JP2003302123A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To ensure a desired heat exchange quantity in both evaporation and condensation. <P>SOLUTION: In a heat exchanger having an inflow side heat transfer pipe group 2a to enable a refrigerant to flow into a chamber demarcated inside a first header 3 and a second header 4 and an outflow side heat transfer pipe group 2b to enable the refrigerant to flow out of the chamber, and allowing the refrigerant to pass from the inflow side heat transfer pipe group 2a to the outflow side heat transfer pipe group 2b via the chamber, the chamber is partitioned in such a manner as a connection part of the evaporation outflow side heat transfer pipe group 2a to enable the refrigerant to flow out at the evaporation is narrower than a connection part of the evaporation inflow side heat transfer pipe group 2b to enable the refrigerant to flow in at the evaporation, and a passage wall 11 having a throttling passage 11a is interposed at a position on the leeward side. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger, and more particularly, in an air conditioner that constitutes a refrigeration cycle, a multi-pass system in which an inflow heat transfer pipe and an outflow heat transfer pipe are connected using a header. The present invention relates to a heat exchanger constituted by

[0002]

2. Description of the Related Art Conventionally, an air conditioner which constitutes a refrigeration cycle uses a header for an inflow side heat transfer tube into which the refrigerant flows and an outflow side heat transfer tube to which the refrigerant flows out in order to suppress pressure loss of the refrigerant. It is common to use a multi-pass heat exchanger for connection. In the following, JP-A-4-268128
FIG. 4 shows the configuration of the multi-pass heat exchanger disclosed in the publication.
9 and FIG. 50.

FIG. 49 is a schematic sectional view of a conventional heat exchanger. This heat exchanger includes a large number of fins 1 and a plurality of sets of heat transfer tube groups 2. Many fins 1
It is a flat plate-shaped member arranged in parallel so as to be parallel to each other. The heat transfer tube group 2 is configured by arranging four heat transfer tubes in parallel, and is arranged so as to penetrate each of the fins 1. The first header 3 is connected to one end of each heat transfer tube group 2, while the second header is connected to the other end of each heat transfer tube group 2.
The header 4 is connected.

By disposing four partition plates 5 inside the first header 3, five chambers 3a, 3b, 3c,
3d and 3e are defined. Further, the first header 3 is formed with a first flow port 3f so as to communicate with the first chamber 3a which is the first chamber from the bottom of the drawing, and the fifth chamber 3 which is the first chamber from the top of the drawing.
The second circulation port 3g is formed so as to communicate with e.

By disposing three partition plates 6 inside the second header 4 so as to divide the internal volume thereof into substantially equal parts, four chambers 4a, 4b, 4c and 4d are defined. There is.

Between the first chamber 3a which is the first from the bottom of the first header 3 and the first chamber 4a which is the first from the bottom of the second header 4, and the first chamber which is the first from the bottom of the second header 4 The chamber 4a and the second chamber 3b, which is the second from the bottom of the first header 3, are communicated with each other by the heat transfer tube group 2. Similarly, the first header 3 and the second header 4 are connected to each other alternately by the heat transfer tube group 2 to form a path through which the refrigerant flows.

FIG. 50 is a vertical sectional view of the heat exchanger shown in FIG. 49 as seen from the second header 4 side. This heat exchanger is installed at an angle of about 45 degrees with respect to the gravity direction 7, and the air 8 is made to flow from an oblique 45 degree upward direction of the heat exchanger to an oblique 45 degree downward direction.

Next, the operation of the conventional heat exchanger will be described with reference to FIGS. 49 and 50. In addition, the solid line arrow in the figure shows the flow of the refrigerant at the time of evaporation, and the broken line arrow in the figure shows the flow of the refrigerant at the time of condensation.

The refrigerant flowing from the first flow port 3f during evaporation is transferred to the first header 3 from the first header 3 to the second header 4 and from the second header 4 to the first header 3 in sequence. It finally flows out from the second distribution port 3g via the second header 4 and the second header 4 alternately. In this way, the first distribution port 3f
The refrigerant flowing in from the heat transfer tube group 2 while flowing out from the second circulation port 3g through the first header 3 and the second header 4.
The heat exchange with the air 8 is performed via the plurality of fins 1 which penetrates.

On the other hand, during condensation, the refrigerant flows in the direction opposite to that during evaporation. That is, the refrigerant that has flowed in through the second circulation port 3 g is transferred from the first header 3 to the second header 4 to the second header 3.
The first header 3 and the second header 4 are alternately passed through so as to sequentially move from the header 4 to the first header 3, and finally the first outlet 3f flows out. In this way, the refrigerant flowing from the second circulation port 3g is supplied to the first header 3 and the second header 4
Heat is exchanged with the air 8 via the plurality of fins 1 penetrating the heat transfer tube group 2 while flowing out from the first circulation port 3f via the.

FIG. 51 is a schematic sectional view showing the distribution of the refrigerant gas 9 and the refrigerant liquid 10 passing through the second header 4 during evaporation, and FIG. 52 is the refrigerant gas 9 passing through the header 4 during condensation. 3 is a schematic cross-sectional view showing the distribution with the refrigerant liquid 10. FIG.
The state of the refrigerant will be described below with reference to FIGS. 51 and 52.

First, the state of the refrigerant during evaporation will be described. The dryness described below is X = W _g / (W _g +
W _l ). Here, X is the dryness, W _g is the mass flow rate [kg / h] of the refrigerant gas 9, and W ₁ is the mass flow rate [kg / h] of the refrigerant liquid 10.

The refrigerant flowing from the first flow port 3f at the time of evaporation is in a state in which the refrigerant gas 9 and the refrigerant liquid 10 having a dryness of about 0.2 are mixed. As shown by the solid arrows in FIGS. 49 and 51, the refrigerant flowing into the first header 3 is transferred to the heat transfer tube group 2
And heat is exchanged with the air 8 through the fins 1 while passing through the heat transfer tube group 2 to gradually evaporate, so that the dryness gradually increases. During this time, the air 8 passing through the fin 1 is
Since heat is absorbed by the heat transfer tube group 2, the temperature decreases as going from the windward to the leeward.

As a result, the temperature difference between the heat transfer tube group 2 and the air 8 is the largest on the windward side, and the amount of heat exchange is large on the windward side. After that, the refrigerant passing through the heat transfer tube group 2 becomes the second
It flows into the next heat transfer tube group 2 through the header 4, and while passing through the heat transfer tube group 2, heat is exchanged with the air 8 to be evaporated.
Thereafter, the first header 3 and the second header 4 are alternately passed, and finally the second header 3 flows out of the second distribution port 3g.

At the time of evaporation described above, since the amount of heat exchange on the windward side is large, it is necessary to flow more refrigerant liquid on the windward side, but as shown in FIG. 51, the heat exchanger is tilted at 45 degrees. Since the refrigerant liquid 10 is easily installed in the leeward side under the influence of gravity, the refrigerant liquid 10 flowing into the heat transfer tube group 2 located on the leeward side increases, while the refrigerant liquid 10 is located on the leeward side. Refrigerant liquid 10 flowing in
Will tend to decrease.

Next, the state of the refrigerant at the time of condensation will be described. The refrigerant flowing from the second circulation port 3g at the time of condensation is in the state of only the refrigerant gas 9 having a dryness of 1.0. As shown by the dashed arrows in FIGS. 49 and 52, the refrigerant flowing into the first header 3 flows into the heat transfer tube group 2, and while passing through the heat transfer tube group 2, the refrigerant flows to the air 8 via the fins 1. Since the heat is exchanged and the heat gradually condenses, the dryness gradually decreases. During this time, the air 8 passing through the fins 1 absorbs heat from the heat transfer tube group 2, so that the temperature rises as going from the windward side to the leeward side.

As a result, the temperature difference between the heat transfer tube group 2 and the air 8 becomes the largest on the windward side, and the amount of heat exchange becomes large on the windward side. After that, the refrigerant passing through the heat transfer tube group 2 becomes the second
It flows into the next heat transfer tube group 2 via the header 4, and while passing through the heat transfer tube group 2, heat is exchanged with the air 8 to be condensed.
After that, the first header 3 and the second header 4 are alternately passed, and finally the first header 3 flows out of the first distribution port 3f.

At the time of condensation described above, since the heat exchange amount on the windward side is large, it is necessary to flow the refrigerant gas on the windward side. However, as shown in FIG. 52, the heat exchanger is installed at an angle of 45 degrees. Is affected by gravity, so the refrigerant liquid 1
0 easily accumulates on the leeward side, the inlet of the heat transfer tube group 2 located on the leeward side is blocked by the refrigerant liquid 10, and the refrigerant gas 9 flowing into the leeward side is
On the other hand, the refrigerant gas 9 that flows into the windward side tends to increase.

[0019]

As described above, in the above-mentioned conventional heat exchanger, when the heat exchanger is tilted with respect to the gravity direction 7, the refrigerant liquid 10 is below the headers 3 and 4 due to the influence of gravity. It is biased toward the side and tends to accumulate. As a result, it becomes difficult to secure a desired heat exchange amount in the heat exchanger during both evaporation and condensation.

For example, the heat exchanger is installed with an inclination of 45 degrees with respect to the gravity direction 7, and the air 8 is rotated 45 degrees from the upper side by 45 degrees.
When flowing downward, the refrigerant gas 9 is located on the windward side of the heat transfer tube group 2, but the refrigerant gas 9 is increased, so that the heat exchange amount at the time of condensation can be increased. However, since the amount of the refrigerant liquid 10 decreases, the amount of heat exchange during evaporation must be small.

Further, the heat exchanger is set to 45 with respect to the gravity direction 7.
When the air 8 is installed at an angle of 45 degrees and flowed from 45 degrees downward to 45 degrees upward, the amount of the refrigerant liquid 10 that is located on the windward side in the heat transfer tube group 2 increases, so the heat exchange amount at the time of evaporation Can be increased, but the amount of refrigerant gas 9 located on the windward side is reduced, so the amount of heat exchange at the time of condensation must be reduced.

In view of the above situation, it is an object of the present invention to obtain a heat exchanger capable of ensuring a desired heat exchange amount both during evaporation and condensation even in the case of an inclined arrangement. To do.

[0023]

In order to achieve the above object, a heat exchanger according to the present invention has a group of inflow side heat transfer tubes for introducing a refrigerant into a chamber defined inside a header, and a refrigerant from the chamber. An outflow-side heat transfer tube group for causing the refrigerant to flow out from the inflow-side heat transfer tube group through the chamber to the outflow-side heat transfer tube group. A throttle passage is provided between a connecting portion of the heat pipe group and a connecting portion of the outflow-side heat transfer pipe group.

According to the present invention, the speed of the refrigerant can be increased when passing through the throttle passage.

In the heat exchanger according to the next invention, in the above invention, a passage having a throttle passage between the connecting portion of the inflow side heat transfer tube group and the connecting portion of the outflow side heat transfer tube group in the chamber. It is characterized by interposing a wall.

According to the present invention, the throttle passage can be constructed by interposing the passage wall inside the chamber.

A heat exchanger according to the next invention is characterized in that, in the above invention, the opening area of the throttle passage is increased as the dryness of the refrigerant passing therethrough increases.

According to the present invention, the refrigerant having a high degree of dryness passes through the throttle passage having a large opening area.

In the heat exchanger according to the next invention, in the above invention, the vaporization inflow heat transfer tube in which the refrigerant flows in at the connecting portion of the vaporization outflow side heat transfer tube group in which the refrigerant flows out in the chamber during evaporation The chamber is partitioned in a manner narrower than the connecting portion of the group, and the throttle passage is provided at a position on the leeward side.

According to the present invention, the refrigerant liquid that has moved to the leeward side at the connecting portion of the evaporating outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the upwind side in a narrow space regardless of the influence of gravity.

In the heat exchanger according to the next invention, in the above invention, the inflow side heat transfer tube at the time of condensation in which the refrigerant flows at the time of condensation at the connecting portion of the group of heat transfer tube side at the time of condensation in which the refrigerant flows out at the time of condensation in the chamber. The chamber is partitioned in such a manner as to be narrower than the connecting portion of the group, and the throttle passage is provided at a position on the windward side.

According to the present invention, the refrigerant liquid that has moved to the upwind side in the connecting portion of the condensation side outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the downwind side regardless of the influence of gravity in a narrow space.

In the heat exchanger according to the next invention, in the above invention, the chamber is partitioned and vaporized by narrowing each connecting portion of the inflow side heat transfer tube group and the outflow side heat transfer tube group in the chamber. At the time of evaporation, the refrigerant flows out at the time of evaporation.At the time of evaporation, a narrowing passage is provided on the leeward side to reach the connecting part of the heat transfer tube group on the evaporation side.At the time of condensation, the refrigerant flows out at the time of condensation. The throttle passage is configured by providing the throttle passage on the windward side.

According to the present invention, the refrigerant liquid that has moved to the upwind side at the connection portion of the evaporating outflow side heat transfer tube group in the chamber becomes difficult to move to the downwind side regardless of the influence of gravity in a narrow space. The refrigerant liquid that has moved to the leeward side in the connection portion of the condensing outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the upwind side in a narrow space regardless of the influence of gravity.

In the heat exchanger according to the next invention, in the above invention, the opening area of the inflow throttle passage into which the refrigerant flowing against gravity is introduced is set larger than the opening area of the inflow throttle passage from which the refrigerant flows. It is characterized by having done.

According to the present invention, since the opening area of the inflow throttle passage into which the refrigerant flowing against gravity flows is increased, the pressure loss of the refrigerant passing through the inflow throttle passage is reduced.

A heat exchanger according to the next invention is characterized in that, in the above-mentioned invention, the throttle passage is constituted by using a pipe.

According to the present invention, the throttle passage can be constituted by the pipe.

[0039]

BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of a heat exchanger according to the present invention will be described below with reference to the accompanying drawings.

Embodiment 1. 1 is a sectional view showing a configuration of a heat exchanger according to a first embodiment of the present invention, and FIG. 2 is a sectional side view of the heat exchanger shown in FIG. The state of the refrigerant at time is shown. FIG. 3 is a cross-sectional view of the heat exchanger shown in FIG. 1 viewed from one header side, showing a state of the refrigerant at the time of condensation. In addition, as shown in FIG. 2 and FIG.
Then, it is assumed that the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7 and that the air flows from 45 degrees above the heat exchanger to 45 degrees downward. First, the structure of the heat exchanger will be described with reference to FIGS. 1 to 3.

The heat exchanger illustrated here is composed of a large number of fins 1 and a plurality of groups (8 groups in the first embodiment) of heat transfer tube groups 2. The large number of fins 1 are flat plate-shaped members arranged in parallel so as to be parallel to each other. Heat transfer tube group 2
Are each composed of a plurality of heat transfer tubes, in the first embodiment, four heat transfer tubes arranged side by side, and are arranged so as to penetrate each of the fins 1. A first header 3 is connected to one end of each heat transfer tube group 2, and a second header 4 is connected to the other end of each heat transfer tube group 2.

By disposing four partition plates 5 inside the first header 3, five chambers 3a, 3b, 3c,
While defining 3d and 3e, three partition plates 6 are provided inside the second header 4 so as to divide the internal volume into substantially equal parts.
By disposing the four chambers 4a, 4b, 4c, 4
The d is defined. The chambers 3a, 3 of these first headers 3
b, 3c, 3d, 3e and the chambers 4a, 4 of the second header 4
b, 4c and 4d are for partitioning the headers 3 and 4 so that a plurality of sets of heat transfer tube groups 2 are alternately connected like a series of passages.

For the sake of convenience, in the first header 3, the first chamber 3a, the second chamber 3b, the third chamber 3c, and the fourth chamber 3 are arranged in this order from the lower side.
d, the fifth chamber 3e, and in the second header 4, the first chamber 4a, the second chamber 4b, the third chamber 4c, and the fourth chamber 4 are sequentially arranged from the lower side.
If referred to as d, between the first chamber 3a of the first header 3 and the first chamber 4a of the second header 4, between the first chamber 4a of the second header 4 and the second chamber 3b of the first header 3 Between the second chamber 3b of the first header 3 and the second chamber 4b of the second header 4, the second header 4
Between the second chamber 4b of the first header 3 and the third chamber 3c of the first header 3,
Between the third chamber 3c of the header 3 and the third chamber 4c of the second header 4, between the third chamber 4c of the second header 4 and the fourth chamber 3d of the first header 3, and between the third chamber 4c of the first header 3 4 chambers 3d and second header 4
Between the fourth chamber 4d of the second header 4 and the first chamber 4d of the second header 4
The header 3 and the fifth chamber 3e are connected by the heat transfer tube group 2, respectively. Therefore, in the above heat exchanger, the first
The first chamber 3a of the header 3, the first chamber 4a of the second header 4, the second chamber 3b of the first header 3, the second chamber 4b of the second header 4,
The third chamber 3c of the first header 3 and the third chamber 4 of the second header 4
c, the fourth chamber 3d of the first header 3, the fourth chamber 4d of the second header 4, and the fifth chamber 3e of the first header 3 are connected in this order to form a path.

The first header 3 is formed with a first flow port 3f so as to communicate with the first chamber 3a, while the fifth
The second circulation port 3g is formed so as to communicate with the chamber 3e. The first circulation port 3f functions as an inflow port through which the refrigerant flows into the first header 3 during evaporation, and functions as an outflow port through which the refrigerant flows out from the first header 3 during condensation. On the contrary, the second circulation port 3g functions as an outflow port for flowing out the refrigerant from the first header 3 at the time of evaporation, and at the same time as an inflow port for inflowing the refrigerant to the first header 3 at the time of condensation.

Here, considering the second header 4 as a reference, the plurality of heat transfer tube groups 2 described above are the second heat transfer tube group at the time of evaporation.
A first heat transfer tube group 2a that functions as an evaporative outflow side heat transfer tube group that allows the refrigerant to flow out from the header 4, and a second heat transfer tube group that functions as an evaporative inflow side heat transfer tube group that causes the refrigerant to flow into the second header 4.
The heat transfer tube group 2b can be classified. On the contrary, focusing on the first header 3, the first heat transfer tube group 2a
Functions as an evaporative inflow side heat transfer tube group that causes the refrigerant to flow into the first header 3, while the second heat transfer tube group 2b functions as an evaporative outflow side heat transfer tube group that causes the refrigerant to flow out from the first header 3. Become.

On the other hand, in the heat exchanger, the second chamber 3b, the third chamber 3c, the fourth chamber 3d of the first header 3 and the first chamber 4a, the second chamber 4b and the third chamber of the second header 4 are provided. Chamber 4c, 4th chamber 4
A passage wall 11 is provided in each d. The passage wall 11 is
It is a plate-shaped member having a throttle passage 11a in the center thereof, and each of the chambers 3b, 3c, 3d, 4a, 4b, 4c, 4d is connected to the first heat transfer tube group 2a and the second heat transfer tube group 2b. Partition plate 5 so as to partition the part connected to
Alternatively, they are arranged in parallel with the partition plate 6.

Next, the operation of the heat exchanger according to the first embodiment will be described. First, at the time of evaporation, the refrigerant flows into the first header 3 from the first circulation port 3f. The inflowing refrigerant is in a state in which the refrigerant gas 9 and the refrigerant liquid 10 having a dryness of about 0.2 are mixed.

As shown by the solid arrows in FIGS. 1 and 2,
The refrigerant flowing into the first header 3 flows into the first chamber 3a, and then flows into the first chamber 4a of the second header 4 through the second heat transfer tube group 2b. During this time, the refrigerant passing through the second heat transfer tube group 2b exchanges heat with the air 8 via the fins 1 to evaporate, and the dryness gradually increases. Air 8
Heat is absorbed by the second heat transfer tube group 2b while passing through the fins 1, so that the temperature thereof decreases as going from the windward side to the leeward side. Therefore, the temperature difference between the second heat transfer tube group 2b and the air 8 is the largest on the windward side, and the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the throttle passage 11a, it will flow out from the first heat transfer tube group 2a. Here, according to the heat exchanger,
Since the velocity of the refrigerant increases when passing through the throttle passage 11a, the refrigerant liquid 10 after passing through the throttle passage 11a collides with the partition plate 6. As a result, as clearly shown in FIG. 2, the refrigerant liquid 10 spreads along the partition plate 6 regardless of the influence of gravity, and the first heat transfer tube group 2a easily flows out uniformly.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 via the fins 1 while passing through the first heat transfer tube group 2a to evaporate, and the second chamber 3b of the first header 3 is evaporated.
Leading to. Thereafter, similarly, the refrigerant passes through the throttle passage 11a, the second heat transfer tube group 2b, the second header 4, the throttle passage 11a, the first heat transfer tube group 2a, the first header 3, and finally the second header of the first header 3. It flows out from the distribution port 3g. Between these,
The speed of the refrigerant increases when passing through the throttle passage 11a of the passage wall 11, and the refrigerant liquid 1 after passing through the throttle passage 11a
Since 0 collides with the partition plate 5 or the partition plate 6, the refrigerant liquid 10 spreads along the partition plates 5 and 6 regardless of the influence of gravity, and from each of the first heat transfer tube group 2a. It becomes easy to flow out uniformly, and it becomes easy to flow out uniformly from each of the second heat transfer tube groups 2b.

Next, the action at the time of condensation will be described.
Here, considering the second header 4 as a reference, the first heat transfer tube group 2 a functions as a condensing inflow side path for allowing the refrigerant to flow into the second header 4 at the time of condensation, while the second heat transfer tube group 2
b functions as a condensing outflow side path that causes the refrigerant to flow out from the second header 4. Conversely, focusing on the first header 3,
While the first heat transfer tube group 2a functions as an outflow path at the time of condensation for allowing the refrigerant to flow out from the first header 3 at the time of condensation,
The second heat transfer tube group 2b functions as a condensing inflow side path that causes the refrigerant to flow into the first header 3.

At the time of condensation, the refrigerant first flows into the first header 3 from the second circulation port 3g. The inflowing refrigerant is in a state of only refrigerant gas having a dryness of 1.0.

As indicated by broken line arrows in FIGS. 1 and 3,
The refrigerant flowing into the first header 3 flows into the fifth chamber 3e, and then flows into the fourth chamber 4d of the second header 4 through the first heat transfer tube group 2a. During this time, the refrigerant passing through the first heat transfer tube group 2a exchanges heat with the air 8 through the fins 1 and is condensed, so that the dryness is gradually reduced. Air 8
Absorbs heat from the first heat transfer tube group 2a while passing through the fins 1, so that the temperature thereof increases as going from the windward side to the leeward side. Therefore, the temperature difference between the first heat transfer tube group 2a and the air 8 is the largest on the windward side, and the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the throttle passage 11a, it will flow out from the second heat transfer tube group 2b. Here, according to the heat exchanger,
Since the velocity of the refrigerant increases when passing through the throttle passage 11a, the refrigerant liquid 10 after passing through the throttle passage 11a collides with the partition plate 6. As a result, the refrigerant liquid 10
Will spread along the partition plate 6 regardless of the influence of gravity, and will easily flow out uniformly from each of the second heat transfer tube groups 2b. As a result, the proportion of the second heat transfer tube group 2b blocked by the refrigerant liquid 10 in each opening cross section becomes substantially equal, and the refrigerant gas 9 easily flows out uniformly from each of the second heat transfer tube group 2b.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 through the fins 1 while passing through the second heat transfer tube group 2b and is condensed, and the fourth chamber 3d of the first header 3 is condensed.
Leading to. Thereafter, similarly, the refrigerant passes through the throttle passage 11a, the first heat transfer tube group 2a, the second header 4, the throttle passage 11a, the second heat transfer tube group 2b, the first header 3, and finally the first header 3 of the first header 3. It flows out from the distribution port 3f. Between these,
The speed of the refrigerant increases when passing through the throttle passage 11a of the passage wall 11, and the refrigerant liquid 1 after passing through the throttle passage 11a
Since 0 collides with the partition plate 5 or the partition plate 6, the refrigerant liquid 10 spreads along the partition plates 5 and 6 regardless of the influence of gravity, and from each of the first heat transfer tube group 2a. It becomes easy to flow out uniformly, and it becomes easy to flow out uniformly from each of the second heat transfer tube groups 2b.

As described above, in the above heat exchanger, the refrigerant gas 9 is provided by providing the throttle passage 11a in the headers 3 and 4.
And the refrigerant liquid 10 can be evenly distributed to each of the heat transfer tube groups 2a and 2b. Therefore, during evaporation, the refrigerant liquid 10 can be secured in the first heat transfer tube group 2a on the windward side, and during condensation, the refrigerant gas 9 can be secured in the second heat transfer tube group 2b on the windward side. it can. That is, according to the heat exchanger,
Even when they are arranged at a certain angle, it is possible to secure a desired heat exchange amount both during evaporation and condensation without being affected by gravity.

41 and 42 show the first heat transfer tube group 2a and the second heat transfer tube group in the heat exchanger described above and the conventional heat exchanger.
It is a graph which shows the result of having verified the distribution ratio of the refrigerant liquid 10 to each of the heat transfer tube groups 2b by experiment. Figure 41
Is the first when the refrigerant flows from the lower side to the upper side with respect to the heat exchanger of the first embodiment and the conventional heat exchanger inclined at 45 degrees.
FIG. 42 shows the distribution ratio of the refrigerant liquid 10 to the heat transfer tube group 2a, and FIG. 42 shows a case where the refrigerant flows from the upper side to the lower side with respect to the heat exchanger of the first embodiment and the conventional heat exchanger inclined at 45 degrees. The distribution ratio of the refrigerant liquid 10 to the second heat transfer tube group 2b is shown.

The dimensions of the heat exchanger used in the experiment are as shown in FIGS. 39 and 40. 39 and 40, both show the chamber defined by the two partition plates 6 in the second header 4, for example, the second chamber 4b. The chamber measures 22.3 mm in width and 1 in height.
The thickness is 4.3 mm and the dimension in the thickness direction is 1.4 mm. The first heat transfer tube group 2a and the second heat transfer tube group 2b each include four heat transfer tubes arranged at a pitch of 6 mm. Furthermore, the distance between the first heat transfer tube group 2a and the second heat transfer tube group 2b is 10 mm. For the sake of convenience, the first heat transfer tube group 2a will be referred to as a, a, a, a in order from the one located above, and the second heat transfer tube group 2b will be located in order from the one located above.
Called b, b, b, b.

Further, in the heat exchanger according to the first embodiment shown in FIG. 40, a plate is provided between the portion connected to the first heat transfer tube group 2a and the portion connected to the second heat transfer tube group 2b in the chamber 4b. A passage wall 11 having a thickness of 4 mm is interposed. This passage wall 11
Is formed with a throttle passage 11a having a width of 1.7 mm and a length of 4 mm at the center thereof.

In the experiment, a refrigerant having a dryness of 0.4 was flowed at a flow rate of 6 kg / h, and the ratio of the refrigerant liquid 10 flowing through each heat transfer tube of the first heat transfer tube group 2a and the second heat transfer tube group 2b was measured. did. 41 and 42, the horizontal axis represents the number of the heat transfer tube described above, and the vertical axis represents the flow rate ratio of the refrigerant liquid flowing into the heat transfer tube.

When the refrigerant flows from the bottom to the top (during evaporation) as shown by the solid arrow in FIGS. 39 and 40, according to the heat exchanger of the first embodiment, as shown in FIG. Compared with the conventional heat exchanger, the heat transfer tube a in the direction opposite to the gravity direction 7
The proportion of the refrigerant liquid 10 flowing into the heat transfer tube a increases in the same direction as the gravity direction 7, while the proportion of the refrigerant liquid 10 flowing into the heat transfer tube a in the same direction as the gravity direction 7 decreases. It can be seen that the heat pipes a, a, a, a are evenly distributed.

When the refrigerant flows from top to bottom (during condensation) as shown by the broken line arrows in FIGS. 39 and 40, the heat exchanger according to the first embodiment is used as shown in FIG. If
It can be seen that the refrigerant liquid 10 flowing into the second heat transfer tube group 2b is evenly distributed as compared with the conventional heat exchanger. That is, the heat transfer tubes b, b, b, of the second heat transfer tube group 2b
It can be seen that the refrigerant gas 9 flowing into b is easily distributed evenly.

As a result, the heat exchanger is installed in a state of being inclined at 45 degrees with respect to the gravity direction 7, and the air 8 is supplied to the heat exchanger at 45 degrees.
When the refrigerant flows from the lower side to the upper side at the time of evaporation, and when the refrigerant flows from the upper side to the lower side at the time of condensation, it flows upward in the first heat transfer tube group 2a at the time of evaporation. The amount of the refrigerant liquid 10 flowing out to the positioned one is sufficient, and the amount of the refrigerant gas 9 flowing out to the one positioned on the windward side in the second heat transfer tube group 2b at the time of condensation is sufficient, so that at the time of evaporation. It is possible to secure a desired heat exchange amount both at the time of condensation and at the time of condensation.

In the first embodiment described above, the heat exchanger is installed at an angle of 45 degrees, the air 8 is made to flow from 45 degrees upward to 45 degrees downward, and the refrigerant is evaporated from the bottom side to the top side during evaporation. In addition, while the refrigerant is made to flow from the upper side to the lower side at the time of condensation, the installation angle of the heat exchanger and the direction of air flow, and the direction of flowing the refrigerant at the time of evaporation and condensation are arbitrary, and in any of the embodiments, It is possible to obtain the same effect as that of 1.

Further, in the above-described first embodiment, the passage walls 11 having the throttle passages 11a are arranged inside the headers 3 and 4 so that the headers 3 and 4 are provided with the throttle passages 11a. Therefore, it is not necessary to process the headers 3 and 4, and there is no fear of complicating the manufacturing work of the headers 3 and 4. However, for example, by forming the inner wall surface of the header into a projection shape, the throttle passage is formed. It is also possible to form the throttle passage by narrowing the wall surface of the header.

Furthermore, in the first embodiment described above, the first
Only the throttle passage 11a is formed in the central portion of each chamber defined by the header 3 and the second header 4, but the number and shape of the throttle passage, the mounting angle, the position, and the size are arbitrarily determined. be able to. In addition, the heat transfer tube group 2a,
The number, thickness, and shape of 2b can be arbitrarily determined.

For example, as shown in FIGS. 4 and 5, the heat transfer tube groups 2a and 2b may be formed as a plurality of microchannels in a flat tube or an elliptical tube. 4 shows the case where the microchannel is circular, and FIG. 5 shows the case where the microchannel is quadrangular, but the shape, size, and number can be arbitrarily selected.

Although the first header 3 and the second header 4 are provided in the first embodiment described above, the hairpin 2c is provided instead of the second header 4 as shown in FIG. 6, and only the first header 3 is provided. May be configured. Further, it is not limited to the hairpin, and it can be arbitrarily selected as long as it can connect the first heat transfer tube group 2a and the second heat transfer tube group 2b.

Embodiment 2. FIG. 7 is a sectional view showing the structure of the heat exchanger according to the second embodiment of the present invention. The heat exchanger illustrated here has the same configuration as the heat exchanger of the first embodiment described above, and only the configuration of the throttle passage is different. That is, in the second embodiment, the throttle passage is configured such that the opening area increases as the dryness of the passing refrigerant increases.

More specifically, the dryness of the refrigerant passing through both during evaporation and condensation is such that the dryness of the first chamber is the first chamber 4a of the second header, the second chamber 3b of the first header, and the second chamber 4 of the second header.
b, the third chamber 3c of the first header, the third chamber 4 of the second header
c, the fourth chamber 3d of the first header, the fourth chamber 4d of the second header
It becomes large in order. Therefore, each room 4a, 3b, 4b,
Throttle passages 11a1, 1 provided in 3c, 4c, 3d, 4d
1a2, 11a3, 11a4, 11a5, 11a6, 1
The opening area of 1a7 is also set to increase according to this order. Throttle passages 11a1 and 11a
2, 11a3, 11a4, 11a5, 11a6, 11a
As in the first embodiment, as a method of providing 7, the throttle passages 11a1, 11a2, 11a3, 11a4, 11a.
The passage wall 11 having 5, 11a6, 11a7 is provided in each chamber 4
It may be arranged at a, 3b, 4b, 3c, 4c, 3d and 4d.

Since the other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof will be omitted. Further, the installation angle of the heat exchanger, the flowing direction of the air 8, and the flowing direction of the refrigerant during evaporation and condensation are the same as those in the first embodiment.

Also in the heat exchanger constructed as described above, the chambers 4a, 3b, 4b, 3 of the headers 3, 4 are respectively formed.
throttle passages 11a1, 11a2 in c, 4c, 3d, 4d
Since 11a3, 11a4, 11a5, 11a6, 11a7 are provided, the throttle passages 11a1, 11a
a2, 11a3, 11a4, 11a5, 11a6, 11
When passing through a7, the speed of the refrigerant increases, and the refrigerant liquid 10 after passing through collides with the partition plate 5 or the partition plate 6. Therefore, the refrigerant liquid 10 spreads along the partition plates 5 and 6 regardless of the influence of gravity, becomes easy to flow out from each of the first heat transfer tube group 2a, and is evenly distributed from each of the second heat transfer tube group 2b. It becomes easy to leak to.
As a result, during evaporation, the refrigerant liquid 10 can be secured in the first heat transfer tube group 2a that is located on the upwind side, and during condensation, the refrigerant gas 9 can be secured in the second heat transfer tube group 2b that is located on the upwind side. You can That is, according to the heat exchanger, it is possible to secure a desired heat exchange amount both during evaporation and condensation without being affected by gravity even when the heat exchanger is arranged at an angle of 45 degrees. Becomes

Moreover, according to the second embodiment, the throttle passages 11a1 and 11a1 are increased as the dryness of the refrigerant increases.
a2, 11a3, 11a4, 11a5, 11a6, 11
The opening area of a7 is enlarged. Therefore, in the region where the dryness of the refrigerant is large, that is, the region where the proportion of the refrigerant gas 9 is large, the throttle passages 11a1, 11a2, 11a are formed.
The flow velocity of the refrigerant passing through 3, 11a4, 11a5, 11a6, 11a7 can be reduced, and the pressure loss can be reduced during both evaporation and condensation.

In the second embodiment described above, the heat exchanger is installed at an angle of 45 degrees, the air 8 is made to flow from 45 degrees upward to 45 degrees downward, and the refrigerant is evaporated from the bottom side to the top side during evaporation. In addition, while the refrigerant is made to flow from the upper side to the lower side at the time of condensation, the installation angle of the heat exchanger and the direction of air flow, and the direction of flowing the refrigerant at the time of evaporation and condensation are arbitrary, and in any of the embodiments, It is possible to achieve the same effect as in 2.

Further, in the second embodiment described above, the throttle passages 11a1, 11a2, 11a are provided inside the headers 3, 4.
By disposing the passage wall 11 having 3, 11a4, 11a5, 11a6, 11a7, the throttle passages 11a1, 11a2, 11a3, 11a4, 11 are provided in the headers 3, 4.
Since the a5, 11a6, and 11a7 are provided, it is not necessary to process the headers 3 and 4, and there is no fear of complicating the manufacturing work of the headers 3 and 4. For example, the inner wall surface of the header is projected. The narrowed passage may be formed by forming the shape, or the narrowed passage may be formed by narrowing the wall surface of the header.

Further, in the above-described second embodiment, the first
The throttle passages 11a1, 11a2, 11a3, 11a are formed in the central portions of the respective chambers defined by the header 3 and the second header 4.
Although only 4, 11a5, 11a6, 11a7 are formed, if the condition that the opening area increases as the dryness of the passing refrigerant increases, the number and shape of the throttle passages, the mounting angle, the position, The size can be arbitrarily determined. Further, the number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined.

For example, as shown in FIGS. 4 and 5, the heat transfer tube groups 2a and 2b may be formed as a plurality of microchannels in a flat tube or an elliptical tube. 4 shows the case where the microchannel is circular, and FIG. 5 shows the case where the microchannel is quadrangular, but the shape, size, and number can be arbitrarily selected.

Although the first header 3 and the second header 4 are provided in the second embodiment described above, the hairpin 2c is provided instead of the second header as shown in FIG. 8, and the first header 3 is provided.
Only the configuration may be used. Further, it is not limited to the hairpin, and it can be arbitrarily selected as long as it can connect the first heat transfer tube group 2a and the second heat transfer tube group 2b.

Third Embodiment 9 is a sectional view showing the structure of a heat exchanger according to a third embodiment of the present invention, and FIG.
FIG. 11 is a cross-sectional side view of the heat exchanger shown in FIG. 9 viewed from one header side, showing a state of the refrigerant at the time of evaporation.
FIG. 11 is a cross-sectional side view of the heat exchanger shown in FIG. 9 viewed from one header side, and shows a state of the refrigerant at the time of condensation.

The heat exchanger illustrated here has the same structure as the heat exchanger of the first embodiment described above, and only the internal structure of the header is different. That is, in the third embodiment, the portion of the header that is connected to the evaporation-time outflow side heat transfer tube group that allows the refrigerant to flow out during evaporation is more than the portion that is connected to the evaporation-time inflow side heat transfer tube group that allows the refrigerant to flow during evaporation. The room is partitioned so as to be narrow, and a throttle passage is provided at a position on the leeward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the second heat transfer tube group 2b, which is the evaporative outflow side heat transfer tube group, is narrower than the portion connected to the first heat transfer tube group 2a, which is the evaporative inflow side heat transfer tube group. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the first heat transfer tube group 2a, which is the heat transfer tube group on the outflow side at the time of evaporation, is evaporated. The passage wall 11 is arranged so as to be narrower than the portion connected to the second heat transfer tube group 2b which serves as the time inflow side heat transfer tube group. Each passage wall 11 is provided with a unique throttle passage 11a at the leeward side of the air 8.

Since the other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof will be omitted. Further, the installation angle of the heat exchanger, the flowing direction of the air 8, and the flowing direction of the refrigerant during evaporation and condensation are the same as those in the first embodiment.

Next, the operation of the heat exchanger according to the third embodiment will be described. First, at the time of evaporation, the refrigerant flows into the first header 3 from the first circulation port 3f. The refrigerant flowing in is a state in which the refrigerant gas 9 and the refrigerant liquid 10 having a dryness of about 0.2 are mixed.

As shown by the solid arrows in FIGS. 9 and 10, the refrigerant flowing into the first header 3 flows into the first chamber 3a, and then the second header 4 through the second heat transfer tube group 2b.
Flows into the first chamber 4a. During this time, the refrigerant passing through the second heat transfer tube group 2b exchanges heat with the air 8 via the fins 1 to evaporate, and the dryness gradually increases. Air 8
Heat is absorbed by the second heat transfer tube group 2b while passing through the fins 1, so that the temperature thereof decreases as going from the windward side to the leeward side. Therefore, the temperature difference between the second heat transfer tube group 2b and the air 8 is the largest on the windward side, and the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the throttle passage 11a, it will flow out from the first heat transfer tube group 2a. Here, according to the heat exchanger,
Since the speed of the refrigerant increases when passing through the throttle passage 11a, the refrigerant liquid 10 that has passed through the throttle passage 11a is separated by the partition plate 6
And then move to the windward side of the air 8. Refrigerant liquid 10 that has moved further to the windward side passes through passage wall 11
Since the space defined by the partition plate 6 and the partition plate 6 is narrow, it is difficult to move to the leeward side regardless of the influence of gravity, and most of it flows out from the one located on the windward side in the first heat transfer tube group 2a. become.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 via the fins 1 while passing through the first heat transfer tube group 2a to evaporate, and the second chamber 3b of the first header 3 is evaporated.
Leading to. After that, it passes through the throttle passage 11a and flows out from the second heat transfer tube group 2b. Here, according to the heat exchanger, since the speed of the refrigerant increases when passing through the throttle passage 11a, the refrigerant liquid 10 that has passed through the throttle passage 11a.
Collides with the partition plate 5, and then moves to the windward side of the air 8. Refrigerant liquid 10 that has moved further to the windward side
Has a narrow space defined by the passage wall 11 and the partition plate 5, so that it is difficult to move to the leeward side regardless of the influence of gravity, and most of them are located on the windward side in the second heat transfer tube group 2b. It comes to flow from things.

Thereafter, similarly, the refrigerant passes through the second header 4, the throttle passage 11a, the first heat transfer tube group 2a, the first header 3, the throttle passage 11a, the second heat transfer tube group 2b, and finally the second flow port. Run off from 3 g. Even between these, the passage wall 11
The speed of the refrigerant increases when passing through the throttle passage 11a of
The refrigerant liquid 10 that has passed through the throttle passage 11a collides with the partition plate 5 or the partition plate 6 and then moves to the windward side of the air 8. Therefore, the refrigerant liquid 1 that has moved to the windward side
0 becomes a state in which it is difficult to move to the leeward side regardless of the influence of gravity, and most of it comes to flow out from the heat transfer tube groups 2a and 2b located on the windward side.

Next, the action at the time of condensation will be described.
At the time of condensation, the refrigerant flows into the first header 3 from the second circulation port 3g. The inflowing refrigerant is in the state of only the refrigerant gas 9 having a dryness of 1.0.

As shown by the broken line arrow in FIGS. 9 and 11, the refrigerant flowing into the first header 3 flows into the fifth chamber 3e, and then the second header 4 passes through the first heat transfer tube group 2a.
Flows into the fourth chamber 4d. During this time, the refrigerant passing through the first heat transfer tube group 2a exchanges heat with the air 8 through the fins 1 and is condensed, so that the dryness is gradually reduced. Air 8
Absorbs heat from the first heat transfer tube group 2a while passing through the fins 1, so that the temperature thereof increases as going from the windward side to the leeward side. Therefore, since the temperature difference between the first heat transfer tube group 2a and the air 8 is the largest on the windward side, the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the throttle passage 11a, it will flow out from the second heat transfer tube group 2b. Here, according to the heat exchanger,
Since the speed of the refrigerant increases when passing through the throttle passage 11a, the refrigerant liquid 10 after passing through the throttle passage 11a collides with the partition plate 6 and then moves to the windward side. The refrigerant liquid 10 that has moved to the windward side has a large space defined by the passage wall 11 and the partition plate 6, and thus the second header 4
After colliding with the inner wall on the windward side, it moves to the leeward side due to the effect of gravity and circulates in the space. Therefore, the refrigerant liquid 10 flowing out from the second heat transfer tube group 2b is likely to be uniformly distributed, and the refrigerant gas 9 flowing out from the second heat transfer tube group 2b is also distributed uniformly.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 through the fins 1 while passing through the second heat transfer tube group 2b to be condensed, and the fourth chamber 3d of the first header 3 is condensed.
Leading to. Thereafter, similarly, the refrigerant passes through the throttle passage 11a, the first heat transfer tube group 2a, the second header 4, the throttle passage 11a, the second heat transfer tube group 2b, the first header 3, and finally the first header 3 of the first header 3. It flows out from the distribution port 3f. Between these,
The speed of the refrigerant increases when passing through the throttle passage 11a, and the refrigerant liquid 10 after passing through the throttle passage 11a collides with the partition plate 6 and then moves to the windward side. The refrigerant liquid 10 that has moved to the windward side has a large space, so that the header 3,
After colliding with the inner wall on the windward side of No. 4, it moves to the leeward side due to the influence of gravity, and circulates in the space, so that it easily flows out uniformly from each of the first heat transfer tube group 2a and the second heat transfer tube group 2a. It becomes easy to flow out uniformly from each of the heat pipe groups 2b.

As described above, in the above heat exchanger, the second heat transfer tube group 2 for allowing the refrigerant to flow out in the first header 3 during evaporation.
The passage wall 11 is arranged such that the portion connected to b is narrower than the portion connected to the first heat transfer tube group 2a into which the refrigerant flows during evaporation, and the throttle passage 11a is located at the leeward side.
And a portion of the second header 4 that is connected to the first heat transfer tube group 2a that allows the refrigerant to flow out at the time of evaporation is the second heat transfer tube group 2b that allows the refrigerant to flow at the time of evaporation.
Since the passage wall 11 is arranged so as to be narrower than the portion connected to and the throttle passage 11a is provided at a position on the leeward side, it is positioned on the windward side in the first heat transfer tube group 2a during evaporation. A large amount of the refrigerant liquid 10 can be secured to the product, and the refrigerant gas 9 can be secured to the product located on the windward side in the second heat transfer tube group 2b at the time of condensation. That is, according to the heat exchanger, it is possible to significantly increase the heat exchange amount at the time of evaporation while securing the heat exchange amount at the time of condensation even when the heat exchanger is arranged at an angle of 45 degrees. Become.

44 and 45 show the first heat transfer tube group 2a and the second heat transfer tube group in the heat exchanger described above and the conventional heat exchanger.
It is a graph which shows the result of having verified the distribution ratio of the refrigerant liquid 10 to each of the heat transfer tube groups 2b by experiment. Figure 44
Is the first when the refrigerant flows from the lower side to the upper side with respect to the heat exchanger of the third embodiment and the conventional heat exchanger inclined at 45 degrees.
FIG. 45 shows the distribution ratio of the refrigerant liquid 10 to the heat transfer tube group 2a, and FIG. 45 shows the case where the refrigerant flows from the upper side to the lower side of the heat exchanger of the third embodiment and the conventional heat exchanger inclined at 45 degrees. The distribution ratio of the refrigerant liquid 10 to the second heat transfer tube group 2b is shown.

The dimensions of the heat exchanger used in the experiment are as shown in FIGS. 39 and 43. 39 and 43, both show the chamber defined by the two partition plates 6 in the second header 4, for example, the second chamber 4b. The chamber measures 22.3 mm in width and 1 in height.
The thickness is 4.3 mm and the dimension in the thickness direction is 1.4 mm. The first heat transfer tube group 2a and the second heat transfer tube group 2b each include four heat transfer tubes arranged at a pitch of 6 mm. Furthermore, the distance between the first heat transfer tube group 2a and the second heat transfer tube group 2b is 10 mm. For the sake of convenience, the first heat transfer tube group 2a will be referred to as a, a, a, a in order from the one located above, and the second heat transfer tube group 2b will be located in order from the one located above.
Called b, b, b, b.

Further, in the heat exchanger of the third embodiment shown in FIG. 43, there is a plate between the portion of the chamber 4b connected to the first heat transfer tube group 2a and the portion connected to the second heat transfer tube group 2b. A passage wall 11 having a thickness of 1 mm is interposed. The position where the passage wall 11 is interposed is 9.65 mm from the bottom, and the portion of the chamber 4b connected to the first heat transfer tube group 2a is sufficiently narrower than the portion connected to the second heat transfer tube group 2b. I have to. The passage wall 11 has a width 1.7 mm and a length 1 mm of the throttle passage 11 at a position further lower than the lowermost one a in the first heat transfer tube group 2 a.
a is formed.

In the experiment, a refrigerant having a dryness of 0.4 was flowed at a flow rate of 6 kg / h, and the ratio of the refrigerant liquid 10 flowing through each heat transfer tube of the first heat transfer tube group 2a and the second heat transfer tube group 2b was measured. did. 38 and 39, the horizontal axis represents the number of the heat transfer tube described above, and the vertical axis represents the flow rate ratio of the refrigerant liquid flowing into the heat transfer tube.

When the refrigerant flows from the bottom to the top (during evaporation) as shown by the solid line arrows in FIGS. 39 and 43, according to the heat exchanger of the third embodiment as shown in FIG. It can be seen that the flow rate ratio of the refrigerant liquid 10 flowing into the heat transfer tube a in the direction opposite to the gravity direction 7 obviously increases as compared with the conventional heat exchanger.

When the refrigerant flows from the upper side to the lower side (during condensation) as shown by the broken line arrows in FIGS. 39 and 43, the heat exchanger of the third embodiment has the structure shown in FIG. According to this, it can be seen that the flow rate ratio of the refrigerant liquid 10 flowing into the second heat transfer tube group 2b is evenly distributed as compared with the header of the conventional heat exchanger. Therefore, the refrigerant gas 9 flowing into the second heat transfer tube group 2b also tends to be uniformly distributed.

As a result, the heat exchanger is installed in a state of being inclined by 45 degrees with respect to the gravity direction 7, and the air 8 is supplied to the heat exchanger 45
When the refrigerant flows from the upper side to the lower side at the time of evaporation, and when the refrigerant flows from the lower side to the upper side at the time of evaporation and the refrigerant flows from the upper side to the lower side at the time of condensation, the first heat transfer tube group 2a moves to the windward side at the time of evaporation. A large amount of the refrigerant liquid 10 flows out to the located one, and the amount of the refrigerant gas 9 that flows out to the one located on the windward side in the second heat transfer tube group 2b at the time of condensation becomes sufficient. Therefore, the desired heat exchange amount can be secured during condensation, while the heat exchange amount can be significantly increased during evaporation.

In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees and the air 8 is flown from 45 degrees upward to 45 degrees downward. Can be arbitrarily selected from 0 degrees to 90 degrees, and the direction in which the air 8 flows can be arbitrarily set as long as the throttle passage 11a is in the leeward direction.

Further, the throttle passage 11 is provided inside the headers 3 and 4.
By arranging the passage wall 11 having a, the throttle passages 11a are provided in the headers 3 and 4,
It is not necessary to process the headers 3 and 4,
Although there is no fear of complicating the manufacturing work of No. 4, for example, the throttle passage may be formed by forming the inner wall surface of the header into a projection shape, or the throttle passage may be formed by narrowing the wall surface of the header. It is possible. In addition, the heat transfer tube groups 2a, 2
The number and thickness of b can be arbitrarily determined. For example, similar to the first embodiment, the heating tube groups 2a, 2
b may be configured as a plurality of microchannels in a flat tube or an elliptical shape. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

The number, shape, mounting angle and size of the throttle passages 11a can be arbitrarily determined. For example, the throttle passage 11a may have the same width as the passage formed by the passage wall 11 and the partition plate 6.

Further, although the first head 3 and the second header 4 are provided in the third embodiment described above, a hairpin 2c is provided instead of the second header as shown in FIG. 12, and only the first header 3 is provided. It may be configured. Further, it is not limited to the hairpin, and it can be arbitrarily selected as long as it can connect the first heat transfer tube group 2a and the second heat transfer tube group 2b.

Fourth Embodiment In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the upper side and from the upper side to the lower side at the time of condensation in the fourth embodiment, the heat exchanger is installed at an inclination of 45 degrees and the air 8 is rotated from the lower side by 45 degrees from the lower side. The refrigerant is caused to flow upward, and the refrigerant is caused to flow from the lower side to the upper side at the time of evaporation, and the refrigerant is caused to flow from the upper side to the lower side at the time of condensation.

13 and 14 are sectional side views of the heat exchanger according to the fourth embodiment of the present invention as seen from one header side, and FIG. 13 shows the state of the refrigerant during evaporation. 14 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the fourth embodiment, the portion of the header that is connected to the condensing outflow-side heat transfer tube group in which the refrigerant flows out at the time of condensation is made to flow in the refrigerant at the time of condensation. The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the windward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the first heat transfer tube group 2a which is the outflow side heat transfer tube group at the time of condensation is narrower than the part connected to the second heat transfer tube group 2b which is the inflow side heat transfer tube group at the time of condensation. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the second heat transfer tube group 2b, which is the heat transfer tube group on the outflow side during condensation, is condensed. The passage wall 11 is arranged so as to be narrower than the portion connected to the first heat transfer tube group 2a, which is the time inflow side heat transfer tube group. Each passage wall 11 is provided with a unique throttle passage 11a at the leeward side of the air 8.

Since the other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

According to the fourth embodiment configured as described above, the heat exchanger is installed at an angle of 45 degrees, the air 8 is made to flow from 45 degrees downward to 45 degrees upward, and the refrigerant is lowered at the time of evaporation. By flowing the refrigerant from the upper side to the upper side from the upper side to the lower side during the condensation, it is possible to significantly increase the heat exchange amount during the condensation while securing a desired heat exchange amount during the evaporation.

In the fourth embodiment described above, the heat exchanger is installed at an angle of 45 degrees and the air 8 is made to flow from 45 degrees downward to 45 degrees upward. Can be arbitrarily selected from 0 to 90 degrees, and the flow direction of the air 8 can be arbitrarily selected as long as the throttle passage 11a is in the windward direction. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Embodiment 5. FIG. In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the description has been given of the case where the refrigerant is made to flow from the side to the upper side and from the upper side to the lower side at the time of condensation, in the fifth embodiment, the heat exchanger is installed at an angle of 45 degrees, and the air 8 is rotated from the 45 degree from the upper side by 45 degrees. The refrigerant flows downward from the upper side to the lower side at the time of evaporation, and the refrigerant flows from the lower side to the upper side at the time of condensation.

15 and 16 are sectional side views of the heat exchanger according to the fifth embodiment of the present invention as seen from one header side, and FIG. 15 shows the state of the refrigerant during evaporation. 16 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the fifth embodiment, the portion of the header that is connected to the evaporating outflow side heat transfer tube group in which the refrigerant flows out at the time of evaporation evaporates the refrigerant when evaporating. The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the leeward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the first heat transfer tube group 2a that is the evaporative outflow side heat transfer tube group is narrower than the portion that is connected to the second heat transfer tube group 2b that is the evaporative inflow side heat transfer tube group. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the second heat transfer tube group 2b, which is the heat transfer tube group on the outflow side at the time of evaporation, evaporates. The passage wall 11 is arranged so as to be narrower than the portion connected to the first heat transfer tube group 2a, which is the time inflow side heat transfer tube group. Each passage wall 11 is provided with a unique throttle passage 11a at the leeward side of the air 8.

Since the other structures are similar to those of the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

According to the fifth embodiment configured as described above, the heat exchanger is installed at an angle of 45 degrees, the air 8 is made to flow from 45 degrees upward to 45 degrees downward, and the refrigerant is evaporated from above at the time of evaporation. By flowing the refrigerant from the lower side to the upper side at the time of condensation on the lower side, it becomes possible to significantly increase the amount of heat exchange at the time of evaporation while securing a desired amount of heat exchange at the time of condensation.

In the fifth embodiment described above, the heat exchanger is installed at an angle of 45 degrees, and the air 8 is flown from 45 degrees upward to 45 degrees downward. Can be arbitrarily selected from 0 degrees to 90 degrees, and the direction in which the air 8 flows can be arbitrarily set as long as the throttle passage 11a is in the leeward direction. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Sixth Embodiment In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the lower side during condensation from the upper side to the upper side, in the sixth embodiment, the heat exchanger is installed at an angle of 45 degrees, and the air 8 is rotated from the lower side by 45 degrees by 45 degrees. The refrigerant flows upward from the upper side, and the refrigerant flows from the upper side to the lower side during evaporation, and the refrigerant flows from the lower side to the upper side during condensation.

17 and 18 are sectional side views of the heat exchanger according to the sixth embodiment of the present invention as seen from one header side. FIG. 17 shows the state of the refrigerant during evaporation. 18 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the sixth embodiment, the portion of the header that is connected to the condensing outflow-side heat transfer tube group in which the refrigerant flows out at the time of condensation is made to flow in the refrigerant at the time of condensation. The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the windward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the second heat transfer tube group 2b, which is the condensing outflow side heat transfer tube group, is narrower than the part connected to the first heat transfer tube group 2a, which is the condensing inflow side heat transfer tube group. While the passage wall 11 is arranged as described above, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the first heat transfer tube group 2a which is the outflow side heat transfer tube group at the time of condensation is condensed. The passage wall 11 is arranged so as to be narrower than the portion connected to the second heat transfer tube group 2b which serves as the time inflow side heat transfer tube group. Each of the passage walls 11 is provided with a unique throttle passage 11a at a portion on the windward side of the air 8.

Since the other structures are similar to those of the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

According to the sixth embodiment configured as described above, the heat exchanger is installed at an angle of 45 degrees, the air 8 is made to flow from 45 degrees downward to 45 degrees upward, and the refrigerant is evaporated from the upper side during evaporation. By flowing the refrigerant from the lower side to the upper side at the time of condensation on the lower side, it becomes possible to significantly increase the amount of heat exchange at the time of condensation while securing a desired amount of heat exchange at the time of evaporation.

In the sixth embodiment described above, the heat exchanger is installed at an angle of 45 degrees and the air 8 is made to flow from 45 degrees downward to 45 degrees upward, but the installation angle of the heat exchanger is Can be arbitrarily selected from 0 degrees to 90 degrees, and the direction in which the air 8 flows can be arbitrarily set as long as the throttle passage 11a is in the windward direction. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Seventh Embodiment In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the upper side and from the upper side to the lower side at the time of condensation in the seventh embodiment, in the seventh embodiment, the heat exchanger is installed along the gravity direction 7 and the air 8 flows horizontally. In addition, the refrigerant flows from the lower side to the upper side during evaporation, and the refrigerant flows from the upper side to the lower side during condensation.

19 and 20 are sectional side views of the heat exchanger according to the seventh embodiment of the present invention as seen from one header side, and FIG. 19 shows the state of the refrigerant during evaporation. 20 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the seventh embodiment, the portion of the header that is connected to the evaporating outflow-side heat transfer tube group in which the refrigerant flows out during evaporation evaporates the refrigerant during evaporation. The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the leeward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the second heat transfer tube group 2b, which is the evaporative outflow side heat transfer tube group, is narrower than the portion connected to the first heat transfer tube group 2a, which is the evaporative inflow side heat transfer tube group. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the first heat transfer tube group 2a, which is the heat transfer tube group on the outflow side at the time of evaporation, is evaporated. The passage wall 11 is arranged so as to be narrower than the portion connected to the second heat transfer tube group 2b which serves as the time inflow side heat transfer tube group. Each passage wall 11 is provided with a unique throttle passage 11a at the leeward side of the air 8.

Since the other structures are similar to those of the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

Even when the heat exchanger is installed along the direction of gravity 7, the amount of heat exchange is large on the windward side, and therefore the refrigerant liquid is condensed on the windward side heat transfer tube during evaporation, and the refrigerant gas on the windward side during condensation. It is necessary to flow to the heat transfer tube.

According to the seventh embodiment configured as described above, the heat exchanger is installed along the gravity direction 7, the air 8 is flown in the horizontal direction, and the refrigerant is condensed from the lower side to the upper side during evaporation. If the refrigerant is sometimes made to flow from the upper side to the lower side, a desired heat exchange amount can be secured at the time of condensation, and the heat exchange amount can be significantly increased at the time of evaporation.

In the seventh embodiment described above, the air 8
Although the air flows in the horizontal direction, the flow direction of the air 8 can be arbitrarily set as long as the throttle passage 11a is in the leeward direction. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Eighth Embodiment In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the upper side and from the upper side to the lower side at the time of condensation in the eighth embodiment, in the eighth embodiment, the heat exchanger is installed along the gravity direction 7 and the air 8 flows horizontally. In addition, the refrigerant flows from the upper side to the lower side during evaporation, and the refrigerant flows from the lower side to the upper side during condensation.

21 and 22 are cross-sectional side views of the heat exchanger according to the eighth embodiment of the present invention as seen from one header side, and FIG. 21 shows the state of the refrigerant during evaporation. 22 shows the state of the refrigerant at the time of condensation.

As is apparent from these figures, in the eighth embodiment, the portion of the header that is connected to the evaporating outflow side heat transfer tube group in which the refrigerant flows out at the time of evaporation evaporates the refrigerant when evaporating. The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the leeward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the first heat transfer tube group 2a that is the evaporative outflow side heat transfer tube group is narrower than the portion that is connected to the second heat transfer tube group 2b that is the evaporative inflow side heat transfer tube group. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the second heat transfer tube group 2b, which is the heat transfer tube group on the outflow side at the time of evaporation, evaporates. The passage wall 11 is arranged so as to be narrower than the portion connected to the first heat transfer tube group 2a, which is the time inflow side heat transfer tube group. Each passage wall 11 is provided with a unique throttle passage 11a at the leeward side of the air 8.

Since the other structures are similar to those of the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

Even when the heat exchanger is installed along the direction of gravity 7, the amount of heat exchange is large on the windward side, so that the refrigerant flows to the heat transfer tube on the windward side during evaporation and the refrigerant gas flows on the windward side during condensation. It is necessary to flow to the heat transfer tube.

According to the eighth embodiment configured as described above, the heat exchanger is installed along the gravity direction 7, the air 8 is flown in the horizontal direction, and the refrigerant is condensed from the upper side to the lower side during evaporation. When the refrigerant is sometimes made to flow from the lower side to the upper side, a desired heat exchange amount can be secured during condensation, and the heat exchange amount can be significantly increased during evaporation.

In the eighth embodiment described above, the air 8
Although it is flowing in the horizontal direction, it can be arbitrarily set as long as it is in the leeward direction of the throttle passage 11a. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Ninth Embodiment In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the upper side and from the upper side to the lower side at the time of condensation, the ninth embodiment installs the heat exchanger along the gravity direction 7 and causes the air 8 to flow in the horizontal direction. In addition, the refrigerant flows from the lower side to the upper side during evaporation, and the refrigerant flows from the upper side to the lower side during condensation.

23 and 24 are sectional side views of the heat exchanger according to the ninth embodiment of the present invention viewed from one header side, and FIG. 23 shows a state of the refrigerant at the time of evaporation. 24 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the ninth embodiment, the portion of the header that is connected to the condensing outflow-side heat transfer tube group in which the refrigerant flows out at the time of condensation makes the refrigerant inflow at the time of condensation The chamber is partitioned so as to be narrower than the portion connected to the inflow side heat transfer tube group, and a throttle passage is provided at a position on the windward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the first heat transfer tube group 2a which is the outflow side heat transfer tube group at the time of condensation is narrower than the part connected to the second heat transfer tube group 2b which is the inflow side heat transfer tube group at the time of condensation. While the passage wall 11 is thus arranged, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the second heat transfer tube group 2b, which is the heat transfer tube group on the outflow side during condensation, is condensed. The passage wall 11 is arranged so as to be narrower than the portion connected to the first heat transfer tube group 2a, which is the time inflow side heat transfer tube group. Each of the passage walls 11 is provided with a unique throttle passage 11a at a portion on the windward side of the air 8.

Since the other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

Even when the heat exchanger is installed along the gravitational direction 7, the amount of heat exchange on the windward side is large, so that the refrigerant liquid is condensed on the windward side heat transfer tube during evaporation and the refrigerant gas on the windward side is condensed. It is necessary to flow to the heat transfer tube.

According to the ninth embodiment configured as described above, the heat exchanger is installed along the gravity direction 7, the air 8 is flown horizontally, and the refrigerant is condensed from the lower side to the upper side during evaporation. If the refrigerant is sometimes made to flow from the upper side to the lower side, a desired heat exchange amount can be secured during evaporation, and the heat exchange amount can be significantly increased during condensation.

In the ninth embodiment described above, the air 8
Although it is flowing in the horizontal direction, it can be arbitrarily selected as long as the throttle passage 11a is in the windward direction. The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Embodiment 10. In the third embodiment described above, the heat exchanger is installed at an angle of 45 degrees with respect to the gravity direction 7, the air 8 is made to flow 45 degrees downward from above the heat exchanger 45 degrees, and the refrigerant is lowered at the time of evaporation. Although the refrigerant is made to flow from the upper side to the lower side during condensation from the upper side to the upper side, in the tenth embodiment, the heat exchanger is installed along the gravity direction 7 and the air 8 flows in the horizontal direction. In addition, the refrigerant flows from the upper side to the lower side during evaporation, and the refrigerant flows from the lower side to the upper side during condensation.

25 and 26 are sectional side views of the heat exchanger according to the tenth embodiment of the present invention as seen from one header side, and FIG. 25 shows the state of the refrigerant during evaporation. 26 shows the state of the refrigerant at the time of condensation.

As is clear from these figures, in the tenth embodiment, the portion of the header connected to the condensing outflow side heat transfer tube group for letting out the refrigerant during condensing is
The chamber is partitioned so as to be narrower than a portion connected to the inflow side heat transfer tube group at the time of condensation for allowing the refrigerant to flow at the time of condensation, and a throttle passage is provided at a position on the windward side.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, the portion connected to the second heat transfer tube group 2b, which is the condensing outflow side heat transfer tube group, is narrower than the part connected to the first heat transfer tube group 2a, which is the condensing inflow side heat transfer tube group. While the passage wall 11 is arranged as described above, in each of the chambers 4a, 4b, 4c, 4d of the second header 4, the portion connected to the first heat transfer tube group 2a which is the outflow side heat transfer tube group at the time of condensation is condensed. The passage wall 11 is arranged so as to be narrower than the portion connected to the second heat transfer tube group 2b which serves as the time inflow side heat transfer tube group. Each of the passage walls 11 is provided with a unique throttle passage 11a at a portion on the windward side of the air 8.

Since other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof is omitted.

Even when the heat exchanger is installed along the direction of gravity 7, the amount of heat exchange is large on the windward side, so the refrigerant liquid flows to the heat transfer tube on the windward side during evaporation and the refrigerant gas flows on the windward side during condensation. It is necessary to flow to the heat transfer tube of.

According to the tenth embodiment configured as described above, the heat exchanger is installed along the gravity direction 7, the air 8 is flown horizontally, and the refrigerant is evaporated from the upper side to the lower side during evaporation.
By allowing the refrigerant to flow from the lower side to the upper side during condensation, it is possible to significantly increase the heat exchange rate during condensation while ensuring a desired heat exchange rate during evaporation.

In the tenth embodiment described above, the air 8 is flown in the horizontal direction, but it can be arbitrarily selected as long as the throttle passage 11a is in the windward direction. Also,
The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Eleventh Embodiment Although the throttle passage 11a is configured by disposing the passage wall 11 in the first header 3 and the second header 4 in the third embodiment described above, the U-shaped pipe having a different diameter is applied in the eleventh embodiment. And the header and the throttle passage are configured.

FIG. 27 is a sectional side view of the heat exchanger according to the eleventh embodiment of the present invention as viewed from one header side. The heat exchanger exemplified here is installed at an angle of 45 degrees with respect to the gravity direction 7 as in the case of the third embodiment, and the air 8 is made to flow from 45 degrees upward to 45 degrees downward, and The refrigerant is made to flow from the lower side to the upper side at the time of evaporation, and the refrigerant is made to flow from the upper side to the lower side at the time of condensation, and only the structure of the header is different.

That is, the second header 4 shown in FIG.
The first heat transfer tube group 2a and the second heat transfer tube group 2b are connected by a U-shaped copper pipe 14. More specifically, the curved portion leading to the first heat transfer tube group 2a, which is the heat transfer tube group on the outflow side at the time of evaporation for letting out the refrigerant at the time of evaporation, is located on the leeward side and the throttle passage 1
4a is configured. Such copper piping 14
The four headers are arranged to form the second header 4.

The second header 4 having the above-described structure includes the chambers 12a, 12b, 12c, 12d, 12e, 12f, 1
2g and 12h are formed and connected to the first heat transfer tube group 2a and those connected to the second heat transfer tube group 2b. Chambers 12a, 12b, 12c, 12d, 12e, 12
In f, 12g, and 12h, the side connected to the first heat transfer tube group 2a serving as the evaporative outflow side heat transfer tube group has a space larger than that connected to the second heat transfer tube group 2b serving as the evaporative inflow side heat transfer tube group. It has a narrow structure.

Although not shown, the first header has the same structure as the second header 4. However,
Regarding the chamber of the header, the space connected to the second heat transfer pipe group 2b serving as the evaporative outflow side heat transfer pipe group is larger than that connected to the first heat transfer pipe group 2a serving as the evaporative inflow side heat transfer pipe group It has a narrow structure. Further, since other configurations are similar to those of the third embodiment, the same reference numerals are given and detailed description thereof is omitted.

In the heat exchanger configured as described above, the second
A portion of the header 4 connected to the first heat transfer tube group 2a for letting out the refrigerant at the time of evaporation is made narrower than a portion connected to the second heat transfer tube group 2b for letting in the refrigerant at the time of evaporation, and is located on the leeward side. Since the throttle passage 14a is provided, a large amount of the refrigerant liquid 10 can be secured in the first heat transfer tube group 2a which is located on the windward side during evaporation, and the condenser liquid can be positioned on the windward side in the second heat transfer tube group 2b during condensation. It is possible to secure the refrigerant gas 9 for the thing that does. That is, according to the heat exchanger, it is possible to significantly increase the heat exchange amount at the time of evaporation while securing the heat exchange amount at the time of condensation even when the heat exchanger is arranged at an angle of 45 degrees. Become.

In the third to eleventh embodiments described above, the case where the heat exchanger is installed at an angle of 45 degrees or the case where the heat exchanger is installed vertically is described. However, the installation angle of the heat exchanger is It is optional, and the same effect can be obtained by adopting the combination shown above.

[Embodiment 12] 28 is a sectional view showing a structure of a heat exchanger according to a twelfth embodiment of the present invention. FIG. 29 is a cross-sectional side view of the heat exchanger shown in FIG. 28 as seen from one header side and shows the state of the refrigerant during evaporation. FIG. 31 is a cross-sectional side view of the heat exchanger shown in FIG. 28 as seen from one header side and shows the state of the refrigerant during condensation.

The heat exchanger illustrated here has the same structure as the heat exchanger of the first embodiment described above, and only the internal structure of the header is different. That is, in the twelfth embodiment, in the header, the chamber is partitioned so that the portion connected to each heat transfer tube group is narrowed, and the portion connected to the evaporating outflow side heat transfer tube group that allows the refrigerant to flow out during evaporation is The first throttle passage is provided at a position on the leeward side, and the second throttle passage is provided at a position on the windward side in a portion connected to the vaporization inflow side heat transfer tube group for allowing the refrigerant to flow during evaporation.

More specifically, each chamber 3b of the first header 3
In 3c and 3d, passage walls 15a and 15b are formed so that the portions connected to the heat transfer tube groups 2a and 2b are narrowed.
Second heat transfer tube group 2b serving as an outflow-side heat transfer tube group at the time of evaporation for allowing the refrigerant to flow out at the time of evaporation.
On the leeward side of the passage wall 15a close to the first throttle passage 15a
While providing a, the passage wall 1 adjacent to the first heat transfer tube group 2a, which is a heat transfer tube group on the inflow side at the time of evaporation for allowing the refrigerant to flow in at the time of evaporation
A second throttle passage 15ba is provided on the windward side of 5b.

Each chamber 4a, 4b, 4c, 4 of the second header 4
In d, the pair of passage walls 16a and 16b are arranged at a distance from each other so that the portions connected to the heat transfer tube groups 2a and 2b are narrowed, and the refrigerant flows out during evaporation. The first throttle passage 16aa is provided on the leeward side of the passage wall 16a adjacent to the first heat transfer pipe group 2a which is the heat transfer pipe group.
On the other hand, the passage wall 16 adjacent to the second heat transfer tube group 2b, which is a heat transfer tube group on the inflow side at the time of evaporation for allowing the refrigerant to flow in at the time of evaporation
The second throttle passage 16ba is provided on the windward side of b.

Since the other structures are the same as those in the first embodiment, the same reference numerals are given and detailed description thereof will be omitted.

Next, the operation of the heat exchanger according to the twelfth embodiment will be described. First, at the time of evaporation, the refrigerant flows into the first header 3 from the first circulation port 3f. The refrigerant flowing in is composed of a refrigerant gas 9 and a refrigerant liquid 10 having a dryness of about 0.2.
And are mixed.

As shown by the solid line arrows in FIGS. 28 and 29, the refrigerant flowing into the first header 3 flows into the first chamber 3a, and then the second header 4 passes through the second heat transfer tube group 2b.
Flows into the first chamber 4a. During this time, the refrigerant passing through the second heat transfer tube group 2b exchanges heat with the air 8 via the fins 1 to evaporate, and the dryness gradually increases. Air 8
Heat is absorbed by the second heat transfer tube group 2b while passing through the fins 1, so that the temperature thereof decreases as going from the windward side to the leeward side. Therefore, the temperature difference between the second heat transfer tube group 2b and the air 8 is the largest on the windward side, and the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the second throttle passage 16ba and the first throttle passage 16aa, it is discharged from the first heat transfer tube group 2a. Here, since the speed of the refrigerant increases when passing through the first throttle passage 16aa, the refrigerant liquid 10 after passing through the first throttle passage 16aa collides with the partition plate 6, and thereafter,
It will move to the windward side. Further, the refrigerant liquid 10 that has moved to the windward side is in a state in which it is difficult to move to the leeward side regardless of the influence of gravity because the space defined by the passage wall 16a and the partition plate 6 is narrow, and most of it is in the first transmission. Outflow comes from the heat pipe group 2a located on the windward side.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 via the fins 1 while passing through the first heat transfer tube group 2a to evaporate, and the second chamber 3b of the first header 3 is evaporated.
Leading to. After that, it passes through the first throttle passage 15aa and the second throttle passage 15ba, and is discharged from the second heat transfer tube group 2b. Here, according to the heat exchanger, since the speed of the refrigerant increases when passing through the second throttle passage 15ba, the refrigerant liquid 10 passing through the throttle passage 15ba collides with the partition plate 5, and then the air It will move to the windward side of 8. Further, the refrigerant liquid 10 that has moved to the windward side is in a state in which it is difficult to move to the leeward side regardless of the influence of gravity because the space defined by the passage wall 15b and the partition plate 5 is narrow, and most of it is in the second transmission. The heat will flow out from the heat pipe group 2b located on the windward side.

After that, similarly, the refrigerant is supplied to the first header 3 and the second header.
It flows through the headers 4 alternately, and finally flows out from the second circulation port 3g of the first header 3.

Next, the action at the time of condensation will be described.
At the time of condensation, the refrigerant flows into the first header 3 from the second circulation port 3g. The inflowing refrigerant is in the state of only the refrigerant gas 9 having a dryness of 1.0.

As shown by the broken line arrows in FIGS. 28 and 30, the refrigerant flowing into the first header 3 flows into the fifth chamber 3e, and thereafter, the second header 4 passes through the first heat transfer tube group 2a.
Flows into the fourth chamber 4d. During this time, the refrigerant passing through the first heat transfer tube group 2a exchanges heat with the air 8 through the fins 1 and is condensed, so that the dryness is gradually reduced. Air 8
Absorbs heat from the first heat transfer tube group 2a while passing through the fins 1, so that the temperature thereof increases as going from the windward side to the leeward side. Therefore, the temperature difference between the first heat transfer tube group 2a and the air 8 is the largest on the windward side, and the heat exchange amount on the windward side is large.

Then, the refrigerant flowing into the second header 4 is
After passing through the first throttle passage 16aa and the second throttle passage 16ba, it is discharged from the second heat transfer tube group 2b. Here, according to the heat exchanger, since the speed of the refrigerant increases when passing through the second throttle passage 16ba, the refrigerant liquid 10 after passing through the second throttle passage 16ba collides with the partition plate 6. Move downwind. Therefore, the area ratio of the refrigerant liquid 10 increases at the inlet of the second heat transfer tube group 2b that is located on the leeward side, and the area ratio that the refrigerant gas 9 can pass through decreases, so that the second heat transfer tube group 2b moves to the leeward side. Refrigerant gas 9 flowing into the positioned one decreases, and conversely, refrigerant gas 9 flowing into the one positioned on the windward side in the second heat transfer tube group 2b increases.

Further, the refrigerant flowing out from the second header 4 exchanges heat with the air 8 via the fins 1 while passing through the second heat transfer tube group 2b to be condensed, and the fourth chamber 3d of the first header 3 is condensed.
Leading to. Thereafter, similarly, the refrigerant alternately passes through the first header 3 and the second header 4, and finally, the first circulation port 3 of the first header 3
out of f.

As described above, in the heat exchanger, each heat transfer tube group 2 is provided in each chamber 3b, 3c, 3d of the first header 3.
A second heat transfer tube group, which is an evaporation-side outflow-side heat transfer tube group, in which the passage walls 15a and 15b are arranged with a space therebetween so as to narrow the portions connected to a and 2b, respectively, and the refrigerant flows out during evaporation. The first throttle passage 15aa is provided on the leeward side of the passage wall 15a close to 2b, and the windward side of the passage wall 15b close to the first heat transfer pipe group 2a which is the inflow side heat transfer pipe group at the time of evaporation for letting the refrigerant in at the time of evaporation. To the second throttle passage 15ba
Is provided. In addition, each chamber 4 of the second header 4
a, 4b, 4c, 4d, each heat transfer tube group 2a, 2
A pair of passage walls 16a, 16b are arranged with a space therebetween so that the portion connected to b becomes narrower, and a first heat transfer tube group serving as an evaporating outflow side heat transfer tube group for letting out a refrigerant during evaporation. The first throttle passage 16aa is provided on the leeward side of the passage wall 16a close to 2a, and the windward side of the passage wall 16b close to the second heat transfer tube group 2b, which is a heat transfer tube group at the time of evaporation inflowing refrigerant, is formed. To the second throttle passage 16ba
Is provided.

As a result, at the time of evaporation, the heat transfer tube group 2
The refrigerant liquid 10 can be made to flow to the ones located on the windward side in a and 2b, while at the time of condensation, the heat transfer tube groups 2a and 2b.
Since the refrigerant gas 9 can be made to flow to the one located on the windward side in b, the heat exchange amount can be greatly increased both during evaporation and condensation.

47 and 48 show the first heat transfer tube group 2a and the second heat transfer tube group in the heat exchanger described above and the conventional heat exchanger.
It is a graph which shows the result of having verified the distribution ratio of the refrigerant liquid 10 to each of the heat transfer tube groups 2b by experiment. FIG. 47
Shows the distribution ratio of the refrigerant liquid 10 to the first heat transfer tube group 2a when the refrigerant flows from the lower side to the upper side with respect to the heat exchanger of the twelfth embodiment and the conventional heat exchanger inclined by 45 degrees,
FIG. 48 shows the distribution ratio of the refrigerant liquid 10 to the second heat transfer tube group 2b when the refrigerant flows from the upper side to the lower side with respect to the heat exchanger of the twelfth embodiment and the conventional heat exchanger inclined at 45 degrees. It is shown.

The dimensions of the heat exchanger used in the experiment are as shown in FIGS. 39 and 46. 39 and 46, both show the chamber defined by the two partition plates 6 in the second header 4, for example, the second chamber 4b. The chamber measures 22.3 mm in width and 1 in height.
The thickness is 4.3 mm and the dimension in the thickness direction is 1.4 mm. The first heat transfer tube group 2a and the second heat transfer tube group 2b each include four heat transfer tubes arranged at a pitch of 6 mm. Furthermore, the distance between the first heat transfer tube group 2a and the second heat transfer tube group 2b is 10 mm. For the sake of convenience, the first heat transfer tube group 2a will be referred to as a, a, a, a in order from the one located above, and the second heat transfer tube group 2b will be located in order from the one located above.
Called b, b, b, b.

Further, in the heat exchanger according to the twelfth embodiment shown in FIG. 46, a plate is provided between the portion connected to the first heat transfer tube group 2a and the portion connected to the second heat transfer tube group 2b in the chamber 4b. A pair of passage walls 16a and 16b having a thickness of 1 mm are interposed. The position where the passage wall 11 is interposed is 3.65 m from the top.
m and two positions of 3.65 mm from the bottom. On the upper passage wall 16a, a first throttle passage 16aa having a width of 1.7 mm and a length of 1 mm is formed at a position further lower than the lowermost one a in the first heat transfer tube group 2a. The lower passage wall 16b has a width of 1.7 mm and a second length of 1 mm at a position further above the uppermost one b in the second heat transfer tube group 2b.
A throttle passage 16ba is formed.

In the experiment, a refrigerant having a dryness of 0.4 was flowed at a flow rate of 6 kg / h, and the ratio of the refrigerant liquid 10 flowing through each heat transfer tube of the first heat transfer tube group 2a and the second heat transfer tube group 2b was measured. did. 47 and 48, the horizontal axis is the number of the heat transfer tube described above, and the vertical axis is the flow rate ratio of the refrigerant liquid flowing into the heat transfer tube.

When the refrigerant flows from the bottom to the top (during evaporation) as shown by the solid arrow in FIGS. 39 and 46, according to the heat exchanger of the twelfth embodiment as shown in FIG. It can be seen that the flow rate ratio of the refrigerant liquid 10 flowing into the heat transfer tube a in the direction opposite to the gravity direction 7 obviously increases as compared with the conventional heat exchanger.

When the refrigerant flows from the upper side to the lower side (during condensation) as shown by the broken line arrows in FIGS. 39 and 46, the heat exchanger of the twelfth embodiment has the same structure as shown in FIG. According to this, it is understood that the flow rate ratio of the refrigerant liquid 10 flowing into the heat transfer tube b in the direction opposite to the gravity direction 7 in the second heat transfer tube group 2b is further reduced as compared with the header of the conventional heat exchanger. That is, in the second heat transfer tube group 2b, the gravity direction 7
It can be seen that the ratio of the refrigerant gas 9 flowing into the heat transfer tube b in the opposite direction increases.

As a result, the heat exchanger is installed in a state of being inclined by 45 degrees with respect to the gravity direction 7, and the air 8 is supplied to the heat exchanger at 45 degrees.
When the refrigerant flows from the lower side to the upper side at the time of evaporation, and when the refrigerant flows from the upper side to the lower side at the time of condensation, it flows upward in the first heat transfer tube group 2a at the time of evaporation. A large amount of the refrigerant liquid 10 flows out to the positioned one, and a large amount of the refrigerant gas 9 flows out to the one located on the windward side in the second heat transfer tube group 2b during condensation. Therefore, the amount of heat exchange can be significantly increased both during evaporation and condensation.

In the twelfth embodiment described above, the heat exchanger is installed at an angle of 45 degrees and the air 8 is blown at 45 degrees.
Although it is flowing from the upper side to the lower side by 45 degrees, the installation angle of the heat exchanger can be arbitrarily selected from 0 to 90 degrees, and the air 8 flows in the leeward direction of the first throttle passage 16aa. In addition, any direction can be selected as long as the second throttle passage 16ba is in the windward direction.

The shape, mounting angle and size of the throttle passages 16aa and 16bb can be arbitrarily selected. For example, even if the throttle passage 16aa has the same width as the flow passage formed by the passage wall 16a and the partition plate 6, the heat exchange amount can be significantly increased.

In the twelfth embodiment described above, the refrigerant liquid after passing through the second throttle passage 16ba at the time of condensation moves to the leeward side due to gravity, so that the opening area of the second throttle passage 16ba is set to the first area. If it is larger than the opening area of the throttle passage 16aa, the heat exchange amount can be significantly increased, and the pressure loss of the refrigerant can be reduced. Further, since the opening area of the second throttle passage 16ba is increased, the pressure loss during evaporation can be reduced.

The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Further, in the twelfth embodiment described above, the first header 3 and the second header 4 are provided, but as shown in FIG. 31, a hairpin 2c is provided instead of the second header, and only the first header 3 is provided. It may be configured. Further, it is not limited to the hairpin, and it can be arbitrarily selected as long as it can connect the first heat transfer tube group 2a and the second heat transfer tube group 2b.

Thirteenth Embodiment 32 and 33 are cross-sectional side views of the heat exchanger according to the thirteenth embodiment of the present invention as seen from one header side, FIG. 32 shows a state of the refrigerant during evaporation, and FIG. The state of the refrigerant at the time of condensation is shown.

The heat exchanger exemplified here has the same structure as the heat exchanger of the twelfth embodiment described above. However, the heat exchanger is installed in a state of being inclined at 45 degrees with respect to the gravity direction 7, and the air 8 is set at 45 degrees from below the heat exchanger.
Since it is made to flow upward by 5 degrees, the internal structure of the header is configured to be symmetrical with that of the twelfth embodiment according to the difference in the wind direction. That is, focusing on the second header 4, the chambers are partitioned by the passage walls 16a and 16b so that the portions connected to the heat transfer tube groups 2a and 2b become narrower. A first throttle passage 16aa is provided at a position on the leeward side at a portion connected to the first heat transfer tube group 2a through which the refrigerant flows during evaporation, and a portion connected to the second heat transfer tube group 2b through which the refrigerant flows during evaporation. Is provided with the second throttle passage 16ba at a position on the windward side.

Therefore, also in the heat exchanger of the thirteenth embodiment, as in the twelfth embodiment, the heat exchange amount can be greatly increased both during the evaporation and during the condensation.

In the thirteenth embodiment described above, the heat exchanger is installed at an angle of 45 degrees, and the air 8 is blown to 45 degrees.
Although it flows from the downward direction to the upward direction of 45 degrees, the installation angle of the heat exchanger can be arbitrarily selected from 0 to 90 degrees, and the air 8 flows in the leeward direction of the first throttle passage 16aa. In addition, any direction can be selected as long as the second throttle passage 16ba is in the windward direction.

In the thirteenth embodiment described above, since the refrigerant that has passed through the first throttle passage 16aa during evaporation moves to the windward side due to gravity, the first throttle passage 16a
When the opening area of a is larger than the opening area of the second throttle passage 16ba, the heat exchange amount can be significantly increased, and the pressure loss of the refrigerant can be reduced. Further, since the opening area of the first throttle passage 16aa is increased, the pressure loss at the time of condensation can be reduced.

The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Fourteenth Embodiment 34 and 35 are cross-sectional side views of the heat exchanger according to the fourteenth embodiment of the present invention seen from one header side, FIG. 34 shows a state of the refrigerant at the time of evaporation, and FIG. The state of the refrigerant at the time of condensation is shown.

The heat exchanger illustrated here has the same structure as the heat exchanger of the twelfth embodiment described above. However, while the refrigerant is allowed to flow from the upper side to the lower side at the time of evaporation, the refrigerant is allowed to flow from the lower side to the upper side at the time of condensation, so that the internal structure of the header may be changed depending on the difference in the flowing direction of the refrigerant. It is configured to be symmetrical with 12. That is, focusing on the second header 4, the chambers are partitioned by the passage walls 16a and 16b so that the portions connected to the heat transfer tube groups 2a and 2b become narrower. The second throttle passage 16b is provided at a position on the leeward side in a portion connected to the second heat transfer tube group 2b that allows the refrigerant to flow out during evaporation.
a is provided, and the first heat transfer tube group 2a into which the refrigerant flows at the time of evaporation is connected to the first heat transfer tube group 2a.
A throttle passage 16aa is provided.

Therefore, also in the heat exchanger of the fourteenth embodiment, as in the twelfth embodiment, the heat exchange amount can be greatly increased both during the evaporation and the condensation.

In the fourteenth embodiment described above, the heat exchanger is installed at an angle of 45 degrees and the air 8 is blown at 45 degrees.
Although it is flowing downward from the upper direction by 45 degrees, the installation angle of the heat exchanger can be arbitrarily selected between 0 degrees and 90 degrees, and the air 8 flows in the leeward direction by the second throttle passage 16ba. In addition, any direction can be selected as long as the first throttle passage 16aa is in the windward direction.

In the fourteenth embodiment described above, the refrigerant liquid after passing through the first throttle passage 16aa at the time of condensation moves to the leeward side due to gravity, so that the first throttle passage 1
When the opening area of 6aa is larger than the opening area of the second throttle passage 16ba, the heat exchange amount can be significantly increased, and the pressure loss of the refrigerant can be reduced. Further, since the opening area of the first throttle passage 16aa is increased, the pressure loss at the time of evaporation can be reduced.

The number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Fifteenth Embodiment 36 and 37 are cross-sectional side views of the heat exchanger according to the fifteenth embodiment of the present invention seen from one header side, FIG. 36 shows a state of the refrigerant at the time of evaporation, and FIG. The state of the refrigerant at the time of condensation is shown.

The heat exchanger illustrated here is opposite to the heat exchanger according to the twelfth embodiment in that the air 8 flows and the refrigerant flows in the opposite direction. However, the heat exchanger shown in FIG. The same as the form 12 of the above. That is, a heat exchanger having the same structure as that of the twelfth embodiment inside the header is installed in a state of being inclined by 45 degrees with respect to the gravity direction 7, and the air 8 is moved upward by 45 degrees from 45 degrees downward of the heat exchanger. In addition to flowing in the same direction, the refrigerant flows from the upper side to the lower side during evaporation, while the refrigerant flows from the lower side to the upper side during condensation.

Therefore, also in the fifteenth embodiment,
The amount of heat exchange can be significantly increased both during evaporation and condensation.

In the fifteenth embodiment described above, the heat exchanger is installed at an angle of 45 degrees, and the air 8 is blown at 45 degrees.
Although it is flowing from the downward direction to the upward direction of 45 degrees, the installation angle of the heat exchanger can be arbitrarily selected from 0 degree to 90 degrees, and the air 8 flows in the leeward direction of the second throttle passage 16ba. In addition, any direction can be selected as long as the first throttle passage 16aa is in the windward direction.

In the fifteenth embodiment described above, the refrigerant that has passed through the second throttle passage 16ba during evaporation moves due to gravity, so the second throttle passage 16ba is used.
If the opening area of is larger than the opening area of the first throttle passage 16aa, the heat exchange amount can be significantly increased, and the pressure loss of the refrigerant can be reduced. Also, the second
Since the opening area of the throttle passage 16ba is increased, the pressure loss at the time of condensation can be reduced.

Further, the number and thickness of the heat transfer tube groups 2a and 2b can be arbitrarily determined. For example, as in the first embodiment, the heating tube groups 2a and 2b may be configured as a plurality of microchannels in a flat tube or an elliptical tube. Further, the microchannel can have any shape other than a circle, a quadrangle, and the size and the number can be arbitrarily selected.

Sixteenth Embodiment Embodiment 12 described above
Then, in the first header 3 and the second header 4, the passage walls 15a,
Although the throttle passages 15aa, 15ba, 16aa, 16ba are configured by disposing 15b, 16a, 16b, in the sixteenth embodiment, the header and the throttle passage are configured by applying the copper pipe meandering in an S shape. It is a thing.

FIG. 38 is a sectional side view of the heat exchanger according to the sixteenth embodiment of the present invention as viewed from one header side. The heat exchanger exemplified here is installed at an angle of 45 degrees with respect to the gravity direction 7 as in the case of the twelfth embodiment, and allows the air 8 to flow from 45 degrees upward to 45 degrees downward, and The refrigerant is made to flow from the lower side to the upper side at the time of evaporation, and the refrigerant is made to flow from the upper side to the lower side at the time of condensation, and only the structure of the header is different.

That is, the second header 4 shown in FIG.
The first heat transfer tube group 2a and the second heat transfer tube group 2b are connected by a copper pipe 21 meandering in an S shape. More specifically,
At the time of evaporation at which the refrigerant flows out at the time of evaporation, the curved portion leading to the first heat transfer tube group 2a at the time of evaporation at which the refrigerant flows out at the time of evaporation is located on the leeward side to form the first throttle passage 21a. The curved portion reaching the second heat transfer tube group 2b serving as the inflow side heat transfer tube group is located on the windward side to form the second throttle passage 21b.

Although not shown, the first header has the same configuration as the second header 4.

In the heat exchanger configured as described above, the heat exchanger is installed in a state of being inclined by 45 degrees with respect to the gravity direction 7,
When the air 8 flows from the upper side of the heat exchanger 45 degrees downward to the lower side of 45 degrees, the refrigerant flows from the lower side to the upper side during evaporation, and the refrigerant flows from the upper side to the lower side during condensation, the first heat transfer tube during evaporation. A large amount of the refrigerant liquid 10 flows out to the one located on the windward side in the group 2a, and a large amount of the refrigerant gas 9 flows out to the one located on the windward side in the second heat transfer tube group 2b during condensation. . Therefore, the amount of heat exchange can be significantly increased both during evaporation and condensation.

In the twelfth to sixteenth embodiments described above, the case where the heat exchanger is installed tilted at 45 degrees has been described, but the installation angle of the heat exchanger is arbitrary.
The same effect can be obtained by adopting the combination shown above.

Further, although the first header 3 and the second header 4 are provided in the above-described first to sixteenth embodiments, a hairpin is provided in place of the second header 4 and only the first header 3 is provided. Also good. Further, it is not limited to the hairpin, and it can be arbitrarily selected as long as it can connect the first heat transfer tube group 2a and the second heat transfer tube group 2b.

The size of the throttle passages 21a and 21b is arbitrary, and the same effect can be obtained even if the diameter is equal to the diameter of the copper pipe.

[0218]

As described above, according to the heat exchanger of the present invention, since the speed of the refrigerant can be increased when passing through the throttle passage, the evaporation by utilizing the collision with the chamber. At both the time of condensation and the time of condensation, the refrigerant easily flows into each of the heat transfer tube groups evenly, and a desired heat exchange amount can be secured for each.

According to the next invention, since the throttle passage can be formed by interposing the passage wall inside the chamber, it is not necessary to process the header, which may complicate the manufacturing work of the header. There is no

According to the next invention, the refrigerant having a high degree of dryness passes through the throttle passage having a large opening area, so that the pressure loss of the heat exchanger can be reduced.

According to the next invention, the refrigerant liquid that has moved to the upwind side in the connection portion of the evaporation side outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the leeward side regardless of the influence of gravity in a narrow space. Therefore, it is possible to increase the heat exchange amount during evaporation while ensuring the heat exchange amount during condensation.

According to the next invention, the refrigerant liquid that has moved to the leeward side in the connecting portion of the condensing outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the upwind side in a narrow space regardless of the influence of gravity. Therefore, it is possible to increase the heat exchange amount during condensation while ensuring the heat exchange amount during evaporation.

According to the next invention, the refrigerant liquid that has moved to the upwind side at the connection portion of the evaporating outflow side heat transfer tube group in the chamber is in a state where it is difficult to move to the downwind side in a narrow space regardless of the influence of gravity. At the same time, the refrigerant liquid that has moved to the leeward side at the connection portion of the condensation-side outflow side heat transfer tube group in the chamber is unlikely to move to the upwind side in a narrow space regardless of the influence of gravity.

According to the next invention, since the pressure loss of the refrigerant passing through the inflow throttle passage is reduced, it is possible to increase the heat exchange amount both during evaporation and during condensation.

According to the present invention, since the throttle passage can be formed by using the pipe, the heat exchanger can be easily manufactured, and the manufacturing cost can be reduced.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a heat exchanger that is Embodiment 1 of the present invention.

2 is a cross-sectional side view of the heat exchanger shown in FIG. 1 viewed from one header side.

3 is a cross-sectional side view of the heat exchanger shown in FIG. 1 viewed from one header side.

FIG. 4 is a diagram showing a modified example of the heat exchanger according to the first embodiment of the present invention.

FIG. 5 is a diagram showing a modification of the heat exchanger according to the first embodiment of the present invention.

FIG. 6 is a diagram showing a modification of the heat exchanger according to the first embodiment of the present invention.

FIG. 7 is a sectional view of a heat exchanger according to a second embodiment of the present invention.

FIG. 8 is a diagram showing a modification of the heat exchanger according to the second embodiment of the present invention.

FIG. 9 is a sectional view of a heat exchanger that is Embodiment 3 of the present invention.

10 is a cross-sectional side view of the heat exchanger shown in FIG. 5 viewed from one header side.

11 is a cross-sectional side view of the heat exchanger shown in FIG. 5 viewed from one header side.

FIG. 12 is a diagram showing a modification of the heat exchanger according to the third embodiment of the present invention.

FIG. 13 is a sectional side view of the heat exchanger according to the fourth embodiment of the present invention as viewed from one header side.

FIG. 14 is a cross-sectional side view of the heat exchanger according to the fourth embodiment of the present invention as viewed from one header side.

FIG. 15 is a sectional side view of a heat exchanger according to a fifth embodiment of the present invention as viewed from one header side.

FIG. 16 is a sectional side view of a heat exchanger according to a fifth embodiment of the present invention as viewed from one header side.

FIG. 17 is a sectional side view of a heat exchanger according to a sixth embodiment of the present invention as viewed from one header side.

FIG. 18 is a sectional side view of the heat exchanger according to the sixth embodiment of the present invention as viewed from one header side.

FIG. 19 is a sectional side view of a heat exchanger according to a seventh embodiment of the present invention as viewed from one header side.

FIG. 20 is a sectional side view of a heat exchanger according to a seventh embodiment of the present invention as viewed from one header side.

FIG. 21 is a sectional side view of a heat exchanger according to an eighth embodiment of the present invention as viewed from one header side.

FIG. 22 is a sectional side view of a heat exchanger according to an eighth embodiment of the present invention as viewed from one header side.

FIG. 23 is a sectional side view of a heat exchanger according to a ninth embodiment of the present invention as viewed from one header side.

FIG. 24 is a sectional side view of a heat exchanger according to a ninth embodiment of the present invention as viewed from one header side.

FIG. 25 is a cross-sectional side view of the heat exchanger according to the tenth embodiment of the present invention as viewed from one header side.

FIG. 26 is a sectional side view of the heat exchanger according to the tenth embodiment of the present invention as viewed from one header side.

FIG. 27 is a sectional side view of a heat exchanger according to an eleventh embodiment of the present invention as viewed from one header side.

FIG. 28 is a sectional view of a heat exchanger according to a twelfth embodiment of the present invention.

29 is a sectional side view of the heat exchanger shown in FIG. 26 as seen from one header.

30 is a sectional side view of the heat exchanger shown in FIG. 26 as viewed from one header.

FIG. 31 is a diagram showing a modified example of the heat exchanger according to the twelfth embodiment of the present invention.

FIG. 32 is a sectional side view of a heat exchanger according to a thirteenth embodiment of the present invention as viewed from one header side.

FIG. 33 is a sectional side view of a heat exchanger according to a thirteenth embodiment of the present invention as viewed from one header side.

FIG. 34 is a sectional side view of a heat exchanger according to a fourteenth embodiment of the present invention as viewed from one header side.

FIG. 35 is a sectional side view of a heat exchanger according to a fourteenth embodiment of the present invention as viewed from one header side.

FIG. 36 is a sectional side view of a heat exchanger according to a fifteenth embodiment of the present invention as viewed from one header side.

FIG. 37 is a sectional side view of a heat exchanger according to a fifteenth embodiment of the present invention as viewed from one header side.

FIG. 38 is a sectional view of a heat exchanger according to a sixteenth embodiment of the present invention as seen from one header side.

FIG. 39 is a view showing a header shape of a conventional heat exchanger.

FIG. 40 is a diagram showing a header shape of the heat exchanger according to the first embodiment.

FIG. 41 is a graph showing the flow rate ratio of the refrigerant liquid flowing into the inflow heat transfer tube during evaporation when the refrigerant flows from the lower side to the upper side in the heat exchanger of the first embodiment and the conventional heat exchanger. is there.

42 is a graph showing a flow rate ratio of a refrigerant liquid flowing into a heat transfer tube at the time of condensation when the refrigerant flows from the upper side to the lower side in the heat exchanger of the first embodiment and the conventional heat exchanger. FIG. is there.

FIG. 43 is a diagram showing a header shape of the heat exchanger according to the third embodiment.

FIG. 44 is a graph showing a flow rate ratio of the refrigerant liquid flowing into the heat transfer pipe on the outflow side at the time of evaporation in the heat exchanger of the third embodiment and the conventional heat exchanger.

FIG. 45 is a graph showing the flow rate ratio of the refrigerant liquid flowing into the condensing outflow side heat transfer tube during condensation in the heat exchanger of the third embodiment and the conventional heat exchanger.

FIG. 46 is a diagram showing a header shape of the heat exchanger according to the twelfth embodiment.

FIG. 47 is a graph showing the flow rate ratio of the refrigerant liquid flowing into the outflow side heat transfer tube during evaporation in the heat exchanger of Embodiment 12 and the conventional heat exchanger.

FIG. 48 is a graph showing a flow rate ratio of the refrigerant liquid flowing into the condensing outflow side heat transfer tube during condensation in the heat exchanger of Embodiment 12 and the conventional heat exchanger.

FIG. 49 is a view showing a schematic cross section of a conventional heat exchanger.

50 is a cross-sectional side view of the heat exchanger shown in FIG. 43 as viewed from one header side.

51 is a schematic cross-sectional view showing the distribution of the refrigerant gas and the refrigerant liquid passing through one header at the time of evaporation in the heat exchanger shown in FIG. 43.

52 is a schematic cross-sectional view showing the distribution of the refrigerant gas and the refrigerant liquid passing through one header at the time of condensation in the heat exchanger shown in FIG. 43.

[Explanation of symbols]

1 fin, 2 heat transfer tube group, 2a 1st heat transfer tube group, 2b
Second heat transfer tube group, 2c hairpin, first header, 3
a, 3b, 3c, 3d, 3e chamber, 3f first flow port,
3g 2nd distribution port, 4th header, 4a, 4b, 4
c, 4d chamber, 5 partition plates, 6 partition plates, 8 air,
9 refrigerant gas, 10 refrigerant liquid, 11 passage walls, 14 U
V-shaped pipe, 15a, 15b passage wall, 15aa throttle passage, 15b passage wall, 15ba throttle passage, 16a passage wall, 16aa throttle passage, 16b passage wall, 16ba
Throttle passage, 21 copper piping, 21a throttle passage, 21b
Throttle passage.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Masahiro Nakayama             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Akira Ishibashi             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd.

Claims (8)

[Claims] 1. An inflow-side heat transfer tube group for allowing a refrigerant to flow into a chamber defined inside a header, and an outflow-side heat transfer tube group for allowing a refrigerant to flow out of the chamber, wherein the inflow-side heat transfer tube group is provided. A heat exchanger configured to allow a refrigerant to pass through the chamber to the outflow-side heat transfer tube group, wherein a throttle is provided between a connection portion of the inflow-side heat transfer tube group and a connection portion of the outflow-side heat transfer tube group in the chamber. A heat exchanger having a passage. 2. A passage wall having a throttle passage is interposed between a connecting portion of the inflow side heat transfer tube group and a connecting portion of the outflow side heat transfer tube group in the chamber. The heat exchanger described in. 3. The heat exchanger according to claim 1, wherein the opening area of the throttle passage is increased as the degree of dryness of the passing refrigerant increases. 4. The chamber is formed in such a manner that a connection portion of the evaporation-side outflow side heat transfer tube group in which the refrigerant flows out at the time of evaporation is narrower than a connection portion of an evaporation-time inflow side heat transfer tube group into which the refrigerant flows at the time of evaporation. The heat exchanger according to any one of claims 1 to 3, wherein the throttle passage is provided at a position on the leeward side of the partition. 5. The chamber is configured such that a connecting portion of a condensing outflow side heat transfer tube group in which a refrigerant flows out at the time of condensation is narrower than a connecting portion of a condensing inflow side heat transfer tube group into which a refrigerant flows at the time of condensing. The heat exchanger according to any one of claims 1 to 3, wherein the throttle passage is provided at a position on the windward side while being partitioned. 6. A condensing outflow side heat transfer tube group in which the chamber is partitioned in a mode in which each connecting portion of the inflow side heat transfer tube group and the outflow side heat transfer tube group is narrowed and a refrigerant flows out at the time of condensation. The condensing inflow throttle passage reaching the connecting portion is provided on the windward side, and the evaporating inflow throttle passage reaching the connecting portion of the evaporating outflow side heat transfer tube group where the refrigerant flows out at the time of evaporation is provided on the leeward side. It comprised, The heat exchanger as described in any one of Claims 1-3. 7. The heat exchange according to claim 6, wherein the opening area of the inflow throttle passage through which the refrigerant flowing against the gravity flows is set larger than the opening area of the inflow throttle passage through which the refrigerant flows out. vessel. 8. The heat exchanger according to claim 1, wherein the throttle passage is formed by using a pipe.