WO2012153490A1

WO2012153490A1 - Heat exchanger and cold cycle device provided therewith

Info

Publication number: WO2012153490A1
Application number: PCT/JP2012/002912
Authority: WO
Inventors: 寿守務吉村; 浩昭中宗; 瑞朗酒井; 宗史池田
Original assignee: 三菱電機株式会社
Priority date: 2011-05-06
Filing date: 2012-04-27
Publication date: 2012-11-15
Also published as: JP2014139484A

Abstract

An intermediate header (31) is provided in the middle portion in the longitudinal direction of a first flat tube (1). The intermediate header (31) partitions the first flat tube (1) into an upstream first flat tube (11) upstream of a high-temperature coolant and a downstream first flat tube (12) downstream of the high-temperature coolant, and high-temperature coolant that has liquefied in the upstream portion of the first flat tube (1) flows downwards in the intermediate header (31). By this means, in the coolant flow path in the downstream portion of the first flat tube (1), it is possible to suppress condensate of the high-temperature coolant from covering the inner surface of the flow path (the heat-transmitting surface) and forming a thermal resistance layer, making it possible to obtain a heat exchanger with improved heat exchange performance, and a cold cycle device provided therewith.

Description

Heat exchanger and refrigeration cycle apparatus including the same

The present invention relates to a heat exchanger that performs heat exchange between a high-temperature refrigerant and a low-temperature refrigerant, and a refrigeration cycle apparatus including the heat exchanger.

As a conventional heat exchanger, a first flat tube having a plurality of through holes through which a high-temperature fluid (that is, a high-temperature refrigerant) flows, and a second flat tube having a plurality of through-holes through which a low-temperature fluid (that is, a low-temperature refrigerant) flows. A first header connected to both ends of the first flat tube, and a second header connected to both ends of the second flat tube, and the first flat tube and the second flat tube are arranged in a longitudinal direction (fluid of fluid There is one in which flat surfaces are contact-laminated by brazing or the like such that the flow direction is parallel (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 2002-340485 (page 8, FIG. 1)

However, when the heat exchanger as described above is used as a condenser, in the flow path on the high temperature fluid side, condensate increases along the flow direction as the high temperature fluid condenses, and the condensate flows in the flow path. The inner surface (heat transfer surface) will be covered. Therefore, there is a problem that the condensed liquid becomes a heat resistance layer and the heat exchange performance is lowered. Further, in order to obtain the heat exchange performance required in such a case, it is necessary to increase the heat transfer area, and there is a problem that the heat exchanger becomes large.

The present invention has been made to solve the above-described problems, and a first object is to obtain a heat exchanger with improved heat exchange performance and a refrigeration cycle apparatus including the same. .
Moreover, the 2nd objective is to obtain the heat exchanger which can be comprised compactly, and a refrigeration cycle apparatus provided with the same.

The heat exchanger according to the present invention is configured such that a first flow path portion configured by arranging a plurality of refrigerant flow paths through which a high-temperature refrigerant flows in parallel and a plurality of refrigerant flow paths through which a low-temperature refrigerant flows are arranged in parallel. The second flow path portion and the first flow path portion are disposed at one end in the flow direction of the high-temperature refrigerant, and form a cylindrical flow path that communicates with each of the refrigerant flow paths. A first inlet portion that flows into the first flow path portion and a cylindrical flow path that is disposed at the other end of the first flow path portion in the flow direction of the high-temperature refrigerant and communicates with each of the refrigerant flow paths; Formed and disposed at one end of the second flow path portion in the flow direction of the low-temperature refrigerant, and flows into each of the refrigerant flow paths. A cylindrical inlet channel is formed, and a second inlet for allowing a low-temperature refrigerant to flow into the second channel from outside, and a low temperature of the second channel. A second outlet portion that is disposed at the other end in the flow direction of the medium, forms a cylindrical channel that communicates with each refrigerant channel, and causes the low-temperature refrigerant to flow out from the second channel unit; An intermediate communication part disposed in the middle of the refrigerant flow path of the first flow path part and forming a cylindrical flow path communicating with at least a part of the refrigerant flow path of the first flow path part, The refrigerant flow paths of the first flow path section and the refrigerant flow paths of the second flow path section are arranged so that the flow path directions are parallel and adjacent to each other via a partition wall, and the intermediate communication The portion is for causing the high-temperature refrigerant condensed in the upstream portion of the first flow path portion to flow downward.

According to the present invention, in the refrigerant flow path in the downstream portion of the first flow path portion, the high temperature refrigerant condensate is prevented from covering the flow path inner surface (heat transfer surface) and becoming a heat resistance layer. Therefore, heat exchange performance can be improved. Further, this eliminates the need to increase the heat transfer area, and the heat exchanger 8 can be made compact.

It is an external view of the heat exchanger 8 which concerns on Embodiment 1 of this invention. It is an external appearance perspective view of another form of the heat exchanger 8 which concerns on Embodiment 1 of this invention. It is an external appearance perspective view of the heat exchanger 8a which concerns on Embodiment 2 of this invention. It is an external appearance perspective view of the heat exchanger 8b which concerns on Embodiment 3 of this invention. It is an external view of the heat exchanger 8c which concerns on Embodiment 4 of this invention. It is a figure which shows the state which makes a refrigerant | coolant flow in toward the tangential direction of the circular cross section of the intermediate header 31 of the heat exchanger 8c which concerns on Embodiment 4 of this invention. It is an external appearance perspective view of the heat exchanger 8d which concerns on Embodiment 5 of this invention. It is an external appearance perspective view of the heat exchanger 8e which concerns on Embodiment 6 of this invention. It is a refrigerant circuit diagram which shows an example of the refrigeration cycle apparatus which concerns on Embodiment 7 of this invention. It is a refrigerant circuit figure which shows an example of the refrigerating-cycle apparatus which concerns on Embodiment 8 of this invention. It is a refrigerant circuit figure which shows an example of the refrigerating-cycle apparatus which concerns on Embodiment 9 of this invention. It is an external appearance side view of the heat exchanger 8f which concerns on Embodiment 10 of this invention. It is an external appearance perspective view of the heat exchanger 8g which concerns on Embodiment 11 of this invention. It is an external appearance perspective view of the heat exchanger 8h which concerns on Embodiment 12 of this invention. It is an external appearance perspective view of the heat exchanger 8i which concerns on Embodiment 12 of this invention. It is an external appearance perspective view of the heat exchanger 8j which concerns on Embodiment 13 of this invention. It is an external appearance perspective view of the heat exchanger 8k which concerns on Embodiment 14 of this invention.

Embodiment 1 FIG.
(Configuration of heat exchanger 8)
FIG. 1 is an external view of a heat exchanger 8 according to Embodiment 1 of the present invention. Among these, FIG. 1A is a perspective view of the heat exchanger 8, and FIG. 1B is a plan view of the heat exchanger 8.
As shown in FIG. 1, the heat exchanger 8 includes a flat first flat tube 1 having a plurality of through holes through which a high-temperature refrigerant (refrigerant or the like) flows in the longitudinal direction, and a low-temperature refrigerant (water or the like) in the longitudinal direction. A flat second flat tube 2 having a plurality of through-holes flowing therethrough, a first inlet header 3 and a first outlet header 4 connected to both longitudinal ends of the first flat tube 1, and a second flat tube 2, a second inlet header 5 and a second outlet header 6 connected to both longitudinal ends. Further, an intermediate header 31 is provided in the middle portion of the first flat tube 1 in the longitudinal direction. The first flat tube 1 is provided with an upstream first flat plate that is upstream of the high-temperature refrigerant. It is divided into a pipe 11 and a downstream first flat pipe 12 that is the downstream side of the high-temperature refrigerant. These pipes and headers are made of, for example, aluminum or an aluminum alloy, copper or a copper alloy, or steel or a stainless alloy, and are manufactured by, for example, extrusion or pultrusion.

The first flat tube 1 and the second flat tube 2 are laminated by joining the flat surfaces by brazing or the like so that the longitudinal direction (flow direction of the refrigerant) is parallel. Moreover, each through-hole formed in the 1st flat tube 1 and the 2nd flat tube 2 comprises the refrigerant | coolant flow path through which a refrigerant | coolant distribute | circulates. Here, although the high-temperature refrigerant | coolant assumes the refrigerant | coolant accompanying a phase change, it does not ask | require whether a low-temperature refrigerant | coolant is what has only a phase change (water etc.).

The first inlet header 3 has a cylindrical shape, is attached to one end in the longitudinal direction of the first flat tube 1, and the high-temperature refrigerant flowing into the first flat header 1 flows into each refrigerant flow path of the first flat tube 1. Inflow. The first inlet header 3 has an upper surface portion opened and a lower surface portion closed in order to allow the high-temperature refrigerant to flow from the upper surface.

The first outlet header 4 has a cylindrical shape, is attached to an end opposite to the first inlet header 3 in the longitudinal direction of the first flat tube 1, and each refrigerant channel of the first flat tube 1. The high-temperature refrigerant that has flowed into the inside from the outside flows out to the outside. The first outlet header 4 has a lower surface portion opened and a top surface portion closed in order to allow the high-temperature refrigerant to flow out from the lower surface.

The second inlet header 5 has a cylindrical shape and is attached to the same side as the first outlet header 4 attached to the first flat tube 1 in both longitudinal ends of the second flat tube 2. The low-temperature refrigerant that has flowed into the inside flows into the refrigerant flow paths of the second flat tube 2. The second inlet header 5 has an upper surface portion opened and a lower surface portion closed in order to allow a low-temperature refrigerant to flow (not shown) from the upper surface.

The second outlet header 6 has a cylindrical shape, and is opposite to the second inlet header 5 in the longitudinal direction of the second flat tube 2, that is, both end portions of the second flat tube 2 in the longitudinal direction. Among them, it is attached to the same side as the first inlet header 3 attached to the first flat tube 1, and causes the low-temperature refrigerant flowing into each of the refrigerant channels of the second flat tube 2 to flow outside. is there. Further, the second outlet header 6 has a lower surface portion opened and a top surface portion closed to allow the low-temperature refrigerant to flow out (not shown) from the lower surface.

Further, as shown in FIG. 1 (b), the first inlet header 3 and the second outlet header 6 are arranged slightly shifted in the flow direction of the refrigerant flow path. The same applies to the first outlet header 4 and the second inlet header 5. Thereby, when it is necessary to increase the inner diameter of each header, the heat exchanger 8 can be reduced in thickness and can be made compact.

The first inlet header 3 and the second inlet header 5 are configured such that the upper surface portion is opened and the lower surface portion is closed. However, the present invention is not limited to this, and the lower surface portion is opened and the upper surface portion is closed. It is good also as a closed structure.
The first outlet header 4 and the second outlet header 6 are configured such that the lower surface portion is opened and the upper surface portion is closed. However, the present invention is not limited to this, and the upper surface portion is opened and the lower surface portion is It is good also as a closed structure.

Further, as shown in FIG. 1, the first inlet header 3, the first outlet header 4, the second inlet header 5, the second outlet header 6 and the intermediate header 31 are each cylindrical, but are not limited thereto. Any other shape may be used as long as it has a cylindrical shape.

The intermediate header 31 has a cylindrical shape and is installed in the middle of the first flat tube 1 in the longitudinal direction, as described above, and each refrigerant flow path of the upstream first flat tube 11 and downstream The side first flat tube 12 communicates with each refrigerant flow path. As will be described later, the intermediate header 31 has a function of separating the liquid high-temperature refrigerant condensed from the high-temperature refrigerant in the upstream first flat tube 11, and causes the liquid high-temperature refrigerant to flow down to the outside. The bottom surface is opened and the top surface is closed.

The first flat tube 1, the second flat tube 2, the first inlet header 3, the first outlet header 4, the second inlet header 5, the second outlet header 6, and the intermediate header 31 are respectively referred to as “first” It corresponds to a “flow channel portion”, a “second flow channel portion”, a “first inlet portion”, a “first outlet portion”, a “second inlet portion”, a “second outlet portion”, and an “intermediate communication portion”.
The wall where the first flat tube 1 and the second flat tube 2 are joined corresponds to the “partition wall” of the present invention.

(Heat exchange operation of the heat exchanger 8)
Next, the heat exchange operation between the high-temperature refrigerant and the low-temperature refrigerant in the heat exchanger 8 will be described with reference to FIG. Fig.1 (a) has shown the flow of the high temperature refrigerant | coolant when the heat exchanger 8 which concerns on this Embodiment acts as a condenser, The arrow of FH (gas) in a figure shows the high temperature refrigerant | coolant of a gas state The arrow of FH (liquid) indicates the flow of the high-temperature refrigerant in the liquid state.

The high-temperature refrigerant flows into the inside from the upper surface portion of the first inlet header 3, in the order of the refrigerant flow path of the upstream first flat tube 11, the intermediate header 31, and the refrigerant flow path of the downstream first flat tube 12. It flows through and flows out from the lower surface portion of the first outlet header 4. On the other hand, the low-temperature refrigerant flows into the inside from the upper surface portion of the second inlet header 5, flows through the refrigerant flow path of the second flat tube 2, and flows out from the lower surface portion of the second outlet header 6. In that case, the high temperature refrigerant | coolant which distribute | circulates the refrigerant | coolant flow path of the upstream 1st flat tube 11 and the downstream 1st flat tube 12, and the low temperature refrigerant | coolant which distribute | circulates the refrigerant | coolant flow path of the 2nd flat tube 2 are each joining surface. The heat exchange is carried out in a counter flow through

Here, the behavior of the high-temperature refrigerant will be described in detail. The high-temperature refrigerant in the gas state (or gas-liquid two-phase state) flows into the inside from the upper surface portion of the first inlet header 3 and flows through the refrigerant flow path of the upstream first flat tube 11 in the second stage. Heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path of the flat tube 2. At least part of the absorbed high-temperature refrigerant is condensed and liquefied, and the gas-liquid two-phase high-temperature refrigerant flows into the intermediate header 31. At this time, among the high-temperature refrigerant in the gas-liquid two-phase state that has flowed into the intermediate header 31, most of the liquid-state high-temperature refrigerant falls by its own weight and flows down toward the lower side of the intermediate header 31. It flows out to the outside. Therefore, most of the high-temperature refrigerant in the liquid state is separated by the intermediate header 31 from the high-temperature refrigerant in the gas-liquid two-phase state. The high-temperature refrigerant, which is mostly in a liquid state after being separated from most of the liquid high-temperature refrigerant, flows into the refrigerant flow path of the downstream first flat tube 12, and in the course of its circulation, the second flat tube 2. The heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path. And the high temperature refrigerant | coolant which flowed in in the 1st exit header 4 from the refrigerant | coolant flow path of the downstream 1st flat tube 12 flows out out of the lower surface part.

(Effect of Embodiment 1)
As described above, the intermediate header 31 separates most of the high-temperature refrigerant in the liquid state condensed in the upstream first flat tube 11, and almost all the high-temperature refrigerant in the gas state flows into the downstream first flat tube 12. Inflow. Therefore, in the refrigerant flow path of the downstream first flat tube 12, it is possible to suppress the condensate of the high-temperature refrigerant from covering the flow path inner surface (heat transfer surface) and becoming a heat resistance layer, so heat exchange Performance can be improved. Further, this eliminates the need to increase the heat transfer area, and the heat exchanger 8 can be made compact.

Further, since the first inlet header 3 and the second outlet header 6 and the first outlet header 4 and the second inlet header 5 are arranged slightly shifted in the flow direction of the refrigerant flow path, the inner diameter of each header The heat exchanger 8 can be thinned and the size can be reduced, for example, when it is necessary to increase the size.
Moreover, as shown in FIG.1 (c), the intermediate header 31 may be provided with two or more in the middle part of the longitudinal direction of the 1st flat tube 1 (two in a figure). In this case, the condensate of the high-temperature refrigerant condensed in the upstream first flat tube 11 separates the condensate before covering the flow path inner surface (heat transfer surface) thickly, and can be prevented from becoming a heat resistance layer. Since the ratio of the 1 flat tube 12 increases, heat exchange performance can be improved more. Further, this eliminates the need to increase the heat transfer area, and the heat exchanger 8 can be made compact.

As shown in FIG. 2, the outflow pipe 41 installed at the lower part of the first outlet header 4 and the lower part of the intermediate header 31 are connected by a bypass pipe 42, and the flow rate adjusting means is connected to the bypass pipe 42. 43 may be provided. Thereby, the high-temperature refrigerant in the liquid state separated by the intermediate header 31 flows through the bypass pipe 42 and merges with the high-temperature refrigerant flowing out from the first outlet header 4 through the flow rate adjusting means 43 in the outflow pipe 41. All of the high temperature refrigerant flows out of the heat exchanger 8. The bypass pipe 42 is not limited to the configuration connected to the outflow pipe 41, and the lower part of the intermediate header 31 and the lower part of the first outlet header 4 are connected, and the combined high-temperature refrigerant is the first. It is good also as a structure which flows out through the outflow pipe 41 from the lower part of the exit header 4. FIG.

The heat exchanger 8 is a condenser in which a high-temperature refrigerant flows through the first flat tube 1, a low-temperature refrigerant flows through the second flat tube 2, and the high-temperature refrigerant condenses in the first flat tube 1. As explained. However, it is not limited to this, The heat exchanger 8 is good also as what acts as an evaporator. In this case, in FIG. 2, the low-temperature refrigerant flows in the first flat tube 1, and the high-temperature refrigerant flows in the second flat tube 2. At this time, the flow rate adjusting means 43 is closed. As a result, all of the low-temperature refrigerant flows into the first outlet header 4 through the outflow pipe 41, and flows in the order of the downstream first flat pipe 12, the intermediate header 31, and the upstream first flat pipe 11. it can.
Needless to say, when the heat exchanger 8 functions only as a condenser, it is not necessary to install the flow rate adjusting means 43.

Further, as shown in FIG. 1, the heat exchanger 8 is configured to have the intermediate header 31 only in the first flat tube 1, but is not limited thereto. For example, the heat exchanger 8 acts as an evaporator, a high-temperature refrigerant circulates in the second flat tube 2, and this high-temperature refrigerant absorbs heat instead of water or the like that does not cause a phase transition, so that the liquid state changes from a gas state In the case of a refrigerant that undergoes phase transition, the intermediate header 31 may also be installed on the second flat tube 2. Thereby, when the heat exchanger 8 acts as a condenser, the liquid state refrigerant is separated in the intermediate header 31 of the first flat tube 1, and when acting as an evaporator, the intermediate header of the second flat tube 2. In 31, the liquid fluid can be separated. Therefore, heat exchange performance can be improved both when the heat exchanger 8 acts as a condenser and when it acts as an evaporator. Further, if the intermediate header 31 of the first flat tube 1 and the intermediate header 31 of the second flat tube 2 are arranged slightly shifted in the refrigerant flow direction, the heat exchanger 8 is made thin. Can be made compact.

Moreover, although the high temperature refrigerant | coolant which distribute | circulates the 1st flat tube 1 and the low temperature refrigerant | coolant which distribute | circulates the 2nd flat tube 2, heat exchange shall be implemented by counterflow through each junction surface, It is not limited and heat exchange may be performed as a parallel flow.

Further, as shown in FIG. 1, the intermediate header 31 is in communication with all the refrigerant flow paths of the first flat tube 1, but is not limited thereto. That is, it may be configured to communicate with at least a part of the refrigerant flow path of the first flat tube 1, for example, with respect to a part of the refrigerant flow path positioned above the first flat pipe 1, these As for the refrigerant flow path, the refrigerant flow path of the upstream first flat tube 11 and the refrigerant flow path of the downstream first flat tube 12 may be in direct communication.

Embodiment 2. FIG.
The heat exchanger 8a according to the present embodiment will be described with a focus on differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.

(Configuration of heat exchanger 8a)
FIG. 3 is an external perspective view of the heat exchanger 8a according to Embodiment 2 of the present invention.
As shown in FIG. 3, the downstream first flat tube 12 included in the heat exchanger 8 a is formed so that the width thereof is larger than the width of the upstream first flat tube 11. The downstream first flat tube 12 is installed such that its lower surface is located below the lower surface of the upstream first flat tube 11. At this time, the refrigerant flow path of the downstream first flat tube 12 that is located below the lower surface of the upstream first flat tube 11 forms a bypass flow path 42a. The bypass flow path 42a replaces the bypass pipe 42 shown in FIG. Further, the intermediate header 31 provided in the heat exchanger 8a is closed on both the upper surface portion and the lower surface portion, unlike the intermediate header 31 provided in the heat exchanger 8 according to Embodiment 1. About another structure, it is the same as that of the heat exchanger 8 which concerns on Embodiment 1. FIG.

(Heat exchange operation of the heat exchanger 8a)
Next, the heat exchange operation between the high-temperature refrigerant and the low-temperature refrigerant in the heat exchanger 8a will be described with reference to FIG. FIG. 3 shows the flow of the high-temperature refrigerant when the heat exchanger 8a according to the present embodiment acts as a condenser, and the FH (gas) arrow in the figure indicates the flow of the high-temperature refrigerant in the gas state. , FH (liquid) arrows indicate the flow of high-temperature refrigerant in the liquid state.

The operation until the high-temperature refrigerant flows into the first inlet header 3, passes through the refrigerant flow path of the upstream first flat tube 11, and flows into the intermediate header 31 into the gas-liquid two-phase state is performed. This is the same as the heat exchanger 8 according to the first embodiment. Of the high-temperature refrigerant in the gas-liquid two-phase state that has flowed into the intermediate header 31, most of the high-temperature refrigerant in the liquid state falls by its own weight and flows downward below the intermediate header 31, and then flows downstream from the lower portion of the intermediate header 31. It flows into the bypass flow path 42a which is a refrigerant flow path formed in the lower part of the side first flat tube 12. Therefore, most of the high-temperature refrigerant in the liquid state is separated by the intermediate header 31 from the high-temperature refrigerant in the gas-liquid two-phase state. On the other hand, among the high-temperature refrigerants in the gas-liquid two-phase state flowing into the intermediate header 31, most of the high-temperature refrigerants in the liquid state are separated, and the high-temperature refrigerant almost in the gas state is downstream as in the first embodiment. In the process of flowing into and flowing through the refrigerant flow path of the side first flat tube 12, heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path of the second flat tube 2. And the high temperature refrigerant | coolant which distribute | circulated the bypass flow path 42a of the downstream 1st flat tube 12 and the high temperature refrigerant | coolant which distribute | circulated refrigerant flow paths other than the bypass flow path 42a of the downstream 1st flat tube 12 are 1st. 1 It mixes in the exit header 4, and flows out outside from the lower surface part.

Further, the behavior of the low-temperature refrigerant is the same as that in the first embodiment.

(Effect of Embodiment 2)
As described above, by forming the bypass flow path 42a in the downstream first flat tube 12, the liquid high-temperature refrigerant separated by the intermediate header 31 can be circulated in another flow path. Since the bypass pipe 42 and the flow rate adjusting means 43 of the heat exchanger 8 according to the first embodiment are not necessary, the structure can be simplified. Moreover, it cannot be overemphasized that it has the same effect as the heat exchanger 8 which concerns on Embodiment 1. FIG.

Embodiment 3 FIG.
The heat exchanger 8b according to the present embodiment will be described mainly with respect to differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.

(Configuration of heat exchanger 8b)
FIG. 4 is an external perspective view of a heat exchanger 8b according to Embodiment 3 of the present invention.
As shown in FIG. 4, a columnar collision member 32 is installed in the intermediate header 31 provided in the heat exchanger 8 b so as to coincide with the longitudinal direction. About another structure, it is the same as that of the heat exchanger 8 which concerns on Embodiment 1. FIG.

(Heat exchange operation of the heat exchanger 8b)
The behavior of the high-temperature refrigerant and the low-temperature refrigerant is basically the same as that in the first embodiment. However, in the present embodiment, the gas-liquid two-phase high-temperature refrigerant that has flowed into the intermediate header 31 collides with the collision member 32, whereby liquid droplets that are difficult to separate and mist-state fluid are separated, and liquid separation is performed. Is promoted. As a result, the efficiently separated liquid high-temperature refrigerant flows down along the collision member 32, and the amount of liquid high-temperature refrigerant flowing into the downstream first flat tube 12 can be reduced.

(Effect of Embodiment 3)
By installing the collision member 32 in the intermediate header 31 as described above, it becomes possible to efficiently separate the liquid from the high-temperature refrigerant in the gas-liquid two-phase state, and the liquid flowing into the downstream first flat tube 12 The amount of the high-temperature refrigerant in the state can be reduced, and further the condensation performance and heat exchange performance can be improved. Moreover, it cannot be overemphasized that it has the same effect as the heat exchanger 8 which concerns on Embodiment 1. FIG.

4 shows a configuration in which only one collision member 32 is installed in the intermediate header 31, this is not a limitation, and a configuration in which a plurality of collision members 32 is installed. It is good. Moreover, although the collision member 32 shall be arrange | positioned so that it may correspond with the longitudinal direction in the intermediate header 31, it is not limited to this, You may arrange | position so that a direction may not correspond. The columnar collision member 32 is not limited to this, but may be a wave shape, a zigzag shape, a net shape, or the like, and the high-temperature refrigerant in the gas-liquid two-phase state that has flowed into the intermediate header 31 is liquid-separated. Any shape can be used.

Further, the configuration of the outflow pipe 41, the bypass pipe 42 and the flow rate adjusting means 43 in the heat exchanger 8 according to the first embodiment shown in FIG. You may apply the structure of the bypass flow path 42a of the downstream 1st flat tube 12 in the heat exchanger 8a which concerns on Embodiment 2 shown.

Further, the configuration in which the collision member 32 is installed in the intermediate header 31 can also be applied to the intermediate header 31 in the second embodiment.

Embodiment 4 FIG.
The heat exchanger 8c according to the present embodiment will be described mainly with respect to differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.
In Embodiment 1, the 1st flat tube 1 showed the structure by which the upstream 1st flat tube 11 and the downstream 1st flat tube 12 are arrange | positioned through the intermediate header 31 in the flow direction of a refrigerant | coolant. In the present embodiment, a configuration in which the upstream first flat tube 11 and the downstream first flat tube 12 are arranged vertically will be described.

(Configuration of heat exchanger 8c)
FIG. 5 is an external view of a heat exchanger 8c according to Embodiment 4 of the present invention. Among these, Fig.5 (a) is a perspective view of the heat exchanger 8c, and FIG.5 (b) is a top view of the heat exchanger 8c.
As shown in FIG. 5, the upstream first flat tube 11 and the downstream first flat tube 12 constituting the first flat tube 1 have flat surfaces parallel to the upper and lower portions of the cylindrical shape of the intermediate header 31. It is connected to become. In other words, the upstream first flat tube 11 is disposed above the intermediate header 31 and the downstream first flat tube 12 is disposed below the intermediate header 31 so as not to contact each other. A first inlet header 3 is attached to the other end of the upstream first flat tube 11 in the refrigerant flow direction, and a first outlet header 4 is attached to the other end of the downstream first flat tube 12 in the refrigerant flow direction. Is attached.

The upper surface of the first inlet header 3 is opened and the lower surface is closed in order to allow high temperature refrigerant to flow from the upper surface.

The first outlet header 4 has a bottom surface opened and a top surface closed to allow the high-temperature refrigerant to flow out from the bottom surface.

As will be described later, the intermediate header 31 has a function of separating the condensed liquid high-temperature refrigerant from the high-temperature refrigerant in the upstream first flat tube 11, and flows the liquid high-temperature refrigerant down to the outside. For this purpose, the lower surface portion is opened and the upper surface portion is closed.

Further, the second flat tube 2 is joined to each of the upstream first flat tube 11 and the downstream first flat tube 12 by brazing or the like between the flat surfaces so that the refrigerant flow direction is parallel. Are stacked.

The second inlet header 5 is attached to the same side as the intermediate header 31 attached to the upstream first flat tube 11 and the downstream first flat tube 12 in both ends of the second flat tube 2 in the refrigerant flow direction. It has been. The second inlet header 5 has an upper surface portion opened and a lower surface portion closed in order to allow a low-temperature refrigerant to flow (not shown) from the upper surface.

The second outlet header 6 is attached to the end opposite to the second inlet header 5 in the refrigerant flow direction of the second flat tube 2 among the both ends of the second flat tube 2 in the refrigerant flow direction. . That is, on both ends of the second flat tube 2, on the same side as the first outlet header 3 attached to the upstream first flat tube 11 and the first outlet header 4 attached to the downstream first flat tube 12. It is attached. Further, the second outlet header 6 has a lower surface portion opened and a top surface portion closed to allow the low-temperature refrigerant to flow out (not shown) from the lower surface.

Further, as shown in FIG. 5B, the first inlet header 3 and the first outlet header 4 (not shown) and the second outlet header 6 are arranged with a slight shift in the flow direction of the refrigerant flow path. Has been. The same applies to the second inlet header 5 and the intermediate header 31. As a result, when it is necessary to increase the inner diameter of each header, the heat exchanger 8c can be thinned, and the size can be reduced.

(Heat exchange operation of the heat exchanger 8c)
Next, the heat exchange operation between the high-temperature refrigerant and the low-temperature refrigerant in the heat exchanger 8c will be described with reference to FIG. Fig.5 (a) has shown the flow of the high temperature refrigerant | coolant when the heat exchanger 8c which concerns on this Embodiment acts as a condenser, The arrow of FH (gas) in a figure shows the high temperature refrigerant | coolant of a gas state The arrow of FH (liquid) indicates the flow of the high-temperature refrigerant in the liquid state.

The high-temperature refrigerant flows into the inside from the upper surface portion of the first inlet header 3, in the order of the refrigerant flow path of the upstream first flat tube 11, the intermediate header 31, and the refrigerant flow path of the downstream first flat tube 12. It flows through and flows out from the lower surface portion of the first outlet header 4. On the other hand, the low-temperature refrigerant flows into the inside from the upper surface portion of the second inlet header 5, flows through the refrigerant flow path of the second flat tube 2, and flows out from the lower surface portion of the second outlet header 6. In that case, the high temperature refrigerant | coolant which distribute | circulates the refrigerant | coolant flow path of the upstream 1st flat tube 11 and the downstream 1st flat tube 12, and the low temperature refrigerant | coolant which distribute | circulates the refrigerant | coolant flow path of the 2nd flat tube 2 are each joining surface. Heat exchange is performed via

Here, the behavior of the high-temperature refrigerant will be described in detail. The high-temperature refrigerant in the gas state (or gas-liquid two-phase state) flows into the inside from the upper surface portion of the first inlet header 3 and flows through the refrigerant flow path of the upstream first flat tube 11 in the second stage. Heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path of the flat tube 2. At least part of the absorbed high-temperature refrigerant is condensed and liquefied, and the gas-liquid two-phase high-temperature refrigerant flows into the intermediate header 31. At this time, the gas-liquid two-phase high-temperature refrigerant that has flowed into the intermediate header 31 collides with the inner wall surface of the intermediate header 31, whereby liquid droplets that are difficult to separate and mist refrigerant are separated, and liquid separation is promoted. The As a result, of the high-temperature refrigerant in the gas-liquid two-phase state, most of the liquid-state high-temperature refrigerant is separated, falls by its own weight, flows down below the intermediate header 31, and flows out from the lower surface portion to the outside. . Then, most of the liquid high-temperature refrigerant is separated, and the high-temperature refrigerant almost in the gas state flows into the refrigerant flow path of the downstream first flat tube 12 located below the upstream first flat tube 11. In the process of circulation, heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path of the second flat tube 2. And the high temperature refrigerant | coolant which flowed in in the 1st exit header 4 from the refrigerant | coolant flow path of the downstream 1st flat tube 12 flows out out of the lower surface part.

(Effect of Embodiment 4)
As described above, the high-temperature refrigerant in the gas-liquid two-phase state can be efficiently separated by colliding with the inner wall surface of the intermediate header 31, and the liquid flowing into the downstream first flat tube 12. The amount of the high-temperature refrigerant in the state can be reduced, and further the condensation performance and heat exchange performance can be improved.

Further, since the first inlet header 3 and the second outlet header 6 and the first outlet header 4 and the second inlet header 5 are arranged slightly shifted in the flow direction of the refrigerant flow path, the inner diameter of each header The heat exchanger 8 can be thinned and the size can be reduced, for example, when it is necessary to increase the size.

In addition, you may apply the structure of the outflow pipe | tube 41, the bypass piping 42, and the flow volume adjustment means 43 in the heat exchanger 8 which concerns on Embodiment 1 shown by FIG. 2 to the heat exchanger 8c of this Embodiment.

Further, regarding the behavior of the low-temperature refrigerant in the heat exchanger 8 c, it flows into the inside from the upper surface portion of the second inlet header 5, flows through the refrigerant flow path of the second flat tube 2, and from the lower surface portion of the second outlet header 6. Although it is supposed to flow out, it is not limited to this. That is, the second outlet header 6 may flow into the inside from the lower surface portion (or upper surface portion) and flow out from the upper surface portion (or lower surface portion) of the second inlet header 5.

Further, as shown in FIG. 5A, the upstream side first flat tube 11 and the downstream side first flat tube 12 are arranged on the intermediate header 31 so that their refrigerant flow direction directions coincide in plan view. Although connected, the present invention is not limited to this and may not match. However, in that case, it is necessary to change the shape of the second flat tube 2 so as to join the flat surfaces of the upstream first flat tube 11 and the downstream first flat tube 12.

Further, regarding the behavior of the gas-liquid two-phase high-temperature refrigerant flowing into the intermediate header 31, the liquid high-temperature refrigerant is separated by simply colliding with the inner wall surface of the intermediate header 31, but this is not limitative. Is not to be done. That is, as shown in FIGS. 6A and 6B, the intermediate header 31 has a cylindrical shape, and the high-temperature refrigerant in the gas-liquid two-phase state is directed toward the tangential direction of the circular cross section of the intermediate header 31. It is good also as what is comprised so that it may flow in. As a result, a swirling flow of the high-temperature refrigerant is generated in the intermediate header 31, and the high-temperature refrigerant in the liquid state is centrifuged and can be separated more efficiently.
The configuration in which the shape of the intermediate header 31 is cylindrical and the high-temperature refrigerant is allowed to flow in the tangential direction of the cylindrical cross section can also be applied to the intermediate header 31 in the first to third embodiments.

Moreover, even if the structure which installs the collision member 32 in the intermediate header 31 like the heat exchanger 8b which concerns on Embodiment 3 shown by FIG. 4 at the heat exchanger 8c which concerns on this Embodiment is applied. Good.

Embodiment 5. FIG.
The heat exchanger 8d according to the present embodiment will be described mainly with respect to differences from the configuration and operation of the heat exchanger 8c according to the fourth embodiment.
In the fourth embodiment, the configuration is shown in which the upstream first flat tube 11 and the downstream first flat tube 12 arranged vertically are joined to the second flat tube 2 that is an integral type. In the present embodiment, a configuration in which the second flat tube 2 is also divided in the vertical direction will be described in the same manner as the first flat tube 1.

(Configuration of heat exchanger 8d)
FIG. 7 is an external perspective view of a heat exchanger 8d according to Embodiment 5 of the present invention.
As shown in FIG. 7, the second flat tube 2 is configured by a downstream second flat tube 21 and an upstream second flat tube 22 that are divided into upper and lower portions, like the first flat tube 1. The downstream second flat tube 21 is laminated by joining the respective flat surfaces to each other by brazing or the like so that the refrigerant flow direction is parallel to the upstream first flat tube 11. Further, the upstream second flat tube 22 is laminated by joining the respective flat surfaces by brazing or the like so that the refrigerant flow direction is parallel to the downstream first flat tube 12. .

In addition, the second inlet header 5 whose lower surface portion is open and whose upper surface portion is closed is the second inlet header 5 attached to the downstream first flat tube 12 among the both ends of the upstream second flat tube 22 in the refrigerant flow direction. 1 is attached to the same side as the outlet header 4. In addition, the second outlet header 6 whose upper surface portion is open and whose lower surface portion is closed is the second outlet header 6 attached to the upstream first flat tube 11 in both ends of the downstream second flat tube 21 in the refrigerant flow direction. It is attached to the same side as the one inlet header 3. Furthermore, the other end of the downstream second flat tube 21 (the same side as the end of the upstream first flat tube 11 in the direction of the refrigerant flow path where the intermediate header 31 is attached) and the upstream second An intermediate header 51 is attached to the other end of the flat tube 22 (the same side as the end of the downstream first flat tube 12 in the direction of the refrigerant flow path where the intermediate header 31 is attached).

Further, for the same purpose as the heat exchanger 8c according to the fourth embodiment, the first inlet header 3 and the second outlet header 6 are arranged slightly shifted in the flow direction of the refrigerant flow path. The same applies to the first outlet header 4 and the second inlet header 5, and the intermediate header 31 and the intermediate header 51. As a result, the heat exchanger 8d can be made thinner and more compact when it is necessary to increase the inner diameter of each header.

The intermediate header 51 corresponds to the “second intermediate communication portion” of the present invention.

(Heat exchange operation of the heat exchanger 8d)
Next, the heat exchange operation between the high-temperature refrigerant and the low-temperature refrigerant in the heat exchanger 8d will be described with reference to FIG. FIG. 7 shows the flow of the high-temperature refrigerant when the heat exchanger 8d according to the present embodiment acts as a condenser, and the FH (gas) arrow in the figure indicates the flow of the high-temperature refrigerant in the gas state. , FH (liquid) arrows indicate the flow of high-temperature refrigerant in the liquid state.

The high-temperature refrigerant flows into the inside from the upper surface portion of the first inlet header 3, in the order of the refrigerant flow path of the upstream first flat tube 11, the intermediate header 31, and the refrigerant flow path of the downstream first flat tube 12. It flows through and flows out from the lower surface portion of the first outlet header 4. On the other hand, the low-temperature refrigerant flows into the inside from the lower surface portion of the second inlet header 5, and the refrigerant channel of the upstream second flat tube 22, the intermediate header 51, and the refrigerant channel of the downstream second flat tube 21. And flows out from the upper surface of the second outlet header 6. At this time, the high-temperature refrigerant that flows through the upstream first flat tube 11 and the low-temperature refrigerant that flows through the downstream second flat tube 21 are subjected to heat exchange in a counterflow through their respective joint surfaces. Moreover, the high temperature refrigerant | coolant which distribute | circulates the downstream 1st flat tube 12 and the low temperature refrigerant | coolant which distribute | circulates the upstream 2nd flat tube 22 are heat-exchanged by counterflow through each junction surface.

Here, the behavior of the high-temperature refrigerant will be described in detail. The high-temperature refrigerant in the gas state (or gas-liquid two-phase state) flows into the inside from the upper surface portion of the first inlet header 3 and flows through the refrigerant flow path of the upstream first flat tube 11 in the downstream side. Heat is absorbed by the low-temperature refrigerant flowing through the refrigerant flow path of the second flat tube 21. At least part of the absorbed high-temperature refrigerant is condensed and liquefied, and the gas-liquid two-phase high-temperature refrigerant flows into the intermediate header 31. At this time, the gas-liquid two-phase high-temperature refrigerant that has flowed into the intermediate header 31 collides with the inner wall surface of the intermediate header 31, whereby liquid droplets that are difficult to separate and mist refrigerant are separated, and liquid separation is promoted. The As a result, of the high-temperature refrigerant in the gas-liquid two-phase state, most of the liquid-state high-temperature refrigerant is separated, falls by its own weight, flows down below the intermediate header 31, and flows out from the lower surface portion to the outside. . Then, most of the liquid high-temperature refrigerant is separated, and the high-temperature refrigerant almost in the gas state flows into the refrigerant flow path of the downstream first flat tube 12 located below the upstream first flat tube 11. In the process of circulation, heat is absorbed by the low-temperature refrigerant that flows through the refrigerant flow path of the upstream second flat tube 22. And the high temperature refrigerant | coolant which flowed in in the 1st exit header 4 from the refrigerant | coolant flow path of the downstream 1st flat tube 12 flows out out of the lower surface part.

(Effect of Embodiment 5)
As described above, the high-temperature refrigerant in the gas-liquid two-phase state can be efficiently separated by colliding with the inner wall surface of the intermediate header 31, and the liquid flowing into the downstream first flat tube 12. The amount of the high-temperature refrigerant in the state can be reduced, and further the condensation performance and heat exchange performance can be improved.

In addition, compared with the heat exchanger 8c according to the fourth embodiment, the heat exchanger 8d according to the present embodiment has the same length of the high-temperature refrigerant flow path and the low-temperature refrigerant flow path, and thus further heat exchange. Performance can be improved.

In addition, you may apply the structure of the outflow pipe | tube 41, the bypass piping 42, and the flow volume adjustment means 43 in the heat exchanger 8 which concerns on Embodiment 1 shown by FIG. 2 to the heat exchanger 8d of this Embodiment.

In addition, as shown in FIG. 7, in a plan view, the upstream first flat tube 11 and the downstream first flat tube 12 are connected to the intermediate header 31 so that the respective refrigerant flow channel directions coincide with each other, The downstream side second flat tube 21 and the upstream side second flat tube 22 are also connected to the intermediate header 51 so that the respective refrigerant flow path directions coincide with each other. However, the present invention is not limited to this and does not match. It may be a thing. In this case, the upstream first flat tube 11 and the downstream second flat tube 21, and the downstream first flat tube 12 and the upstream second flat tube 22 are joined to each other by flat surfaces. do it.

Further, as shown in FIG. 7, the intermediate header 31 and the intermediate header 51 are configured to be attached to the same side of the first flat tube 1 and the second flat tube 2 in the refrigerant flow direction, respectively. It is good also as a structure attached to the other side rather than a refrigerant | coolant flow path direction. In this case, the second inlet header 5 and the second outlet header 6 are also attached to the opposite side of the first inlet header 3 and the first outlet header 4.

Further, the behavior of the low-temperature refrigerant in the heat exchanger 8d is assumed to flow from the lower surface portion of the second inlet header 5 and flow out from the upper surface portion of the second outlet header 6, but is not limited to this. That is, the low-temperature refrigerant may flow from the upper surface portion of the second outlet header 6 and flow out from the lower surface portion of the second inlet header 5. In this case, heat exchange between the high-temperature refrigerant and the low-temperature refrigerant is performed by a parallel flow.

Further, regarding the behavior of the gas-liquid two-phase high-temperature refrigerant flowing into the intermediate header 31, the liquid high-temperature refrigerant is separated by simply colliding with the inner wall surface of the intermediate header 31, but this is not limitative. Is not to be done. That is, as shown in FIGS. 6A and 6B in the fourth embodiment, the intermediate header 31 has a cylindrical shape, and the gas-liquid two-phase high-temperature refrigerant is exchanged with the circular cross section of the intermediate header 31. It is good also as what is comprised so that it may flow toward toward the tangential direction. As a result, a swirling flow of the high-temperature refrigerant is generated in the intermediate header 31, and the high-temperature refrigerant in the liquid state is centrifuged and can be separated more efficiently.

Moreover, even if the structure which installs the collision member 32 in the intermediate header 31 like the heat exchanger 8b which concerns on Embodiment 3 shown by FIG. 4 to the heat exchanger 8d which concerns on this Embodiment is applied. Good.

Embodiment 6 FIG.
In the first embodiment, the first flat tube 1 through which the high-temperature refrigerant, which is a separate body, and the second flat tube 2 through which the low-temperature refrigerant circulate are laminated by joining the flat surfaces by brazing or the like. The configuration was shown. In the present embodiment, a configuration in which a refrigerant flow path through which a high-temperature refrigerant flows and a refrigerant flow path through which a low-temperature refrigerant flows are integrally formed will be described.
(Configuration of heat exchanger 8e)
FIG. 8 is an external perspective view of a heat exchanger 8e according to Embodiment 6 of the present invention.
As shown in FIG. 8, the main body 110 of the heat exchanger 8e according to the present embodiment is formed so that a plurality of first refrigerant flow paths 101a through which a high-temperature refrigerant flows are arranged in a row and penetrate in the longitudinal direction. The first refrigerant path 101 is configured. A plurality of second refrigerant flow paths 102a through which the low-temperature refrigerant flows are arranged in a row so as to be adjacent to the first refrigerant flow paths 101a of the first refrigerant path 101, and are formed so as to penetrate in the longitudinal direction. Two refrigerant paths 102 are configured. The main body 110 in which the first refrigerant path 101 and the second refrigerant path 102 are formed is formed of, for example, aluminum or an aluminum alloy, copper or a copper alloy, or steel or a stainless alloy, for example, extrusion or pultrusion molding. Manufactured by.

A first inlet communication hole 103a that communicates with all the first refrigerant flow paths 101a is formed in one of both ends of the main body 110 in the direction in which the first refrigerant flow paths 101a are arranged. On the other side, first outlet communication holes 104a communicating with all the first refrigerant flow paths 101a are formed in the direction in which the first refrigerant flow paths 101a are arranged.

Further, the second inlet communication that communicates with all the second refrigerant flow paths 102a in the direction in which the second refrigerant flow paths 102a are arranged on the side where the first outlet communication holes 104a are formed on both ends of the main body 110. A hole 105a is formed. In addition, on the side where the first inlet communication hole 103a is formed on both ends of the main body 110, second outlet communication communicating with all the second refrigerant flow paths 102a in the direction in which the second refrigerant flow paths 102a are arranged. A hole 106a is formed.

Further, the first inlet communication hole 103a and the second outlet communication hole 106a are formed with a slight shift in the flow direction of the refrigerant flow path of the first refrigerant path 101 (or the second refrigerant path 102). The first outlet communication hole 104a and the second inlet communication hole 105a are formed so as to be slightly shifted in the flow direction of the refrigerant flow path of the first refrigerant path 101 (or the second refrigerant path 102).

Note that the insertion direction of the first inlet communication hole 103a and the first outlet communication hole 104a does not necessarily have to be perpendicular to the direction of each first refrigerant flow path 101a. Further, the insertion direction of the second inlet communication hole 105a and the second outlet communication hole 106a is not necessarily perpendicular to the direction of the second refrigerant flow path 102a.

The lower ends of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are opened, and the first inlet connection so as to communicate with the outside respectively. The pipe 103, the first outlet connecting pipe 104, the second inlet connecting pipe 105, and the second outlet connecting pipe 106 are connected. The upper ends of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are closed by a sealing member or the like.

Further, an intermediate communication hole communicating with all the first refrigerant flow paths 101a in the direction in which the first refrigerant flow paths 101a are arranged in a portion between the first inlet communication holes 103a and the first outlet communication holes 104a in the main body 110. 131 is formed. The intermediate communication hole 131 has a lower end opened, and an upper end is closed by a sealing member or the like.

In addition, both ends of the plurality of first refrigerant channels 101a and second refrigerant channels 102a formed so as to penetrate in the longitudinal direction of the main body 110 are sealed by pinching or the like or sealed by a sealing member (Not shown).

Note that the first refrigerant path 101, the second refrigerant path 102, the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, the second outlet communication hole 106a, and the intermediate communication hole 131 are the main line, respectively. The “first flow path part”, “second flow path part”, “first inlet part”, “first outlet part”, “second inlet part”, “second outlet part” and “intermediate communication part” of the invention Is equivalent to.

(Heat exchange operation of the heat exchanger 8e)
Next, the heat exchange operation between the high-temperature refrigerant and the low-temperature refrigerant in the heat exchanger 8e will be described with reference to FIG. FIG. 8 shows the flow of the high-temperature refrigerant when the heat exchanger 8e according to the present embodiment acts as a condenser, and the arrow of FH (gas) in the figure shows the flow of the high-temperature refrigerant. .

The high-temperature refrigerant flows into the first inlet communication hole 103a through the first inlet connection pipe 103, flows in the order of the first refrigerant path 101, and the first outlet communication hole 104a, from the first outlet connection pipe 104. leak. On the other hand, the low-temperature refrigerant flows into the second inlet communication hole 105a through the second inlet connection pipe 105, and flows through the second refrigerant path 102 and the second outlet communication hole 106a in this order, and then the second outlet connection pipe. It flows out from 106. At this time, heat exchange is performed between the high-temperature refrigerant flowing through the first refrigerant path 101 and the low-temperature refrigerant flowing through the second refrigerant path 102 in a counterflow via a partition between the refrigerant paths.

Here, the behavior of the high-temperature refrigerant will be described in detail. The high-temperature refrigerant in the gas state (or the gas-liquid two-phase state) flows into the first inlet communication hole 103a from the first inlet connection pipe 103 and flows through each first refrigerant flow path 101a of the first refrigerant path 101. In the process, heat is absorbed by the low-temperature refrigerant flowing through each second refrigerant flow path 102 a of the second refrigerant path 102. At least a part of the absorbed high-temperature refrigerant is condensed and liquefied, and the gas-liquid two-phase high-temperature refrigerant flows into the intermediate communication hole 131. At this time, most of the high-temperature refrigerant in the liquid state out of the gas-liquid two-phase high-temperature refrigerant that has flowed into the intermediate communication hole 131 falls by its own weight and flows down toward the lower side of the intermediate communication hole 131, and its lower end. Out to the outside. Therefore, most of the liquid high-temperature refrigerant is separated from the high-temperature refrigerant in the gas-liquid two-phase state by the intermediate communication hole 131. Then, the high-temperature refrigerant that has been mostly separated from the liquid-state high-temperature refrigerant and is almost in a gas state flows again into the first refrigerant flow passages 101a toward the first outlet communication holes 104a, and in the process of flowing therethrough. The heat is absorbed by the low-temperature refrigerant flowing through each second refrigerant flow path 102a. And the high temperature refrigerant | coolant which flowed in in the 1st exit communication hole 104a from each 1st refrigerant | coolant flow path 101a flows out outside via the 1st exit connection pipe 104. FIG.

(Effect of Embodiment 6)
As described above, most of the liquid high-temperature refrigerant condensed in the first refrigerant path 101 is separated by the intermediate communication hole 131, and almost all the high-temperature refrigerant in the gas state flows downstream. Accordingly, in the first refrigerant path 101 on the downstream side, it is possible to suppress the condensate of the high-temperature refrigerant from covering the flow path inner surface (heat transfer surface) and becoming a heat resistance layer, thereby improving the heat exchange performance. Can be made. Further, this eliminates the need to increase the heat transfer area, and the heat exchanger 8e can be made compact.

In addition, since the first refrigerant path 101 and the second refrigerant path 102 are configured integrally with the main body 110, heat conduction thermal resistance or contact thermal resistance generated in the joint portion when configured separately is suppressed, and Heat exchange performance can be improved.

Since the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, the second outlet communication hole 106a, and the intermediate communication hole 131 are provided in the heat exchanger 8e, the first refrigerant There is no need to provide a separate pipe for connecting to the path 101 and the second refrigerant path 102. Therefore, the heat exchanger 8e can be made compact and the manufacturing operation can be simplified.

Further, the first inlet communication hole 103a and the second outlet communication hole 106a, and the first outlet communication hole 104a and the second inlet communication hole 105a are respectively connected to the refrigerant flow in the first refrigerant path 101 (or the second refrigerant path 102). It is formed with a slight shift in the distribution direction of the road. Therefore, when it is necessary to increase the diameter of each communication hole, each communication hole can be prevented from interfering without increasing the distance between adjacent refrigerant flow paths, and the heat exchanger 8e is compact. Can be achieved.

In addition, you may apply the structure of the outflow pipe | tube 41, the bypass piping 42, and the flow volume adjustment means 43 in the heat exchanger 8 which concerns on Embodiment 1 shown by FIG. 2 to the heat exchanger 8e which concerns on this Embodiment. .

The heat exchanger 8e is a condenser in which a high-temperature refrigerant flows through the first refrigerant path 101, a low-temperature refrigerant flows through the second refrigerant path 102, and the high-temperature refrigerant condenses in the first refrigerant path 101. As explained. However, it is not limited to this, The heat exchanger 8e is good also as what acts as an evaporator. In this case, the low temperature refrigerant flows in the first refrigerant path 101 and the high temperature refrigerant flows in the second refrigerant path 102. At this time, when the configuration of the outflow pipe 41, the bypass pipe 42 and the flow rate adjusting means 43 in the heat exchanger 8 according to Embodiment 1 shown in FIG. 2 is applied to the heat exchanger 8e, the flow rate adjusting means 43 is closed. It shall be. As a result, all of the low-temperature refrigerant flows into the first outlet communication hole 104a via the outflow pipe 41, the first refrigerant path 101 (upstream side), the intermediate communication hole 131, the first refrigerant path 101 (downstream side), and The first inlet communication hole 103a can be circulated in this order.
Needless to say, when the heat exchanger 8e functions only as a condenser, it is not necessary to install the flow rate adjusting means 43.

Further, the configuration in which the shape of the intermediate header 31 in the fourth embodiment is cylindrical and the high-temperature refrigerant is allowed to flow in the tangential direction of the cylindrical cross section is also applied to the intermediate communication hole 131 of the heat exchanger 8e according to the present embodiment. be able to.

Moreover, about the heat exchanger 8e which concerns on this Embodiment, like the structure where the collision member 32 is installed in the intermediate header 31 like the heat exchanger 8b which concerns on Embodiment 3 shown by FIG. The collision member 32 may be installed in the communication hole 131.

In addition, the high-temperature refrigerant that circulates through the first refrigerant path 101 and the low-temperature refrigerant that circulates through the second refrigerant path 102 are assumed to perform heat exchange in a counterflow, but are not limited thereto. It is good also as what implements heat exchange as a parallel flow.

Further, as shown in FIG. 8, the cross-sectional shapes of the first refrigerant flow path 101a and the second refrigerant flow path 102a are rectangular, but the present invention is not limited to this, and any polygon can be used. Also, it may be circular in order to improve pressure resistance. Furthermore, in order to improve the heat transfer performance, a groove may be provided on the inner surface of the refrigerant flow path to increase the heat transfer area. In this case, if the groove is processed at the same time as the extrusion of the heat exchanger 8e and the pultrusion molding, the manufacturing operation can be simplified.

Also, as shown in FIG. 8, the number of refrigerant flow paths in the first refrigerant path 101 and the second refrigerant path 102 is the same, but the present invention is not limited to this. That is, according to the operating conditions of the heat exchanger 8e, the heat of the refrigerant and the fluid property values, the heat transfer performance is high, the pressure loss is low, and the numbers may be different from each other so as to be a suitable heat exchanger. .

Further, the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are configured such that the lower end is opened and the upper end is closed. However, the opening side and the closing side may be reversed individually.

Further, in the heat exchanger 8e according to the present embodiment, the configuration in which the intermediate communication hole 131 is formed so as to communicate with the first refrigerant channel 101a is the heat exchanger according to each of the first to third embodiments. It may be applied instead of the intermediate header 31. That is, instead of the intermediate header 31 formed so as to divide the first flat tube 1 of each heat exchanger according to the first to third embodiments, each refrigerant flow is directed to the first flat tube 1. It is good also as a structure which forms a hole like the intermediate | middle communication hole 131 so that it may connect with a path | route. Thereby, it is not necessary to divide the first flat tube 1 and connect the upstream first flat tube 11 and the downstream first flat tube 12 to the intermediate header 31 respectively, and the manufacturing work can be simplified.

Further, in the heat exchanger 8e according to the present embodiment, a refrigerant flow path corresponding to the bypass flow path 42a in the heat exchanger 8a according to the second embodiment may be configured. That is, the lower end of the intermediate communication hole 131 is closed by a sealing member or the like in the same manner as the upper end, and the downstream side of the lower surface of the first refrigerant path 101 portion upstream of the first inlet communication hole 103a. If the first refrigerant path 101 is formed so that the lower surface of the first refrigerant path 101 is on the lower side, a refrigerant channel corresponding to the bypass channel 42a can be formed.

Embodiment 7 FIG.
Each heat exchanger according to Embodiments 1 to 6 described above is mounted on a refrigeration cycle apparatus such as an air conditioner, a hot water storage apparatus, and a refrigerator. The refrigeration cycle apparatus according to the present embodiment will be described by taking as an example a case where the heat exchanger 8 according to the first embodiment is mounted.

(Configuration of refrigeration cycle apparatus 200)
FIG. 9 is a refrigerant circuit diagram illustrating an example of a refrigeration cycle apparatus according to Embodiment 7 of the present invention.
As shown in FIG. 9, the refrigeration cycle apparatus 200 includes a first compressor 230, a first radiator 231, a heat exchanger 8, a first decompressor 232, and a first cooler 233, which are sequentially connected by refrigerant piping. The first refrigerant circuit is provided. Moreover, the 1st inlet header 3 in the heat exchanger 8 is connected to the 1st heat radiator 231 by refrigerant | coolant piping, and the 1st exit header 4 is connected to the 1st decompression device 232 by refrigerant | coolant piping. The first refrigerant circuit is configured such that the first refrigerant, which is a high-temperature refrigerant, circulates and operates in a vapor compression refrigeration cycle.

Further, the refrigeration cycle apparatus 200 includes a second refrigerant circuit in which a second compressor 240, a second heat radiator 241, a second pressure reducing device 242, and a heat exchanger 8 are sequentially connected by a refrigerant pipe. Moreover, the 2nd inlet header 5 in the heat exchanger 8 is connected to the 2nd decompression device 242 by refrigerant | coolant piping, and the 2nd outlet header 6 is connected to the 2nd compressor 240 by refrigerant | coolant piping. The second refrigerant circuit is configured such that the second refrigerant, which is a low-temperature refrigerant, circulates and operates in a vapor compression refrigeration cycle.

As the first refrigerant and the second refrigerant, a refrigerant such as carbon dioxide, an HFC refrigerant, an HC refrigerant, an HFO refrigerant, ammonia, or a mixed refrigerant thereof is used. In the present embodiment, a case where carbon dioxide is used as the first refrigerant will be described.

(Operation of refrigeration cycle apparatus 200)
The first refrigerant in the gas state is compressed by the first compressor 230 and discharged as a high-temperature and high-pressure supercritical refrigerant. The first high-temperature and high-pressure supercritical refrigerant flows into the first radiator 231 and exchanges heat with air or the like to dissipate heat to become a high-pressure supercritical refrigerant. The high-pressure supercritical first refrigerant flows into the heat exchanger 8, where it is cooled by dissipating heat to the second refrigerant flowing through the second refrigerant circuit. It flows into the apparatus 232 and is depressurized to become a low-temperature low-pressure gas-liquid two-phase refrigerant. This low-temperature and low-pressure gas-liquid two-phase refrigerant flows into the first cooler 233, evaporates by exchanging heat with air or the like, and becomes a low-temperature and low-pressure gas-state refrigerant. The low-temperature and low-pressure gas state first refrigerant is again sucked into the first compressor 230 and compressed.

On the other hand, the second refrigerant in the gas state is compressed by the second compressor 240 and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas state second refrigerant flows into the second radiator 241, exchanges heat with air and the like, and condenses to become a high-pressure liquid state refrigerant. The second refrigerant in the high-pressure liquid state flows into the second decompression device 242 and is depressurized to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This low-temperature and low-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 8, where it absorbs heat and evaporates from the first refrigerant flowing through the first refrigerant circuit, and is a low-temperature and low-pressure gas-state refrigerant. It becomes. The second refrigerant in the low-temperature and low-pressure gas state is again sucked into the second compressor 240 and compressed.

(Effect of Embodiment 7)
In the refrigeration cycle apparatus 200 configured as described above, a large degree of supercooling of the first refrigerant that has flowed out of the first radiator 231 can be secured, and the efficiency of the refrigeration cycle apparatus 200 can be greatly improved. . In particular, in the above example, since carbon dioxide is used as the first refrigerant, the efficiency of the refrigeration cycle apparatus 200 is particularly improved when the heat exchanger 8 dissipates heat to the second refrigerant in a state above the critical point. .

Moreover, when the heat exchanger 8 is downsized, it contributes to downsizing of the entire refrigeration cycle apparatus 200.

In addition, although the example which used the carbon dioxide was demonstrated as a 1st refrigerant | coolant which flows through a 1st refrigerant circuit, it is not limited to this, HFC type refrigerant | coolant, HC type | system | group refrigerant | coolant, HFO type | system | group refrigerant | coolants, such as ammonia, Needless to say, these mixed refrigerants may be used. Even in this case, the efficiency of the refrigeration cycle apparatus 200 can be improved by ensuring a large degree of supercooling of the first refrigerant that has flowed out of the first radiator 231.

Moreover, in the refrigeration cycle apparatus 200 shown in FIG. 9, the case where the heat exchanger 8 is used as a radiator is shown, but the present invention is not limited to this, and the circulation direction of the first refrigerant using a four-way valve or the like. If the above is reversed, the heat exchanger 8 can also be used as a cooler.

In the present embodiment, the second refrigerant circuit is a vapor compression refrigeration cycle, but the second refrigerant is brine (antifreeze) such as water or ethylene glycol aqueous solution, and the second compressor 240 is pumped. It may be configured.
Moreover, as shown in FIG. 9, although the example using the heat exchanger 8 which concerns on Embodiment 1 was shown as a heat exchanger in the refrigerating-cycle apparatus 200 which concerns on this Embodiment, it is limited to this. Needless to say, any one of the heat exchangers 8a to 8e according to the second to sixth embodiments may be used.

Embodiment 8 FIG.
The refrigeration cycle apparatus 200a according to the present embodiment will be described focusing on differences from the configuration and operation of the refrigeration cycle apparatus 200 according to Embodiment 7.

(Configuration of refrigeration cycle apparatus 200a)
FIG. 10 is a refrigerant circuit diagram illustrating an example of a refrigeration cycle apparatus according to Embodiment 8 of the present invention.
As shown in FIG. 10, the refrigeration cycle apparatus 200a is the high temperature discharged from the first compressor 230 except for the first radiator 231 from the configuration of the refrigeration cycle apparatus 200 according to the seventh embodiment shown in FIG. All the high-pressure first refrigerant is cooled in the heat exchanger 8. That is, the refrigeration cycle apparatus 200a shown in FIG. 10 is a so-called secondary loop refrigeration cycle apparatus. In this case, the heat exchanger 8 in the present embodiment replaces the functions of both the first radiator 231 and the heat exchanger 8 in the seventh embodiment.

(Effect of Embodiment 8)
With the above configuration, the necessary heat exchange amount in the heat exchanger 8 is increased, and the volume ratio of the heat exchanger 8 in the entire refrigeration cycle apparatus 200a is the refrigeration according to the seventh embodiment including the first radiator 231. It becomes larger than the cycle device 200. At this time, the heat exchanger 8 is made compact, which contributes to making the entire refrigeration cycle apparatus 200a compact.

In addition, although the case where the heat exchanger 8 was used as a radiator was shown in the refrigeration cycle apparatus 200a shown in FIG. 10, it is not limited to this, and the circulation direction of the first refrigerant using a four-way valve or the like. If the above is reversed, the heat exchanger 8 can also be used as a cooler.

Embodiment 9 FIG.
The refrigeration cycle apparatus according to the present embodiment will be described by taking as an example a case where the heat exchanger 8 according to the first embodiment is mounted.

(Configuration of refrigeration cycle apparatus 200b)
FIG. 11 is a refrigerant circuit diagram illustrating an example of a refrigeration cycle apparatus according to Embodiment 9 of the present invention.
As shown in FIG. 11, the refrigeration cycle apparatus 200b includes a refrigerant circuit in which a compressor 250, a heat radiator 251, a heat exchanger 8, a pressure reducing device 252, and a cooler 253 are sequentially connected by a refrigerant pipe. Yes. Further, a bypass pipe 255 branched from the refrigerant pipe between the heat exchanger 8 and the decompression device 252 is connected to an injection port 256 provided in the compression chamber of the compressor 250 or to the compressor 250 although not shown here. It is connected between the cooler 253. In this bypass pipe 255, the bypass pressure reducing device 254 and the heat exchanger 8 are installed in this order from the branch point of the refrigerant pipe between the heat exchanger 8 and the pressure reducing device 252.

In addition, the first inlet header 3 in the heat exchanger 8 is connected to the radiator 251 through the refrigerant pipe, and the first outlet header 4 is connected to the decompression device 252 through the refrigerant pipe. Further, the second inlet header 5 in the heat exchanger 8 is connected to the bypass pressure reducing device 254 by the refrigerant pipe, and the second outlet header 6 is connected to the injection port 256 of the compressor 250 by the refrigerant pipe.

(Operation of refrigeration cycle apparatus 200b)
The gas refrigerant is compressed by the compressor 250 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant flows into the radiator 251, exchanges heat with air or the like to radiate heat, and the high-pressure refrigerant (high-temperature refrigerant) that flows out of the radiator 251 flows into the heat exchanger 8. The high-pressure refrigerant (high-temperature refrigerant) that has flowed into the heat exchanger 8 is cooled by dissipating heat to the low-temperature refrigerant that has flowed out of the bypass decompression device 254, and further flows into the decompression device 252, where it is depressurized. It becomes a two-phase refrigerant. This low-temperature low-pressure gas-liquid two-phase refrigerant flows into the cooler 253, exchanges heat with air or the like, and evaporates to become a low-temperature low-pressure gas refrigerant. This low-temperature and low-pressure gas refrigerant is again sucked into the compressor 250 and compressed.

Further, a part of the refrigerant that has flowed out of the heat exchanger 8 branches before flowing into the decompression device 252, and flows into the bypass pipe 255. The refrigerant flowing into the bypass pipe 255 is decompressed by the bypass decompression device 254, becomes a low-temperature gas-liquid two-phase refrigerant (low-temperature refrigerant), and flows into the heat exchanger 8. The low-temperature gas-liquid two-phase refrigerant (low-temperature refrigerant) flowing into the heat exchanger 8 is heated by absorbing heat from the high-temperature refrigerant, and is injected into the compression chamber from the injection port 256 of the compressor 250.

As the refrigerant circulating in the refrigeration cycle apparatus 200b, carbon dioxide, HFC refrigerant, HC refrigerant, HFO refrigerant, refrigerant such as ammonia, or a mixed refrigerant thereof is used.

(Effect of Embodiment 9)
Also in the refrigeration cycle apparatus 200b configured as described above, a large degree of supercooling of the refrigerant that has flowed out of the radiator 251 can be secured, and the efficiency of the refrigeration cycle apparatus 200b can be greatly improved.

Further, in the refrigeration cycle apparatus 200b shown in FIG. 11, the higher the saturation temperature (gas-liquid equilibrium temperature) of the low-temperature refrigerant flowing from the heat exchanger 8 into the injection port 256, the higher the efficiency of the compressor 250. Power can be reduced.

As shown in FIG. 11, when the high-temperature refrigerant flowing out from the radiator 251 is cooled by the heat exchanger 8, particularly when the outside air temperature is high and the temperature of the high-temperature refrigerant flowing out from the radiator 251 is relatively high, In the exchanger 8, the temperature difference between the high temperature refrigerant and the low temperature refrigerant can be sufficiently large. For this reason, the temperature of the low-temperature refrigerant injected into the compression chamber of the compressor 250 from the injection port 256 can be maintained high, and high efficiency of the first compressor 230 can be ensured.
In addition, when the other end of the bypass pipe 255 is connected between the compressor 250 and the cooler 253, the refrigerant flowing through the cooler 253 without reducing the refrigeration effect compared to the case where the heat exchanger 8 is not used. The flow rate can be reduced. In particular, when the piping length between the compressor 250 and the cooler 253 is long, it is possible to suppress a decrease in performance due to an increase in pressure loss.

Moreover, when the heat exchanger 8 is downsized, it contributes to downsizing of the entire refrigeration cycle apparatus 200b.

Embodiment 10 FIG.
The heat exchanger 8f according to the present embodiment will be described with a focus on differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.

12A and 12B are side views of the heat exchanger 8f according to the tenth embodiment of the present invention. FIG. 12A is a cylindrical shape in which the cross section of the intermediate header 31 is substantially circular, and FIG. An elliptical or rectangular cylindrical shape is shown.
The intermediate header 31 has a function of separating the condensed liquid high-temperature refrigerant from the high-temperature refrigerant in the upstream first flat tube 11, and in order to cause the liquid high-temperature refrigerant to flow down and flow outside, A part of the side surface portion is opened.
With such a configuration, even when the heat exchanger is horizontally arranged, liquid separation is possible at the intermediate header, and the high-temperature refrigerant in the gas-liquid two-phase state is the first flat side on the downstream side as in the first embodiment. The amount of liquid high-temperature refrigerant flowing into the pipe 12 can be reduced, and the condensation performance and heat exchange performance can be improved.

12B, the gravity separation of the condensate is promoted in the space at the bottom of the intermediate header part, and the condensate generated on the upstream side becomes a buffer space. Even in the case of a large amount, the overflow does not occur and the condensate does not flow downstream, so that the condensation performance and the heat exchange performance can be improved more stably.
In addition, you may apply the collision member 32 in the heat exchanger 8 which concerns on Embodiment 3 shown by FIG. 4 to the intermediate header of the heat exchanger 8f of this Embodiment.

Embodiment 11 FIG.
The heat exchanger 8g according to the present embodiment will be described mainly with respect to differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.
In the present embodiment, the first flat tube 1 and the second flat tube 2 are in the vertical direction, and the first inlet header 3, the first outlet header 4, the second inlet header 5, the second outlet header 6 and the intermediate header 31 are The structure arrange | positioned horizontally is demonstrated.

FIG. 13 is an external view of a heat exchanger 8g according to Embodiment 11 of the present invention, in which (a) is a perspective view and (b) is a side view.
The intermediate header 31 has a function of separating the condensed liquid high-temperature refrigerant from the high-temperature refrigerant in the upstream first flat tube 11, and has one end portion for allowing the liquid high-temperature refrigerant to flow out to the outside. Is open. Further, a trap member that is slightly inclined in the vertical direction is inserted into the intermediate header so as to trap the condensate flowing in from the upstream side and to flow the condensate to the end portion.

With such a configuration, even when the heat exchanger is arranged vertically, liquid separation is possible at the intermediate header, and the high-temperature refrigerant in the gas-liquid two-phase state is the first flat side on the downstream side as in the first embodiment. The amount of liquid high-temperature refrigerant flowing into the pipe 12 can be reduced, and the condensation performance and heat exchange performance can be improved.
In addition, you may apply the collision member 32 in the heat exchanger 8 which concerns on Embodiment 3 shown by FIG. 4 to the intermediate header of the heat exchanger 8g of this Embodiment.

Embodiment 12 FIG.
The heat exchangers 8h and 8i according to the present embodiment will be described focusing on differences from the configuration and operation of the heat exchanger 8 according to the first embodiment.
In the present embodiment, the first flat tube 1 and the second flat tube 2 are in the vertical direction, and the first inlet header 3, the first outlet header 4, the second inlet header 5, the second outlet header 6 and the intermediate header 31 are The structure arrange | positioned horizontally is demonstrated.

14 and 15 are external views of heat exchangers 8h and 8i according to Embodiment 11 of the present invention, in which (a) is a perspective view and (b) is a side view, respectively.
The intermediate header 31 has a function of separating the condensed liquid high-temperature refrigerant from the high-temperature refrigerant in the upstream first flat tube 11, and one side surface portion is provided to allow the liquid high-temperature refrigerant to flow out. The part is opened. Further, one end of the downstream second flat tube 12 protrudes into the intermediate header 31 and is fixed.

With such a configuration, even when the heat exchanger is arranged vertically, liquid separation is possible at the intermediate header, and the high-temperature refrigerant in the gas-liquid two-phase state is the first flat side on the downstream side as in the first embodiment. The amount of liquid high-temperature refrigerant flowing into the pipe 12 can be reduced, and the condensation performance and heat exchange performance can be improved.

Further, as shown in FIG. 15, if the tip of the end in the intermediate header 31 is bent, the upstream condensate can be prevented from flowing directly into the downstream first flat tube 12, Liquid separation at the header can be further promoted. In addition, if the configuration is such that the end of the pipe connected at a part of the side surface portion is bent downward and fixed to the intermediate header in order to allow the condensate to flow outside, the condensate is connected to flow out to the outside. The condensate can be stably separated from the piping without causing gas to flow out.

In addition, you may apply the collision member 32 in the heat exchanger 8 which concerns on Embodiment 3 shown by FIG. 4 to the intermediate header of the heat exchangers 8h and 8i of this Embodiment.

Embodiment 13 FIG.
The heat exchanger 8j according to the present embodiment will be described focusing on the differences from the configuration and operation of the heat exchanger 8 according to the sixth embodiment.
In the sixth embodiment, the first refrigerant path 101, the second refrigerant path 102, the first refrigerant path, and the first refrigerant path 101 are integrally formed of a refrigerant flow path through which a high-temperature refrigerant flows and a refrigerant flow path through which a low-temperature refrigerant flows. Although the case where the inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, the second outlet communication hole 106a, and the intermediate communication hole 131 are arranged in the vertical direction has been shown, A configuration in which is arranged horizontally will be described.

FIG. 16 is a perspective view of a heat exchanger 8j according to Embodiment 13 of the present invention. The intermediate communication hole 131 has a function of separating the condensed liquid high-temperature refrigerant from the high-temperature refrigerant on the upstream side, and in order to cause the liquid high-temperature refrigerant to flow down and flow outside, A part is opened (not shown).

With such a configuration, even when the heat exchanger is horizontally arranged, liquid separation can be performed at the intermediate communication hole, and the high-temperature refrigerant in the gas-liquid two-phase state flows downstream as in the sixth embodiment. The amount of high-temperature refrigerant in the liquid state can be reduced, and the condensation performance and heat exchange performance can be improved.

Note that a hole having a cross-sectional shape like the intermediate header in the heat exchanger 8 according to Embodiment 10 shown in FIG. 12B is applied to the intermediate communication hole of the heat exchanger 8j of this embodiment. Good.
Moreover, you may apply the collision member 32 in the heat exchanger 8 which concerns on Embodiment 3 shown by FIG. 4 to the intermediate header of the heat exchanger 8j of this Embodiment.

Embodiment 14 FIG.
The heat exchanger 8k according to the present embodiment will be described mainly with respect to differences from the configuration and operation of the heat exchanger 8 according to the sixth embodiment.

In the sixth embodiment, the first refrigerant path 101, the second refrigerant path 102, the first inlet of the configuration in which the refrigerant flow path through which the high-temperature refrigerant flows and the refrigerant flow path through which the low-temperature refrigerant flows are integrally formed. The case where the communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, the second outlet communication hole 106a, and the intermediate communication hole 131 are arranged in the vertical direction is shown. In the present embodiment, the first refrigerant path 101 and the second refrigerant path 102 are in the vertical direction, the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, the second outlet communication hole 106a, and A configuration in which the intermediate communication hole 131 is horizontally disposed will be described.

FIG. 17 is an external view of a heat exchanger 8k according to Embodiment 14 of the present invention. The intermediate communication hole 131 has a function of separating the condensed liquid high-temperature refrigerant out of the high-temperature refrigerant on the upstream side, and one end portion is opened to allow the liquid high-temperature refrigerant to flow out to the outside. Yes. Further, a trap member 31a in the heat exchanger 8 according to the eleventh embodiment shown in FIG.

With such a configuration, even when the heat exchanger is arranged vertically, liquid separation can be performed at the intermediate header, and the high-temperature refrigerant in the gas-liquid two-phase state is the first flat side on the downstream side as in the sixth embodiment. The amount of liquid high-temperature refrigerant flowing into the pipe 12 can be reduced, and the condensation performance and heat exchange performance can be improved.

In addition, you may apply the collision member 32 in the heat exchanger 8 which concerns on Embodiment 3 shown by FIG. 4 to the intermediate header of the heat exchanger 8k of this Embodiment.

1 1st flat tube, 2nd flat tube, 3rd first inlet header, 4th first outlet header, 5th 2nd inlet header, 6th 2nd outlet header, 8, 8a ~ 8e heat exchanger, 11 upstream first Flat tube, 12 downstream first flat tube, 21 downstream second flat tube, 22 upstream second flat tube, 31 intermediate header, 31 intermediate header, 32 impact member, 41 outflow tube, 42 bypass piping, 42a bypass flow path, 43 flow rate Adjustment means, 51, intermediate header, 101, first refrigerant path, 101a, first refrigerant flow path, 102, second refrigerant path, 102a, second refrigerant flow path, 103, first inlet connection pipe, 103a, first inlet communication hole, 104, first Outlet connection pipe, 104a, first outlet communication hole, 105, second inlet connection pipe, 105a, second inlet communication hole, 106, second outlet connection pipe, 106a, second outlet communication hole 110 main body, 131 intermediate communication hole, 200, 200a, 200b refrigeration cycle apparatus, 230 first compressor, 231 first radiator, 232 first decompressor, 233 first cooler, 240 second compressor, 241 second Radiator, 242 second decompressor, 250 compressor, 251 radiator, 252 decompressor, 253 cooler, 254 bypass decompressor, 255 bypass pipe, 256 injection port.

Claims

A first flow path portion configured by arranging a plurality of refrigerant flow paths through which a high-temperature refrigerant flows;
A second flow path portion configured by arranging a plurality of refrigerant flow paths through which a low-temperature refrigerant flows;
A cylindrical flow path is formed at one end of the first flow path portion in the flow direction of the high-temperature refrigerant and communicated with each of the refrigerant flow paths, and the high-temperature refrigerant is passed from the outside to the first flow path portion. A first inlet to be introduced,
A cylindrical flow path is formed at the other end of the first flow path portion in the flow direction of the high-temperature refrigerant, and communicates with each of the refrigerant flow paths. A first outlet portion for draining;
A cylindrical flow path is formed at one end of the second flow path portion in the flow direction of the low-temperature refrigerant and communicated with each of the refrigerant flow paths, and the low-temperature refrigerant is supplied from the outside to the second flow path portion. A second inlet to be introduced,
The second flow path portion is disposed at the other end in the flow direction of the low-temperature refrigerant to form a cylindrical flow path that communicates with each of the refrigerant flow paths, and the low-temperature refrigerant is discharged from the second flow path portion to the outside. A second outlet portion for draining;
An intermediate communication part that is disposed in the middle of the refrigerant flow path of the first flow path part and forms a cylindrical flow path that communicates with at least a part of the refrigerant flow path of the first flow path part;
With
Each refrigerant flow path of the first flow path section and each refrigerant flow path of the second flow path section are arranged so that the flow path directions are parallel and adjacent to each other via a partition wall,
The intermediate communication portion causes the high-temperature refrigerant liquefied in the upstream portion of the first flow path portion to flow downward.
The heat exchanger according to claim 1, wherein the plurality of refrigerant flow paths through which the high-temperature refrigerant flows and the plurality of refrigerant flow paths through which the low-temperature refrigerant flows are arranged in the vertical direction.
The intermediate communication portion has a lower end closed.
The first flow path portion is configured such that the lower surface of the downstream portion located on the opposite side via the intermediate communication portion is positioned below the lower surface of the upstream portion with respect to the intermediate communication portion,
The heat exchanger according to claim 2, further comprising a bypass channel that is a refrigerant channel formed in a lower portion of the downstream portion than a lower surface of the upstream portion.
The first outlet part and the intermediate communication part have a lower end part or a side part opened,
A pipe extending from the first outlet part or a side connected to the outside of the first outlet part and a lower end part or a side part of the intermediate communication part are connected, and the first outlet part and the intermediate communication part are connected. The heat exchanger according to claim 1, further comprising a bypass pipe that joins the high-temperature refrigerant that has flowed out of the refrigerant.
The heat exchanger according to any one of claims 1 to 4, wherein the first channel portion and the second channel portion are integrally formed.
The first inlet part and the first outlet part are formed as holes that are penetrated so as to communicate with each refrigerant flow path of the first flow path part,
The heat exchange according to claim 5, wherein the second inlet portion and the second outlet portion are formed as through holes so as to communicate with the respective refrigerant flow paths of the second flow path section. vessel.
The first flow path section and the second flow path section are formed as separate bodies, and are configured to be joined at a contact surface. The described heat exchanger.
The intermediate communication part is formed as a through-hole so as to communicate with at least a part of the refrigerant flow path of the first flow path part. The heat exchanger according to item.
Of the first inlet portion disposed at one end of the first flow path portion in the flow direction of the high-temperature refrigerant and the both ends of the second flow path portion in the flow direction of the low-temperature refrigerant, the one end The second inlet part or the second outlet part connected to the end on the same side as the part is arranged with a predetermined amount shifted in the flow direction of each refrigerant,
The other end of the first outlet portion disposed at the other end portion of the first flow path portion in the flow direction of the high-temperature refrigerant and the both ends of the second flow path portion in the flow direction of the low-temperature refrigerant. 9. The second inlet portion or the second outlet portion connected to an end portion on the same side as the portion is arranged so as to be shifted by a predetermined amount in the flow direction of each refrigerant. The heat exchanger as described in any one.
An upstream part and a downstream part of the first flow path part are arranged separately in the vertical direction,
In the upstream portion, one end in the flow direction of the high-temperature refrigerant is connected to the intermediate coupling portion, and the other end is connected to the first inlet portion.
8. The heat according to claim 7, wherein the downstream portion has one end in the flow direction of the high-temperature refrigerant connected to the intermediate coupling portion and the other end connected to the first outlet portion. Exchanger.
In plan view, the upstream communication portion and the downstream communication portion of the first flow channel section are arranged so that the refrigerant flow direction of the upstream flow portion and the refrigerant flow direction of the downstream flow portion are parallel to each other. Connected to the
The intermediate inlet and the second inlet or the second outlet connected to the end on the same side as the intermediate outlet of both ends of the second flow path in the flow direction of the low-temperature refrigerant Are shifted by a predetermined amount in the flow direction of each refrigerant,
Of the first inlet portion and the first outlet portion, and the second inlet portion connected to the opposite end of the intermediate communication portion among both ends of the second flow path portion in the flow direction of the low-temperature refrigerant. Alternatively, the heat exchanger according to claim 10, wherein the second outlet portion is arranged by being shifted by a predetermined amount in the flow direction of each refrigerant.
The intermediate communication portion includes a collision member that collides with a liquid phase portion in a flowing high-temperature refrigerant in a gas-liquid two-phase state and causes the liquid phase portion to flow downward. The heat exchanger according to any one of claims 11 to 11.
The heat according to any one of claims 1 to 12, wherein the intermediate communication portion has a cylindrical shape and is formed such that the high-temperature refrigerant flows in a tangential direction of the circular cross section. Exchanger.
The flow direction of the high-temperature refrigerant in the first flow path part and the flow direction of the low-temperature refrigerant in the second flow path part are configured to be opposed to each other in at least some of the refrigerant flow paths. The heat exchanger according to any one of claims 1 to 13.
A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 14.