropriately. For example, a branch current adjustment section having such a way that the height positions of a plurality of lateral branch pipes of the outlet port such as the Y-shaped branch pipes or the distributors of Low pressure loss are made different from each other, a current flow of a branch of a liquid phase is changed by an influence of gravity, and the dryness and flow rate are adjusted simultaneously.

List of reference signs

1 heat exchanger, 3 surface unit of the heat exchange function, 5 upper collector pipe, 7 lower collector pipe, 5a, 7a side inlet and outlet collection port, 9 heat exchange pipe, 17 adjustment section branch current, 19, lower collection tube, 21 distributor, 23 flow adjustment section, 25 lower communication tube, 27 perforated tube, 29 distribution hole.

Claims (7)

1. A heat exchanger (1) comprising: a plurality of surface units of the heat exchange function; an upper collecting tube (5); Y a lower collector tube (7), the plurality of surface units (3) of the heat exchange function having the upper collecting tube (5), the lower collecting tube (7), and a plurality of heat exchange tubes (9) disposed between a pair of the upper collecting tube (5) and the lower collecting tube (7); the plurality of surface units (3) of the heat exchange function having a parallel connection ratio; a plurality of lower manifold tubes (7) that are connected to a lower collection tube (19) through a branch current adjustment section (17); wherein the branch adjustment section (17) comprises a distributor (21) and at least one flow adjusting section (23); wherein the distributor (21) is disposed between the lower collection tube (19) and the plurality of the lower collecting tubes (7), and equals a dryness of the refrigerant to be supplied to the plurality of the lower collecting tubes (7) ; wherein the at least one flow adjusting section (23) is disposed between the distributor (21) and a corresponding one of the plurality of the lower header tubes (7); Y characterized in that each of the plurality of lower manifold tubes (7) having a perforated tube (27), the perforated tube (27) includes distribution holes (29) that are arranged approximately in the lower section of the perforated tube (27) 2. A heat exchanger (1) according to claim 1, wherein in each of the plurality the surface units (3) of the heat exchange function, a port (7a) of lateral inlet and outlet of the heat exchange function. collecting the lower collecting tube (7) is disposed on an end side of the lower collecting tube (7), and a side (5a) of intake and lateral collection port of the upper collecting tube (5) is disposed at another side end of the tube upper collector (5). 3. A heat exchanger (1) according to claim 1 or 2, wherein the refrigerant to be used comprises HFO1234yf, HFO1234ze, or R134a as a low pressure refrigerant. 4. A refrigeration cycle system comprising the heat exchanger according to any of claims 1 to 3. 5. An air conditioner comprising the heat exchanger according to any of claims 1 to 3. 6. A heat exchange method of carrying out the heat exchange on a plurality of surfaces using the heat exchanger defined in claim 1, characterized in that: The heat exchange method comprises: preparing an upper collecting tube (5), a lower collecting tube (7), and a plurality of heat exchange tubes (9) disposed between a pair of the upper collecting tube (5) and the lower collecting tube (7) at each one of a plurality of surface units (3) of the heat exchange function, each of the plurality of lower manifold tubes (7) having a perforated tube (27), including the perforated tube (27) a few holes of distribution (29) that are arranged approximately in the lower section of the perforated tube (27); connecting the plurality of surface units (3) of the heat exchange function in parallel, and connecting a plurality of the lower header tubes (7) to a lower collection tube (19) through an adjustment section (17) ) of the branch current, the branch adjustment section (17) comprising a distributor (21) and at least one flow adjusting section (23), the at least one flow adjusting section (23) being arranged between the distributor (21) and a corresponding one of the plurality of lower manifold tubes (7); branching, by the branch adjustment section (17), the refrigerant within the lower collection tube (19) in parallel to the plurality of surface units (3) of the heat exchange function, subjecting the refrigerant to heat exchange in each of the plurality of surface units (3) of the heat exchange function, and causing the refrigerant to flow out from a plurality of the upper header pipes (5) to be joined together with a pipe top collection (15); Y the distributor (21) being arranged between the lower collection tube (19) and the plurality of lower collecting tubes (7), and equalizing a dryness of the refrigerant to be supplied to the plurality of the lower collecting tubes (7). 7. A heat exchange method according to claim 6, wherein the refrigerant to be used comprises HFO1234yf, HFO1234ze, or R134a as a low pressure refrigerant.