JPWO2020012548A1 - Heat exchanger, heat exchanger unit and refrigeration cycle equipment - Google Patents

Abstract

The heat exchanger is arranged between the first heat transfer tube, the second heat transfer tube, the first heat transfer tube and the second heat transfer tube, and is adjacent to both the first heat transfer tube and the second heat transfer tube via a gap. A matching third heat transfer tube is provided, and a heat transfer fin for connecting the first heat transfer tube and the third heat transfer tube is not provided between the first heat transfer tube and the third heat transfer tube, and the second heat transfer tube is provided. No heat transfer fins for connecting the second heat transfer tube and the third heat transfer tube are provided between the heat transfer tube and the third heat transfer tube, and the first heat transfer tube, the second heat transfer tube, and the third heat transfer tube are not provided. Has a first end, a second end, and a third end on the upstream side in the flow of air, and the first end and the third end are separated by a first interval. The second end and the third end are separated by a second interval, and the first interval is wider than the second interval.

Description

The present invention relates to a heat exchanger having a plurality of heat transfer tubes, a heat exchanger unit including a heat exchanger, and a refrigeration cycle device including a heat exchanger unit.

Patent Document 1 describes a finless heat exchanger for an air conditioner including a plurality of flat tubes. In this finless heat exchanger for an air conditioner, a plurality of flat tubes are arranged so that the major axis direction of each of the flat tubes is substantially parallel to the air flow. Further, the plurality of flat tubes are arranged side by side in a row at equal intervals in a direction intersecting the direction of air flow.

Japanese Unexamined Patent Publication No. 2009-14510

In a finless heat exchanger as described in Patent Document 1, heat transfer tubes are arranged at a higher density than a heat exchanger provided with heat transfer fins in order to secure a heat transfer area with air. Often. If the heat transfer tubes are arranged at a high density, when the finless heat exchanger operates as an evaporator, the air passage is likely to be blocked due to frost formation. Therefore, the finless heat exchanger has a problem that the heat exchange performance may be sharply deteriorated due to the blockage of the air passage.

The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle device capable of preventing a sudden decrease in heat exchange performance. And.

The heat exchanger according to the present invention is arranged between the first heat transfer tube, the second heat transfer tube arranged in parallel with the first heat transfer tube, and the first heat transfer tube and the second heat transfer tube. A third heat transfer tube that is adjacent to both the first heat transfer tube and the second heat transfer tube via a gap is provided, and the first heat transfer tube is located between the first heat transfer tube and the third heat transfer tube. A heat transfer fin for connecting the heat transfer tube and the third heat transfer tube is not provided, and the second heat transfer tube and the third heat transfer tube are between the second heat transfer tube and the third heat transfer tube. The first heat transfer tube, the second heat transfer tube, and the third heat transfer tube are provided with the first heat transfer tube, the second heat transfer tube, and the third heat transfer tube on the upstream side of the first end portion, the second end portion, and the third heat transfer tube. Each has a third end portion, the first end portion and the third end portion are separated by a first interval, and the second end portion and the third end portion are separated by a second interval. The first interval is wider than the second interval.
Further, the heat exchanger unit according to the present invention includes a heat exchanger according to the present invention and a blower that blows air to the heat exchanger.
Further, the refrigeration cycle apparatus according to the present invention includes a heat exchanger unit according to the present invention.

In the present invention, the space between the second end and the third end, which are relatively narrow, is blocked by frost before the space between the first end and the third end, which are relatively wide. Occurs. As a result, even if the air passage between the second heat transfer tube and the third heat transfer tube is blocked by frost, the air path between the first heat transfer tube and the third heat transfer tube is secured. Therefore, according to the present invention, it is possible to prevent a sudden decrease in the heat exchange performance of the heat exchanger.

It is a perspective view which shows the schematic structure of the heat exchanger 20 which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the structure of the heat exchanger 20 which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the structure of the heat exchanger 20 which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the structure of the heat exchanger 20 which concerns on Embodiment 3 of this invention. It is a graph which shows the relationship between the position and temperature in the air flow direction of the heat exchanger 20 which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the modification 1 of the structure of the heat exchanger 20 which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the modification 2 of the structure of the heat exchanger 20 which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the structure of the heat exchanger 20 which concerns on Embodiment 4 of this invention. It is a circuit diagram which shows the structure of the refrigeration cycle apparatus which concerns on Embodiment 5 of this invention.

Embodiment 1.
The heat exchanger according to the first embodiment of the present invention will be described. FIG. 1 is a perspective view showing a schematic configuration of the heat exchanger 20 according to the present embodiment. The vertical direction in FIG. 1 represents a direction parallel to the direction of gravity. As shown in FIG. 1, the heat exchanger 20 includes a first distributor 21, a second distributor 22 arranged to face the first distributor 21, a first distributor 21 and a second distributor 22. It has a plurality of heat transfer tubes 30 arranged between the heat transfer tubes 30 and the heat transfer tubes 30. The heat exchanger 20 is an air heat exchanger that exchanges heat between the internal fluid flowing through the heat transfer tube 30 and air. In FIG. 1, the air flow direction is indicated by a white arrow. When the heat exchanger 20 constitutes a part of the refrigeration cycle device, a refrigerant is used as the internal fluid flowing through the heat transfer tube 30. The heat transfer tube 30 is formed by using a metal material having high thermal conductivity such as aluminum, copper or brass.

Since the vertical flow type heat exchanger 20 is illustrated in the present embodiment, the heat exchanger 20 is installed so that each of the plurality of heat transfer tubes 30 extends in the vertical direction along the direction of gravity. .. The plurality of heat transfer tubes 30 are arranged in parallel in the horizontal direction which is substantially perpendicular to both the direction of gravity and the direction of air flow. Hereinafter, the direction in which each of the plurality of heat transfer tubes 30 extends may be referred to as the extension direction of the heat transfer tubes 30. The extending direction of the heat transfer tube 30 is the vertical direction of FIG. 1, that is, the direction parallel to the gravitational direction. Further, the direction in which the plurality of heat transfer tubes 30 are arranged in parallel may be referred to as the parallel direction of the plurality of heat transfer tubes 30. The parallel direction of the plurality of heat transfer tubes 30 is the left-right direction of FIG. 2, which will be described later, and usually coincides with the longitudinal direction of the first distributor 21 and the longitudinal direction of the second distributor 22.

The upper ends of each of the plurality of heat transfer tubes 30 are connected to the first distributor 21. The lower ends of each of the plurality of heat transfer tubes 30 are connected to the second distributor 22. A gap that serves as an air passage for air is formed between two heat transfer tubes 30 that are adjacent to each other among the plurality of heat transfer tubes 30. No heat transfer fins are provided between the two heat transfer tubes 30 adjacent to each other. That is, the heat exchanger 20 is a finless type heat exchanger. Since no heat transfer fins are provided between the two heat transfer tubes 30 adjacent to each other, the plurality of heat transfer tubes 30 are mechanically connected to each other only via the first distributor 21 and the second distributor 22. Has been done. Further, the plurality of heat transfer tubes 30 are substantially thermally connected to each other only via the first distributor 21 and the second distributor 22.

In the present embodiment, as the heat transfer tube 30, a flat tube having a flat cross-sectional shape in one direction is used. Hereinafter, the major axis direction of the flat tube in the cross section perpendicular to the extension direction of the flat tube may be simply referred to as the major axis direction of the flat tube. When a flat tube is used as the heat transfer tube 30, the major axis direction of the flat tube may be referred to as the major axis direction of the heat transfer tube 30. The heat transfer tube 30 is provided so that the major axis direction of the heat transfer tube 30 is parallel to the air flow direction. Inside the heat transfer tube 30, a plurality of fluid passages 40 arranged in parallel along the major axis direction of the heat transfer tube 30 are formed (see FIG. 2).

FIG. 2 is a cross-sectional view showing the configuration of the heat exchanger 20 according to the present embodiment. FIG. 2 shows a configuration in which an intermediate portion of the heat exchanger 20 in the vertical direction is cut in a horizontal plane. In FIG. 2, the air flow direction is downward. The plurality of downward arrows in FIG. 2 schematically represent the magnitude of the air flow direction and the air flow velocity. As shown in FIG. 2, the plurality of heat transfer tubes 30 are arranged so that the major axis directions of the heat transfer tubes 30 are parallel to each other. The arrangement intervals of the plurality of heat transfer tubes 30 are different at least in part. In other words, the arrangement interval of the plurality of heat transfer tubes 30 is relatively narrow at least in part and relatively wide in at least part. In the configuration shown in FIG. 2, the plurality of heat transfer tubes 30 are arranged so that relatively wide arrangement intervals and relatively narrow arrangement intervals are alternately repeated in the parallel direction of the plurality of heat transfer tubes 30.

The arrangement interval of the plurality of heat transfer tubes 30 will be described by paying attention to the first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c, which are a part of the plurality of heat transfer tubes 30. The first heat transfer tube 30a is one of a plurality of heat transfer tubes 30. The second heat transfer tube 30b is a heat transfer tube 30 arranged in parallel with the first heat transfer tube 30a. The third heat transfer tube 30c is arranged between the first heat transfer tube 30a and the second heat transfer tube 30b, is adjacent to the first heat transfer tube 30a through the gap 41, and is adjacent to the first heat transfer tube 30a through the gap 42, and the second heat transfer tube 30b The heat transfer tubes 30 are adjacent to each other. That is, in the parallel direction of the plurality of heat transfer tubes 30, the first heat transfer tube 30a, the third heat transfer tube 30c, and the second heat transfer tube 30b are arranged in this order. The gap 41 serves as an air passage between the first heat transfer tube 30a and the third heat transfer tube 30c. The gap 42 serves as an air passage between the second heat transfer tube 30b and the third heat transfer tube 30c.

At least, a heat transfer fin for connecting the first heat transfer tube 30a and the third heat transfer tube 30c is not provided between the first heat transfer tube 30a and the third heat transfer tube 30c. At least, a heat transfer fin for connecting the third heat transfer tube 30c and the second heat transfer tube 30b is not provided between the third heat transfer tube 30c and the second heat transfer tube 30b.

The first heat transfer tube 30a has a first end portion 31a located on the upstream side, that is, on the windward side in the flow of air, as an end portion in the major axis direction of the first heat transfer tube 30a. The second heat transfer tube 30b has a second end portion 31b located on the windward side as an end portion in the major axis direction of the second heat transfer tube 30b. The third heat transfer tube 30c has a third end portion 31c located on the windward side as an end portion in the major axis direction of the third heat transfer tube 30c. In the parallel direction of the plurality of heat transfer tubes 30, the first end portion 31a, the third end portion 31c, and the second end portion 31b are arranged in this order. The first end portion 31a and the third end portion 31c are separated by the first interval D1. The second end portion 31b and the third end portion 31c are separated by the second interval D2. The first interval D1 is wider than the second interval D2 (D1> D2). Here, it is assumed that both the first interval D1 and the second interval D2 are measured in parallel with the parallel direction of the plurality of heat transfer tubes 30.

Further, the first heat transfer tube 30a has a fourth end portion 32a located on the downstream side, that is, on the leeward side in the air flow, as the end portion in the major axis direction of the first heat transfer tube 30a. The second heat transfer tube 30b has a fifth end portion 32b located on the leeward side as an end portion in the major axis direction of the second heat transfer tube 30b. The third heat transfer tube 30c has a sixth end portion 32c located on the leeward side as an end portion in the major axis direction of the third heat transfer tube 30c. In the parallel direction of the plurality of heat transfer tubes 30, the fourth end portion 32a, the sixth end portion 32c, and the fifth end portion 32b are arranged in this order. Since the major axis directions of the first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c are parallel to each other, the distance between the fourth end portion 32a and the sixth end portion 32c is equal to the first distance D1. , The distance between the fifth end 32b and the sixth end 32c is equal to the second distance D2.

When the heat exchanger 20 is under conditions where frost can occur, the frost 50 tends to adhere to the windward side of the plurality of heat transfer tubes 30. In the present embodiment, the first interval D1 between the first end 31a of the first heat transfer tube 30a and the third end 31c of the third heat transfer tube 30c and the second end 31b of the second heat transfer tube 30b The second interval D2 between the third heat transfer tube 30c and the third end portion 31c satisfies the relationship of D1> D2. The frost 50 adhering to the heat transfer tubes 30 grows at a substantially constant growth rate regardless of the distance between the adjacent heat transfer tubes 30. As a result, between the second end 31b and the third end 31c, which are relatively narrow in spacing, frost precedes between the first end 31a and the third end 31c, which are relatively wide in spacing. Occlusion by 50 occurs. When the space between the second end 31b and the third end 31c is blocked by the frost 50, the block between the first end 31a and the third end 31c is not caused by the frost 50. Therefore, even if the air passage between the second heat transfer tube 30b and the third heat transfer tube 30c is blocked by the frost 50, the air passage between the first heat transfer tube 30a and the third heat transfer tube 30c is secured. To. That is, in the present embodiment, even if a part of the air passages of the heat exchanger 20 is blocked by the frost 50, another air passage is secured. Therefore, in the present embodiment, since it is possible to prevent all the air passages of the heat exchanger 20 from being blocked, it is possible to prevent the heat exchange performance of the heat exchanger 20 from being suddenly deteriorated due to the blockage of the air passages. Can be done.

Further, in the example shown in FIG. 2, in the plurality of heat transfer tubes 30, the relatively wide first interval D1 and the relatively narrow second interval D2 are alternately repeated in the parallel direction of the plurality of heat transfer tubes 30. Are arranged. Therefore, in the parallel direction of the plurality of heat transfer tubes 30, the portion where the blockage due to the frost 50 occurs first and the portion where the air passage is secured can be evenly dispersed. Therefore, even if a part of the air passages of the heat exchanger 20 is blocked, the deterioration of the heat exchange performance can be suppressed.

In this embodiment, a plurality of heat transfer tubes 30 are extended in the vertical direction. Further, in the present embodiment, the heat transfer fins are not provided between the two heat transfer tubes 30 adjacent to each other. Therefore, when the frost 50 is melted by the defrosting operation of the refrigeration cycle apparatus or the like, the melted water flows down through the heat transfer tube 30 due to its own weight and is drained without being hindered by the heat transfer fins. Similarly, when the heat exchanger 20 functions as an evaporator of the refrigeration cycle device, the condensed water generated on the surface of the heat transfer tube 30 also flows down through the heat transfer tube 30 due to its own weight and is hindered by the heat transfer fins. It is drained without water. Therefore, according to the present embodiment, the drainage property of the heat exchanger 20 can be improved.

As described above, the heat exchanger 20 according to the present embodiment includes a first heat transfer tube 30a, a second heat transfer tube 30b arranged in parallel with the first heat transfer tube 30a, and a first heat transfer tube 30a. A third heat transfer tube 30c, which is arranged between the second heat transfer tube 30b and is adjacent to both the first heat transfer tube 30a and the second heat transfer tube 30b via gaps 41 and 42, is provided. A heat transfer fin for connecting the first heat transfer tube 30a and the third heat transfer tube 30c is not provided between the first heat transfer tube 30a and the third heat transfer tube 30c. A heat transfer fin for connecting the second heat transfer tube 30b and the third heat transfer tube 30c is not provided between the second heat transfer tube 30b and the third heat transfer tube 30c. The first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c have a first end portion 31a, a second end portion 31b, and a third end portion 31c, respectively, on the upstream side due to the flow of air. The first end portion 31a and the third end portion 31c are separated by the first interval D1. The second end portion 31b and the third end portion 31c are separated by the second interval D2. The first interval D1 is wider than the second interval D2.

According to this configuration, the distance between the second end 31b and the third end 31c, which are relatively narrow, is larger than that between the first end 31a and the third end 31c, which are relatively wide. Blockage due to frost 50 occurs first. Therefore, even if the air passage between the second heat transfer tube 30b and the third heat transfer tube 30c is blocked by the frost 50, the air passage between the first heat transfer tube 30a and the third heat transfer tube 30c is secured. To. Therefore, it is possible to prevent the heat exchange performance of the heat exchanger 20 from being sharply deteriorated due to the blockage of the air passage.

Embodiment 2.
The heat exchanger according to the second embodiment of the present invention will be described. FIG. 3 is a cross-sectional view showing the configuration of the heat exchanger 20 according to the present embodiment. FIG. 3 shows a cross section corresponding to FIG. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. As shown in FIG. 3, in the present embodiment, the arrangement intervals of the windward ends of the plurality of heat transfer tubes 30 are relatively narrow at least in part and relatively in at least part. It's getting wider. Therefore, as in the first embodiment, even if a part of the air passages is blocked by the frost 50, the other air passages are secured. Therefore, the heat exchange performance of the heat exchanger 20 suddenly increases due to the blockage of the air passages. It can be prevented from decreasing.

In the present embodiment, the major axis directions of the two heat transfer tubes 30 adjacent to each other are inclined in opposite directions with respect to the air flow direction. As a result, when viewed along the extending direction of the heat transfer tube 30, the major axis direction of the two heat transfer tubes 30 adjacent to each other is V-shaped or inverted V-shaped.

The first end 31a on the windward side of the first heat transfer tube 30a and the third end 31c on the windward side of the third heat transfer tube 30c are separated by a first interval D1. The second end 31b on the windward side of the second heat transfer tube 30b and the third end 31c on the windward side of the third heat transfer tube 30c are separated by a second interval D2. The point that the first interval D1 and the second interval D2 satisfy the relationship of D1> D2 is the same as that of the first embodiment.

The leeward fourth end 32a of the first heat transfer tube 30a and the leeward sixth end 32c of the third heat transfer tube 30c are separated by a third interval D3. In the present embodiment, the third interval D3 is narrower than the first interval D1 (D3 <D1). That is, the air passage between the first heat transfer tube 30a and the third heat transfer tube 30c is formed so as to be narrower on the leeward side than on the leeward side.

The leeward fifth end 32b of the second heat transfer tube 30b and the leeward sixth end 32c of the third heat transfer tube 30c are separated by a fourth interval D4. In the present embodiment, the fourth interval D4 is wider than the second interval D2 (D4> D2). That is, the air passage between the second heat transfer tube 30b and the third heat transfer tube 30c is formed so as to be wider on the leeward side than on the leeward side.

Comparing the third interval D3 and the fourth interval D4, the fourth interval D4 is, for example, the same as or wider than the third interval D3 (D4 ≧ D3). Here, it is assumed that the third interval D3 and the fourth interval D4 are both measured in parallel with the parallel direction of the plurality of heat transfer tubes 30 as in the case of the first interval D1 and the second interval D2.

As described above, in the heat exchanger 20 according to the present embodiment, the first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c have the fourth end portion 32a on the downstream side due to the flow of air. It has a fifth end 32b and a sixth end 32c, respectively. The fourth end 32a and the sixth end 32c are separated by a third interval D3. The fifth end 32b and the sixth end 32c are separated by a fourth interval D4. The third interval D3 is narrower than the first interval D1. The fourth interval D4 is wider than the second interval D2.

According to this configuration, the air passage between the first heat transfer tube 30a and the third heat transfer tube 30c, which is less likely to be blocked by frost formation, is formed so as to be narrower on the leeward side than on the windward side. As a result, the wind speed of the air flowing through the air passage between the first heat transfer tube 30a and the third heat transfer tube 30c increases, so that the heat exchange efficiency in the air passage can be increased. Therefore, according to the present embodiment, the heat exchange performance of the heat exchanger 20 can be further improved.

Further, in the present embodiment, the plurality of heat transfer tubes 30 are arranged so that the first interval D1 and the second interval D2 narrower than the first interval D1 are alternately repeated in the parallel direction of the plurality of heat transfer tubes 30. ing. Therefore, in the parallel direction of the plurality of heat transfer tubes 30, the portion where the blockage due to the frost 50 occurs first and the portion where the air passage is secured can be evenly dispersed. Therefore, even if a part of the air passages of the heat exchanger 20 is blocked, the deterioration of the heat exchange performance can be suppressed.

Embodiment 3.
The heat exchanger according to the third embodiment of the present invention will be described. FIG. 4 is a cross-sectional view showing the configuration of the heat exchanger 20 according to the present embodiment. FIG. 4 shows a cross section corresponding to FIG. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. As shown in FIG. 4, the heat transfer tube 30 of the present embodiment is formed on the tube portion 33, the plate-shaped fin portion 34 formed on the windward side of the tube portion 33, and the leeward side of the tube portion 33. It has a plate-shaped fin portion 35 and. The tube portion 33 is formed by a flat tube.

In the cross section perpendicular to the extending direction of the heat transfer tube 30, the fin portion 34 extends from the windward end of the tube 33 toward the windward side. The fin portion 34 also extends along the extending direction of the heat transfer tube 30 perpendicular to the paper surface of FIG. The fin portion 34 has, for example, a rectangular flat plate shape having a long side along the extending direction of the heat transfer tube 30. When the pipe portion 33 is formed of a flat pipe, the fin portion 34 has a plate thickness dimension smaller than the minor diameter dimension of the flat pipe. The fluid passage 40 is not formed in the fin portion 34.

Further, in the cross section perpendicular to the extending direction of the heat transfer tube 30, the fin portion 35 extends from the leeward end of the tube 33 toward the leeward side. The fin portion 35 also extends along the extending direction of the heat transfer tube 30 perpendicular to the paper surface of FIG. The fin portion 35 has, for example, a rectangular flat plate shape having a long side along the extending direction of the heat transfer tube 30. When the pipe portion 33 is formed of a flat pipe, the fin portion 35 has a plate thickness dimension smaller than the minor diameter dimension of the flat pipe. The fluid passage 40 is not formed in the fin portion 35.

In the cross section shown in FIG. 4, the major axis direction of the flat tube portion 33, the extending direction of the fin portion 34, and the extending direction of the fin portion 35 are parallel. Further, the plurality of heat transfer tubes 30 are arranged so that the major axis direction of each tube portion 33 is parallel and the major axis direction of each tube portion 33 is parallel to the air flow direction. The arrangement interval of the plurality of heat transfer tubes 30 is relatively narrow at least in a part and relatively wide in at least a part.

The tube portion 33 may be formed by a circular tube instead of a flat tube. Since the fin portion 34 and the fin portion 35 are a part of the heat transfer tube 30, the heat transfer tube 30 has a flat cross-sectional shape in one direction even when the tube portion 33 is formed by a circular tube. Therefore, even when the tube portion 33 is formed by a circular tube, the heat transfer tube 30 can be regarded as a flat tube as a whole. When the pipe portion 33 is formed by a circular pipe, the fin portion 34 and the fin portion 35 have, for example, a plate thickness dimension smaller than the outer diameter dimension of the circular pipe.

Since the heat transfer tube 30 has the fin portions 34 and 35, the heat transfer area between the heat transfer tube 30 and the air can be increased, so that the heat exchange performance of the heat exchanger 20 can be further improved. In the present embodiment, the fin portion 35 on the leeward side can be omitted.

The tube portion 33, the fin portion 34, and the fin portion 35 of each heat transfer tube 30 may be integrally molded using the same material, or may be formed as separate members. It is desirable that the fin portion 34 and the fin portion 35 are formed by using a metal material having high thermal conductivity such as aluminum, copper or brass.

FIG. 5 is a graph showing the relationship between the position of the heat exchanger 20 according to the present embodiment in the air flow direction and the temperature. The horizontal axis represents the position in the air flow direction, and the vertical axis represents the temperature. The positions on the horizontal axis correspond to the positions of the two types of heat transfer tubes 30 shown below the horizontal axis. The white arrows shown below the horizontal axis indicate the direction of air flow. The position P1 corresponds to a position on the windward side of the heat transfer tube 30. That is, the temperature T1 at the position P1 corresponds to the representative temperature of the air before flowing into the heat exchanger 20. The position P2 corresponds to the position of the windward end of the heat transfer tube 30 including the fin portion 34. That is, the temperature T2 at the position P2 corresponds to the temperature of the front edge of the fin portion 34. The position P3 corresponds to the position of the windward end of the heat transfer tube 30 having no fin portion 34 and the position of the windward end of the tube portion 33 in the heat transfer tube 30 having the fin portion 34. That is, the temperature T3 at the position P3 corresponds to the temperature of the front edge of the heat transfer tube 30 in the heat transfer tube 30 not provided with the fin portion 34, and the temperature of the windward end portion of the tube portion 33 in the heat transfer tube 30 provided with the fin portion 34. Corresponds to. Here, if the temperatures of the internal fluids flowing through the heat transfer tube 30 are equal, the temperature T3 of the heat transfer tube 30 having no fin portion 34 and the temperature T3 of the heat transfer tube 30 having the fin portion 34 are equal.

As shown in FIG. 5, the front edge temperature T2 of the fin portion 34 is higher than the front edge temperature T3 of the heat transfer tube 30 not provided with the fin portion 34. Therefore, the temperature difference ΔT1 between the representative temperature T1 of air and the front edge temperature T2 of the fin portion 34 is based on the temperature difference ΔT2 between the representative temperature T1 of air and the front edge temperature T3 of the heat transfer tube 30 not provided with the fin portion 34. Also becomes smaller. Therefore, in the heat transfer tube 30 provided with the fin portion 34, the temperature difference ΔT1 becomes small, so that frost formation is less likely to occur than in the heat transfer tube 30 not provided with the fin portion 34. Further, in the heat transfer tube 30 provided with the fin portion 34, the length of the heat transfer portion in the air flow direction can be lengthened, so that even if frost is formed at the windward end of the fin portion 34, the heat transfer portion is formed. The heat transfer part on the leeward side of the frost part can be effectively used. Therefore, since the heat transfer tube 30 has the fin portion 34, it is possible to prevent frost formation in the heat exchanger 20 and improve the heat exchange performance of the heat exchanger 20.

Returning to FIG. 4, when the heat transfer tube 30 has the fin portion 34, the first end portion 31a of the first heat transfer tube 30a, the second end portion 31b of the second heat transfer tube 30b, and the third end of the third heat transfer tube 30c. Each of the portions 31c is located at the windward end of the fin portion 34. In the present embodiment, as in the first embodiment, the first interval D1 between the first end portion 31a and the third end portion 31c and the space between the second end portion 31b and the third end portion 31c The second interval D2 satisfies the relationship of D1> D2. As a result, between the second end 31b and the third end 31c, which are relatively narrow in spacing, frost precedes between the first end 31a and the third end 31c, which are relatively wide in spacing. Occlusion by 50 occurs. Therefore, according to the present embodiment, the same effect as that of the first embodiment can be obtained.

FIG. 6 is a cross-sectional view showing a modified example 1 of the configuration of the heat exchanger 20 according to the present embodiment. As shown in FIG. 6, in this modification, the major axis directions of the two heat transfer tubes 30 adjacent to each other are inclined in opposite directions with respect to the air flow direction. The first distance D1 between the first end 31a and the third end 31c and the second distance D2 between the second end 31b and the third end 31c satisfy the relationship D1> D2. ing. Therefore, according to this modification, the same effect as that of the first embodiment can be obtained.

When the heat transfer tube 30 has the fin portion 35, the fourth end portion 32a of the first heat transfer tube 30a, the fifth end portion 32b of the second heat transfer tube 30b, and the sixth end portion 32c of the third heat transfer tube 30c are all included. , Located at the leeward end of the fin portion 35. In this modification, as in the second embodiment, the third interval D3 between the fourth end portion 32a and the sixth end portion 32c is narrower than the first interval D1 (D3 <D1). Further, the fourth interval D4 between the fifth end portion 32b and the sixth end portion 32c is wider than the second interval D2 (D4> D2). Therefore, according to this modification, the same effect as that of the second embodiment can be obtained.

FIG. 7 is a cross-sectional view showing a modified example 2 of the configuration of the heat exchanger 20 according to the present embodiment. As shown in FIG. 7, in this modification, the plurality of heat transfer tubes 30 are arranged so that the major axis direction of the tube portion 33 is parallel to the air flow direction. That is, the tube portions 33 of the plurality of heat transfer tubes 30 are arranged in parallel with each other. Further, the plurality of heat transfer tubes 30 are arranged so that the tube portions 33 are arranged at equal intervals. The fin portions 34 on the windward side of the two heat transfer tubes 30 adjacent to each other are inclined in opposite directions with respect to the air flow direction. As a result, when viewed along the extending direction of the heat transfer tubes 30, the fin portions 34 of the two heat transfer tubes 30 adjacent to each other have a V-shape or an inverted V-shape. The fin portion 35 on the leeward side of the heat transfer tube 30 extends parallel to the major axis direction of the tube portion 33.

The first interval D1 between the first end 31a of the first heat transfer tube 30a and the third end 31c of the third heat transfer tube 30c, and the second end 31b and the third heat transfer tube 30c of the second heat transfer tube 30b. The second interval D2 with the third end portion 31c of the above satisfies the relationship of D1> D2. As a result, between the second end 31b and the third end 31c, which are relatively narrow in spacing, frost precedes between the first end 31a and the third end 31c, which are relatively wide in spacing. Occlusion by 50 occurs. Therefore, according to this modification, the same effect as that of the first embodiment can be obtained.

The third interval D3 between the fourth end 32a and the sixth end 32c of the first heat transfer tube 30a is narrower than the first interval D1 (D3 <D1). Further, the fourth interval D4 between the fifth end portion 32b and the sixth end portion 32c is wider than the second interval D2 (D4> D2). Therefore, according to this modification, the same effect as that of the second embodiment can be obtained.

As described above, in the heat exchanger 20 according to the present embodiment, each of the first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c has a plate shape extending upstream due to the flow of air. It has a fin portion 34 of the above. According to this configuration, the temperature difference ΔT1 between the temperature T1 of the air flowing into the heat exchanger 20 and the temperature T2 of the front edge of the fin portion 34 can be reduced, so that frost formation is less likely to occur in the heat exchanger 20. can do.

Embodiment 4.
The heat exchanger according to the fourth embodiment of the present invention will be described. FIG. 8 is a cross-sectional view showing the configuration of the heat exchanger 20 according to the present embodiment. FIG. 8 shows a cross section corresponding to FIG. The components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. As shown in FIG. 8, a heat transfer promoting unit 36 for promoting heat transfer is provided on each facing surface of two heat transfer tubes 30 adjacent to each other with a relatively narrow interval among the plurality of heat transfer tubes 30. Has been done. For example, a heat transfer promoting unit 36 is provided on each facing surface of the second heat transfer tube 30b and the third heat transfer tube 30c. On the other hand, the heat transfer promoting unit 36 is not provided on the opposite surfaces of the two heat transfer tubes 30 adjacent to each other with a relatively wide interval. For example, the heat transfer promoting section 36 is not provided on the opposite surfaces of the first heat transfer tube 30a and the third heat transfer tube 30c. The heat transfer promoting portion 36 is formed by, for example, a groove-shaped concave portion extending along the extending direction of the heat transfer tube 30, a linear convex portion extending along the extending direction of the heat transfer tube 30, or the like. When the heat transfer tube 30 has a tube portion 33, a fin portion 34, and a fin portion 35, the heat transfer promotion portion 36 may be provided in each of the tube portion 33, the fin portion 34, and the fin portion 35.

As described above, in the heat exchanger 20 according to the present embodiment, the heat transfer promoting unit for promoting heat transfer is provided on the facing surfaces of the second heat transfer tube 30b and the third heat transfer tube 30c facing each other. 36 is provided. A heat transfer promoting unit 36 is not provided on each of the facing surfaces of the first heat transfer tube 30a and the third heat transfer tube 30c facing each other. According to this configuration, heat exchange between air and the internal fluid is further promoted in the air passage between the second heat transfer tube 30b and the third heat transfer tube 30c. Therefore, between the second end portion 31b and the third end portion 31c, frost formation can be more positively generated and the growth of the frost 50 can be promoted, so that the first end portion 31a and the third end portion 31a and the third end portion can be promoted. Frost formation and growth of frost 50 can be relatively suppressed with and from 31c.

In the present embodiment, the heat transfer promoting unit 36 is not provided on the facing surfaces of the two heat transfer tubes 30 adjacent to each other with a relatively wide interval, but the heat transfer promoting is also promoted on these facing surfaces. The portion 36 may be provided. For example, a heat transfer promoting unit 36 may be provided on each of the facing surfaces of the first heat transfer tube 30a and the third heat transfer tube 30c facing each other. By providing the heat transfer promoting portion 36 on these facing surfaces as well, the heat exchange performance of the heat exchanger 20 can be further improved.

Embodiment 5.
The heat exchanger unit and the refrigeration cycle apparatus according to the fifth embodiment of the present invention will be described. FIG. 9 is a circuit diagram showing the configuration of the refrigeration cycle device 100 according to the present embodiment. In the present embodiment, an air conditioner is exemplified as the refrigeration cycle device 100. As shown in FIG. 9, the refrigeration cycle device 100 has a refrigeration cycle circuit 10 for circulating a refrigerant. The refrigeration cycle circuit 10 has a configuration in which a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, an expansion valve 14, and an indoor heat exchanger 15 are connected in an annular shape via a refrigerant pipe. Further, the refrigeration cycle device 100 includes a blower 16 that blows air to the outdoor heat exchanger 13 and a blower 17 that blows air to the indoor heat exchanger 15. In the refrigeration cycle apparatus 100, the compressor 11 is driven to execute a refrigeration cycle in which the refrigerant circulates in the refrigeration cycle circuit 10 while changing the phase. In the outdoor heat exchanger 13, heat exchange is performed between the air blown by the blower 16 and the refrigerant which is an internal fluid. In the indoor heat exchanger 15, heat exchange is performed between the air blown by the blower 17 and the refrigerant which is an internal fluid.

As the refrigerant filled in the refrigeration cycle circuit 10, a refrigerant such as R410A, R32 or HFO-1234yf can be used. As the refrigerating machine oil used in the compressor 11, various refrigerating machine oils such as mineral oil type, alkylbenzene oil type, ester oil type, ether oil type and fluorine oil type may be used regardless of the compatibility with the refrigerant. it can.

As the outdoor heat exchanger 13, the heat exchanger 20 according to any one of the first to fourth embodiments is used. The outdoor heat exchanger 13 is installed in the outdoor unit 110 so that each of the plurality of heat transfer tubes 30 extends in the vertical direction. Further, as the indoor heat exchanger 15, any of the heat exchangers 20 of the first to fourth embodiments can be used. In this case, the indoor heat exchanger 15 is installed in the indoor unit 120 so that each of the plurality of heat transfer tubes 30 extends in the vertical direction.

The refrigeration cycle device 100 has an outdoor unit 110 and an indoor unit 120. The outdoor unit 110 includes a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, an expansion valve 14, and a blower 16. The indoor unit 120 includes an indoor heat exchanger 15 and a blower 17. Both the outdoor unit 110 and the indoor unit 120 are heat exchanger units that house at least a heat exchanger.

The operation of the refrigeration cycle device 100 will be described by taking a cooling operation as an example. The high-pressure gas refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13 via the four-way valve 12. During the cooling operation, the outdoor heat exchanger 13 functions as a condenser. That is, in the outdoor heat exchanger 13, heat exchange is performed between the refrigerant flowing inside and the outdoor air blown by the blower 16, and the heat of condensation of the refrigerant is dissipated to the outdoor air. As a result, the gas refrigerant that has flowed into the outdoor heat exchanger 13 is condensed into a high-pressure liquid refrigerant.

The liquid refrigerant flowing out of the outdoor heat exchanger 13 is depressurized by the expansion valve 14 to become a low-pressure two-phase refrigerant. The two-phase refrigerant flowing out of the expansion valve 14 flows into the indoor heat exchanger 15. During the cooling operation, the indoor heat exchanger 15 functions as an evaporator. That is, in the indoor heat exchanger 15, heat exchange is performed between the refrigerant flowing inside and the indoor air blown by the blower 17, and the heat of vaporization of the refrigerant is absorbed from the indoor air. As a result, the two-phase refrigerant that has flowed into the indoor heat exchanger 15 evaporates to become a low-pressure gas refrigerant. The gas refrigerant flowing out of the indoor heat exchanger 15 is sucked into the compressor 11 via the four-way valve 12. The gas refrigerant sucked into the compressor 11 is compressed to become a high-pressure gas refrigerant. During the cooling operation, the above refrigeration cycle is continuously and repeatedly executed. Although the description is omitted, during the heating operation, the flow direction of the refrigerant is switched by the four-way valve 12, the outdoor heat exchanger 13 functions as an evaporator, and the indoor heat exchanger 15 functions as a condenser.

As described above, the heat exchanger unit according to the present embodiment includes a heat exchanger 20 and a blower that blows air to the heat exchanger 20. The heat exchanger unit is, for example, an outdoor unit 110 or an indoor unit 120. According to this configuration, it is possible to realize a heat exchanger unit provided with the heat exchanger 20 that can prevent a sudden decrease in heat exchange performance due to blockage of the air passage.

Further, in the heat exchanger unit according to the present embodiment, the heat exchanger 20 is arranged so that each of the first heat transfer tube 30a, the second heat transfer tube 30b, and the third heat transfer tube 30c extends in the vertical direction. There is. According to this configuration, the drainage property of the heat exchanger 20 can be improved in the heat exchanger unit.

Further, the refrigeration cycle device 100 according to the present embodiment includes a heat exchanger unit according to the present embodiment. According to this configuration, it is possible to realize a refrigeration cycle device 100 provided with a heat exchanger 20 capable of preventing a sudden decrease in heat exchange performance due to blockage of the air passage.

In the above-described first to fifth embodiments, the vertical flow type heat exchanger 20 in which the extending direction of the heat transfer tube 30 is parallel to the direction of gravity is given as an example, but the present invention is not limited to this. The present invention can be applied to a cross-flow heat exchanger in which the extension direction of the heat transfer tube 30 is horizontal, or a heat exchanger in which the extension direction of the heat transfer tube 30 is tilted with respect to both the gravity direction and the horizontal direction. ..

Further, in the first to fifth embodiments, the refrigerant is used as an example as the internal fluid flowing through the heat transfer tube 30 of the heat exchanger 20, but the present invention is not limited to this. As the internal fluid flowing through the heat transfer tube 30 of the heat exchanger 20, another fluid containing a liquid such as water or brine can also be used.

Each of the above embodiments and modifications can be implemented in combination with each other.

10 Refrigeration cycle circuit, 11 Compressor, 12 Four-way valve, 13 Outdoor heat exchanger, 14 Expansion valve, 15 Indoor heat exchanger, 16, 17 Blower, 20 Heat exchanger, 21 1st distributor, 22 2nd distributor , 30 heat transfer tube, 30a first heat transfer tube, 30b second heat transfer tube, 30c third heat transfer tube, 31a first end, 31b second end, 31c third end, 32a fourth end, 32b fifth End, 32c 6th end, 33 pipe, 34, 35 fin, 36 heat transfer promotion, 40 fluid passage, 41, 42 gap, 50 frost, 100 refrigeration cycle device, 110 outdoor unit, 120 indoor unit, D1 1st interval, D2 2nd interval, D3 3rd interval, D4 4th interval.

The heat exchanger according to the present invention is arranged between the first heat transfer tube, the second heat transfer tube arranged in parallel with the first heat transfer tube, and the first heat transfer tube and the second heat transfer tube. A plurality of heat transfer tubes arranged in parallel with each other, including a third heat transfer tube adjacent to each of the first heat transfer tube and the second heat transfer tube via a gap, are provided, and the first heat transfer tube and the said A heat transfer fin for connecting the first heat transfer tube and the third heat transfer tube is not provided between the third heat transfer tube, and the second heat transfer tube and the third heat transfer tube are separated from each other. Is not provided with heat transfer fins for connecting the second heat transfer tube and the third heat transfer tube, and the first heat transfer tube, the second heat transfer tube, and the third heat transfer tube are formed by an air flow. It has a first end portion, a second end portion, and a third end portion on the upstream side, respectively, and the first end portion and the third end portion are separated by a first interval, and the second end portion is provided. the said third end section, are separated by a second distance, said first distance, said has wide Kuna' than the second distance, the two heat transfer tubes adjacent to each other among the plurality of heat transfer tubes The heat transfer tubes are separated from each other by the first interval or the second interval so that the first interval and the second interval are alternately repeated in the parallel direction of the plurality of heat transfer tubes. It is an array .
Further, the heat exchanger unit according to the present invention includes a heat exchanger according to the present invention and a blower that blows air to the heat exchanger.
Further, the refrigeration cycle apparatus according to the present invention includes a heat exchanger unit according to the present invention.

Claims (7)

The first heat transfer tube and
The second heat transfer tube arranged in parallel with the first heat transfer tube and
A third heat transfer tube arranged between the first heat transfer tube and the second heat transfer tube and adjacent to both the first heat transfer tube and the second heat transfer tube via a gap, and a third heat transfer tube.
With
A heat transfer fin for connecting the first heat transfer tube and the third heat transfer tube is not provided between the first heat transfer tube and the third heat transfer tube.
A heat transfer fin for connecting the second heat transfer tube and the third heat transfer tube is not provided between the second heat transfer tube and the third heat transfer tube.
The first heat transfer tube, the second heat transfer tube, and the third heat transfer tube have a first end portion, a second end portion, and a third end portion on the upstream side in the flow of air, respectively.
The first end portion and the third end portion are separated from each other at the first interval.
The second end and the third end are separated by a second interval.
The first interval is a heat exchanger wider than the second interval. The first heat transfer tube, the second heat transfer tube, and the third heat transfer tube have a fourth end portion, a fifth end portion, and a sixth end portion on the downstream side in the flow of air, respectively.
The fourth end and the sixth end are separated by a third interval.
The fifth end and the sixth end are separated by a fourth interval.
The third interval is narrower than the first interval,
The heat exchanger according to claim 1, wherein the fourth interval is wider than the second interval. A heat transfer promoting unit for promoting heat transfer is provided on each facing surface of the second heat transfer tube and the third heat transfer tube facing each other.
The heat exchanger according to claim 1 or 2, wherein the heat transfer promoting portion is not provided on the facing surfaces of the first heat transfer tube and the third heat transfer tube facing each other. The first heat transfer tube, the second heat transfer tube, and the third heat transfer tube each have a plate-shaped fin portion extending upstream by the flow of air, according to any one of claims 1 to 3. The heat exchanger described. The heat exchanger according to any one of claims 1 to 4.
A blower that blows air to the heat exchanger and
Heat exchanger unit equipped with. The heat exchanger unit according to claim 5, wherein the heat exchanger is arranged so that each of the first heat transfer tube, the second heat transfer tube, and the third heat transfer tube extends in the vertical direction. A refrigeration cycle apparatus comprising the heat exchanger unit according to claim 5 or 6.

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