JP6414331B2 - Heat exchanger and refrigeration equipment - Google Patents

Description

  The present invention relates to a heat exchanger for cooling and a cooling device including the same.

  In a refrigeration apparatus such as a refrigerator-freezer that circulates air and removes heat with a heat exchanger to cool the inside of a cooling space, moisture contained in the circulated air adheres to the heat exchanger as frost (hereinafter referred to as frost formation). Generally, a lot of frost is generated on the upstream side of the circulating air, and the amount of frost on the downstream side is small. There is a problem that the amount of circulating air in the heat exchanger decreases and the amount of heat exchange decreases due to the amount of frost formation on the upstream side and the air passage being blocked. As a configuration for preventing a decrease in the heat exchange amount, for example, in Patent Document 1, in a fin-and-tube heat exchanger, in order to make it difficult to reduce the air amount at the time of frost formation, Disclosed is a configuration in which the tube arrangement is a grid pattern, the tube arrangement on the downstream side is staggered, and a louver or corrugated processing portion is provided on the fins of the staggered area in order to obtain sufficient freezing capacity. ing. Further, in Patent Document 2, in order to secure the air circulation amount to the downstream side and prevent the reduction of the heat removal amount, the upstream fin interval is made larger than the downstream fin interval, and the upstream side and the downstream side In order to adjust the amount of frost formation on the side, a configuration in which ribs or louvers are formed on the fins is disclosed.

Japanese Utility Model Publication No. 57-196962 JP-A-5-18636

  However, in the techniques disclosed in Patent Documents 1 and 2, the processed parts such as ribs and louvers provided on the fins have a shape that rises in a direction perpendicular to the fin surface, leading to a leading edge effect or disturbance. Since the flow promoting effect is produced, frosting occurs intensively in the processed portion and the vicinity thereof, and there is a problem that the heat exchange amount is reduced due to the air passage blockage and the cooling quality is lowered.

  The present invention was made to solve the above-described problems, and provides a heat exchanger capable of maintaining high cooling quality by preventing air passage blockage due to frost formation, and a refrigerator such as a refrigerator using the heat exchanger. The purpose is to do.

A heat exchanger according to the present invention includes at least two fin rows each including a plurality of fins stacked at intervals, and a pipe that passes through the fins in the stacking direction and through which a refrigerant flows. In the heat exchanger for exchanging heat between the air flowing between the fins and the refrigerant, the positions of the end portions in the longitudinal direction of the fins for each fin row are not aligned with each other, and at least one of the fin rows In addition, at least one opening having a flat peripheral edge is formed in a region upstream of the pipe in the fin in the airflow direction of the pipe, and the fin row is upstream of the airflow direction. provided with a plurality on the side, fin the opening formed in the fins of the fin rows on the upstream side of the airflow direction, in which the said opening longitudinally in the arrangement of fins of the upstream side is formed It is inclined with respect to the longitudinal direction, the short direction is provided facing the upstream side, and the angles of the inclination of the openings of the adjacent fin rows adjacent to each other are different from each other. And

The cooling / heating device according to the present invention includes the heat exchanger. Moreover, the cooling / heating device according to the present invention includes a storage room, a back side partition plate provided on the back side of the store room, and a back space formed between the back side partition plate and the back wall of the store room. A heat exchanger that is provided inside and operates as a cooler; a compressor, a condenser, and a capillary that form a refrigeration circuit together with the heat exchanger; and the back side partition plate provided above the back side partition plate A fan that blows air sucked from an air inflow port below to the warehouse through the heat exchanger, and the heat exchanger includes a plurality of fins stacked at intervals, and the fins At least two fin rows comprising a pipe through which the refrigerant flows, and heat exchange between the air flowing between the fins and the refrigerant. End of the fin in the longitudinal direction The positions are not aligned with each other, and at least one of the fins has at least one opening having a flat peripheral edge on the upstream side of the air flow direction of the air with respect to the through position of the pipe in the fin. A plurality of fin rows are provided on the upstream side in the airflow direction, and the opening formed in the fin of each fin row on the upstream side in the airflow direction has a longitudinal direction on the upstream side The fins of the fin rows are inclined with respect to the longitudinal direction of the fins in which the openings are formed , and the short side direction thereof is directed toward the air inlet, and the upstream fin rows adjacent to each other are provided. The inclination angles of the openings are different from each other.
Moreover, the refrigerator according to the present invention includes a heat insulating box provided with a refrigerator compartment, a rear partition plate provided on the rear side of the refrigerator compartment, and between the rear partition plate and the rear wall of the refrigerator compartment. A heat exchanger provided in the formed back space and operating as a cooler, a compressor, a condenser, and a capillary tube constituting a refrigeration circuit together with the heat exchanger, and an air inlet below the back side partition plate And a fan that blows out air sucked from above from above the rear-side partition plate through the heat exchanger, and the heat exchanger includes a plurality of fins stacked at intervals, and the fins It includes at least two fin rows that pass through in the stacking direction and through which the refrigerant flows, and can exchange heat between the air flowing between the fins and the refrigerant. Longitudinal direction of fin The positions of the end portions of the fins are not aligned with each other, and at least one of the fins has a flat peripheral edge portion, and the air flow direction of the air is more than the through-penetration position of the pipe in the fins. A plurality of fin rows are provided on the upstream side in the airflow direction, and the openings formed in the fins of each fin row on the upstream side in the airflow direction are in the longitudinal direction. Is inclined with respect to the longitudinal direction of the fin in which the opening is formed in the upstream fin row, and its short direction is directed toward the air inlet, and the upstream side adjacent to each other is provided. The angles of the inclination of the openings of the fin row are different from each other.

  The heat exchanger and refrigerator of the present invention have the effect of preventing air passage blockage due to frost formation and maintaining high cooling quality.

It is a front view of the heat exchanger in Embodiment 1 of this invention. It is a side view of the heat exchanger of FIG. It is sectional drawing in the AA of the heat exchanger of FIG. It is the fragmentary enlarged plan view (a) of a fin, and sectional drawing (b) in the BB line of (a). It is the elements on larger scale (a) and (b) of the fin of the heat exchanger of Embodiment 2 of this invention. It is the elements on larger scale (a) and (b) of the fin of another heat exchanger of Embodiment 2 of this invention. It is sectional drawing of the heat exchanger of Embodiment 3 of this invention. It is sectional drawing of the heat exchanger of Embodiment 4 of this invention. It is sectional drawing of another heat exchanger of Embodiment 4 of this invention. It is sectional drawing of another heat exchanger of Embodiment 4 of this invention. It is sectional drawing of the heat exchanger of Embodiment 5 of this invention. It is a perspective view of the fin of the heat exchanger of Embodiment 6 of this invention. It is sectional drawing of the depth direction of the cooling / heating apparatus which is Embodiment 7 of this invention. It is sectional drawing which shows an example of the heat exchanger provided in the cooling / heating apparatus of FIG. It is sectional drawing of the horizontal direction of the cooling / heating apparatus which is Embodiment 7 of this invention.

Embodiment 1 FIG.
FIG. 1 is a front view of a heat exchanger 1 in the present embodiment. A plurality of plate-like fins 2 are arranged at predetermined intervals to form six fin rows 21 to 26. Side plates 4 are provided on both sides of the fin rows 21 to 26. The fin rows 21 to 26 are arranged in order in the airflow direction D1. Each of the fins 2 is provided with an insertion hole 2a (FIG. 3) having a cylindrical collar. The pipe 3 has a configuration bent so that the straight pipe portion 3a and the curved pipe portion 3b are continuous. The straight pipe portion 3 a of the pipe 3 is inserted into the insertion hole 2 a of the fin 2, and penetrates the fin rows 21 to 26 in the direction perpendicular to the surface of the fin 2 (hereinafter referred to as the arrangement direction D <b> 2 of the fins 2). doing. The straight pipe portion 3a is in close contact with the fin 2 in the insertion hole 2a. A refrigerant that is a heat exchange fluid flows inside the pipe 3. In the heat exchanger 1, heat as a heat exchange fluid flows between the plurality of fins 2 and the plurality of straight pipe portions 3a, whereby heat is exchanged between the refrigerant and the air. A flow path of air along the airflow direction D1 from the most upstream fin row 21 to the most downstream fin row 26 in the airflow direction D1 is an air passage in the heat exchanger 1.
An interval (hereinafter referred to as fin pitch) S1 between adjacent fins on the upstream side in the airflow direction D1 is larger than the fin pitch S2 on the downstream side.

  FIG. 2 is a side view of the heat exchanger 1. FIG. 3 is a cross-sectional view taken along line AA of the heat exchanger 1. In the fin rows 21 and 22, the straight pipe portions 3a of the two pipes 3 are arranged in the step direction D3 and penetrate the fins 2 in the arrangement direction D2 (FIG. 1). In the fin rows 23 to 26, the straight pipe portions 3a of the three pipes 3 are arranged in series at a predetermined interval in the step direction D3, and penetrate the fins 2 in the arrangement direction D2 (FIG. 1). . Hereinafter, for the sake of convenience, the step direction D3 is referred to as the upper step side and the lower step side as shown in FIG. In one fin 2, only the straight pipe portion 3a1 of one pipe 3 is inserted in the airflow direction D1. The straight pipe portion 3 a of the pipe 3 is also inserted into the insertion holes 2 a of the side plate 4 provided on both sides of the fin rows 21 to 26. The curved pipe portion 3 b of the pipe 3 is located outside the side plate 4. The distance T1 between the opening 2b and the center of the pipe 3 in one fin 2 is smaller than the pitch T2 of the pipes 3 in the fin rows adjacent to each other. Due to this positional relationship, the amount of frost formation is reduced as compared with the case where the opening 2b is not provided.

  FIG. 4A is a partially enlarged plan view of the fin 2. FIG. 4B is a cross-sectional view taken along line BB in FIG. The fin 2 is provided with an opening 2b. The opening 2b is formed between the upstream side of the fin 2 in the airflow direction D1 and the insertion hole 2a. That is, the opening 2b is formed on the upstream side in the airflow direction D1 when viewed from the insertion hole 2a. The peripheral edge E1 of the opening 2b exists in the plane of the fin 2, and does not have a structure perpendicular to or inclined from the plane of the fin 2. That is, the peripheral edge E1 is flat and does not have a shape that rises from the surface of the fin 2. The opening 2b can have a slit shape. The slit shape is a quadrangle having a short side and a long side. In this case, the longitudinal direction of the opening 2 b coincides with the longitudinal direction of the fin 2. The outline of the opening 2b in FIG. 4A is a quadrangle in plan view. Note that the outline of the opening 2b in plan view is not limited to a quadrangle, and may be any other shape such as a polygon, a circle, or an ellipse. From the viewpoint of reducing the amount of frost formation, it is desirable that the length L of the opening 2b in the direction perpendicular to the air flow direction D1 is 0.5 times or more the diameter D of the straight pipe portion 3a of the pipe 3. The amount of frost reduction varies depending on the size of the length L, and the length L is, for example, an arbitrary size within a range of 0.5 to 20 times the diameter D of the straight pipe portion 3a. can do. The length W of the opening 2b in the direction parallel to the airflow direction D1 only needs to be large enough to prevent heat transfer from the region R1 to the region R2. The length W can be, for example, 0.1 mm or more and 50 mm or less. Further, the length W can be 0.01 times or more and 5 times or less of the diameter D of the straight pipe portion 3 a of the pipe 3. The opening 2 b can be formed at an arbitrary position of the fin 2. From the viewpoint of reducing the amount of frost formation, the shortest distance Y from the penetrating position of the pipe 3 on the fin 2 to the opening 2b is from the penetrating position of the pipe 3 on the fin 2 to the upstream side of the fin 2 in the airflow direction. It is preferable to form the opening 2b at a position that is 1/2 or less of the shortest distance X. Further, if the opening 2b is formed in a slit shape, the opening 2b can be provided in a narrow region, and the degree of design freedom regarding the position and number can be increased.

  According to such a configuration, in the region R1 downstream of the opening 2b in the region of the fin 2, the temperature decreases due to the cooling effect by the refrigerant flowing through the pipe 3, but the region R2 upstream of the opening 2b. Then, the cooling effect by the refrigerant | coolant which flows through the piping 3 reduces, and temperature becomes high compared with downstream area | region R1. Since the heat transfer from the pipe 3 to the region R1 is hindered by the opening 2b, a temperature distribution with a height difference is formed with the opening 2b as a boundary. By reducing the difference between the temperature of the upstream region R2 and the temperature of the incoming air, the amount of frost formation is reduced as compared with the case where the opening 2b is not provided.

  For example, it can be set as the structure which provided the opening part 2b in the upstream fin row | line | columns 21 and 22 which are easy to form frost, and provided the opening part in the fin 2 of the downstream fin row | line 23-26 which is hard to form frost. . According to this configuration, it is possible to secure a sufficient amount of heat exchange on the downstream side while suppressing excessive frost formation on the upstream side and achieving uniform frost formation on the heat exchanger 1. Further, since the peripheral edge E1 of the opening 2b is flat and there is no structure rising from the surface of the fin 2, concentrated frost formation in the vicinity of the opening 2b due to the leading edge effect or the turbulent flow promoting effect does not occur. Therefore, according to the heat exchanger 1 of this embodiment, there exists an effect that the air path obstruction | occlusion by concentrated frost formation can be prevented. Further, the amount of frost formation when the circulating air is provided on the upstream side where the circulating air is first contacted is more than when the opening 2b is provided on the downstream side of the air flow direction D1 in the fin 2, that is, the rear side of the pipe 3. Less. Therefore, in order to increase the effect of reducing the amount of frost formation, it is preferable to arrange the opening 2 b on the upstream side of the fin 2. Unlike this embodiment, if two or more straight pipe parts are inserted in parallel in the airflow direction D1 in one fin, the upstream side of one straight pipe part is another straight pipe. Corresponding to the downstream side of the part, even if the opening is provided upstream of the one straight pipe part, the effect of preventing frosting upstream from the opening is low. On the other hand, in the heat exchanger 1 of the present embodiment, only the straight pipe portion 3a1 of one pipe 3 is inserted in the airflow direction D1 in one fin 2, so that the upstream side from the opening 2b. The effect of preventing frost formation is great. The opening 2b is not necessarily provided in all of the fin rows 21 to 26, and may be provided in at least one of them. Moreover, the opening part 2b does not need to be provided in all the fins 2 which comprise one fin row, and should just be provided in at least one of these. That is, the opening 2b can be appropriately provided in any fin 2 for adjusting the amount of frost reduction.

Embodiment 2. FIG.
FIGS. 5A to 5D are partially enlarged plan views showing modifications of the fin 2 in which the opening 2b is formed. The opening 2b can have a slit shape. In the following, different parts from the first embodiment will be mainly described.

  In the example of FIG. 5A, the opening 2b1 is formed on the upper side of the step direction D3 when viewed from the insertion hole 2a, and the opening 2b2 is formed on the lower side. That is, two openings 2b1 and 2b2 are formed across the insertion hole 2a. The longitudinal directions of the openings 2 b 1 and 2 b 2 coincide with the short direction of the fin 2.

  According to such a configuration, in the region R1 between the opening 2b1 and the opening 2b2, the temperature decreases due to the cooling effect by the refrigerant flowing through the pipe 3. On the other hand, in the region R21 on the upper side of the opening 2b1 and the region R22 on the lower side of the opening 2b2, the cooling effect by the refrigerant flowing through the pipe 3 is reduced, and the temperature is higher than that of the region R1. By reducing the difference between the temperatures of the regions R21 and R22 and the temperature of the incoming air, the amount of frost formation in the regions R21 and R22 is reduced. As described above, the arrangement of the openings shown in FIG. 5A can also form a temperature distribution with a height difference in the fins 2, reduce the amount of frost formation, and prevent air passage blockage. For example, when the width of the fin 2 in the short direction is narrow and the opening cannot be formed on the upstream side of the airflow direction D1, it is effective to use the arrangement shown in FIG.

  In the example of FIG. 5B, as viewed from the insertion hole 2a, the opening 2b1 is formed on the upper side of the step direction D3, the opening 2b2 is formed on the lower side, and upstream of the air flow direction D1. An opening 2b3 is formed on the side. The longitudinal directions of the openings 2 b 1 and 2 b 2 coincide with the short direction of the fin 2. The longitudinal direction of the opening 2 b 3 coincides with the longitudinal direction of the fin 2.

  According to such a configuration, in the region R1 surrounded by the openings 2b1, 2b2, and 2b3 in the region of the fin 2, the temperature decreases due to the cooling effect by the refrigerant flowing through the pipe 3. On the other hand, in the region R2 outside the openings 2b1, 2b2, and 2b3 when viewed from the insertion hole 2a, the cooling effect by the refrigerant flowing through the pipe 3 is reduced, and the temperature is higher than that in the region R1. By reducing the difference between the temperatures of the regions R21 and R22 and the temperature of the incoming air, the amount of frost formation in the regions R21 and R22 is reduced. According to the arrangement of the openings in FIG. 5 (b), a temperature distribution with a larger height difference can be formed compared to the case of FIG. 5 (a), and the amount of frost formation can be further reduced. Therefore, when it is desired to significantly reduce the amount of frost formation, the arrangement shown in FIG. 5B is effective.

  In the example of FIG. 6A, an arcuate opening 2b is formed. In order to reduce the amount of frost formation, it is preferable that at least a part of the opening 2b is formed on the upstream side in the airflow direction D1 of the insertion hole 2a.

  According to such a configuration, in the region 2 of the fin 2, in the region R <b> 1 on the downstream side in the airflow direction D <b> 1 when viewed from the opening 2 b, the temperature decreases due to the cooling effect by the refrigerant flowing through the pipe 3. On the other hand, in the region R2 on the upstream side when viewed from the opening 2b, the cooling effect by the refrigerant flowing through the pipe 3 is reduced, and the temperature is higher than that in the region R1. By reducing the difference between the temperature in the region R2 and the temperature of the inflowing air, the amount of frost formation in the region R2 decreases. As described above, even with the opening arrangement in FIG. 6A, a temperature distribution with a difference in height can be formed in the fins 2, and the amount of frost formation can be reduced to prevent air passage blockage. The opening 2b can be formed close to the insertion hole 2a by making the curvature of the arc of the opening 2b substantially the same as the curvature of the outer periphery of the insertion hole 2a. According to such a configuration, a temperature distribution having a sufficient height difference can be obtained in a narrow opening formation region.

  In the example of FIG. 6B, as viewed from the insertion hole 2a, three openings 2b1, 2b2, and 2b3 are formed in parallel on the upstream side in the airflow direction D1. The longitudinal direction of the openings 2 b 1, 2 b 2 and 2 b 3 coincides with the longitudinal direction of the fin 2.

  According to this configuration, in the region R1 on the downstream side of the opening 2b1 in the region of the fin 2, the temperature decreases due to the cooling effect by the refrigerant flowing through the piping 3, while in the upstream region R2, the piping 3 is The cooling effect by the flowing refrigerant is reduced, and the temperature becomes higher than that in the region R1. By reducing the difference between the temperature in the region R2 and the temperature of the inflowing air, the amount of frost formation in the region R2 decreases. As described above, even with the opening arrangement shown in FIG. 6B, a temperature distribution with a height difference can be formed in the fins 2, and the amount of frost formation can be reduced to prevent air passage blockage. For example, when it is not possible to ensure a region that can form an opening between two adjacent insertion holes 2a, it is effective to use the arrangement shown in FIG. 6B in order to reduce the amount of frost formation.

  FIG. 6B shows an example in which three openings are formed, but two or four or more openings can also be formed. As the number of openings increases, frost formation becomes difficult. For example, there are three in the upstream fin rows 21 and 22 where frost formation is likely to occur, and two in the downstream fin rows 23 to 26 where frost formation is difficult. As described above, the number of openings may be changed between the upstream side and the downstream side. According to this configuration, the frost distribution in the entire heat exchanger 1 can be made uniform, and the cooling quality can be improved.

Embodiment 3 FIG.
In the following, different parts from the first embodiment will be mainly described.
FIG. 7 is a cross-sectional view showing an example of the heat exchanger 1 of the present embodiment. The fin rows 21 and 22 arranged at the fin pitch S1 on the upstream side in the air flow direction D1 are provided with openings 2b, and the fin rows 23 to 23 arranged at the fin pitch S2 narrower than the fin pitch S1 on the downstream side. 26 is not provided with an opening 2b.

  According to such a configuration, in the fin rows 21 and 22 on the upstream side, in addition to widening the fin pitch S1, the opening 2b is formed in the fin 2, so that the amount of frost formation on the upstream side is further increased. The effect of preventing air passage blockage can be further enhanced. On the other hand, in the fin rows 23 to 26 on the downstream side, since the fin pitch S2 is narrowed, a sufficient heat exchange amount can be ensured. For example, if the fin pitch S1 of the upstream fin rows 21 and 22 cannot be further increased due to restrictions in design specifications or cost requirements, the opening 2b is provided only in the upstream fin rows 21 and 22 to provide heat. The distribution of frost formation in the entire exchanger 1 can be made uniform, and air passage blockage due to frost formation can be prevented.

  As a modification of the present embodiment, the fin rows 21 to 26 are divided into an upstream group and a downstream group regardless of the size of the fin pitch, and the fin rows belonging to the upstream group in the airflow direction D1 are separated. The opening 2b may be provided, and the fin 2 belonging to the downstream group may not be provided with the opening 2b. Even with this configuration, it is possible to prevent the air passage from being blocked due to frost formation on the upstream side, and to achieve uniform frost distribution in the entire heat exchanger 1. The upstream group refers to only the most upstream fin row 21 or the fin row 21 to the fin row 23 in order. The downstream side group means only the most downstream fin row 26 or the fin row 26 to the fin row 24 in order. In this manner, the upstream group and the downstream group can be divided at positions that are half the number of the fin rows 21 to 26. Although this Embodiment and its modification are examples when the opening part 2b is formed in the upstream of the airflow direction D1 seeing from the insertion hole 2b, it is not restricted to this, Fig.5 (a)-FIG.6 ( You may form in the position shown by b).

Embodiment 4 FIG.
In the following, different parts from the first embodiment will be mainly described.
FIG. 8 is a cross-sectional view showing an example of the heat exchanger 1 of the present embodiment. The longitudinal length L1 of the openings 2b of the fin rows 21 and 22 arranged at the fin pitch S1 on the upstream side in the airflow direction D1 is arranged at the fin pitch S2 narrower than the fin pitch S1 on the downstream side. It is larger than the length L2 of the longitudinal direction of the opening part 2b of the fin rows 23-26. According to the configuration of FIG. 8, in the upstream fin rows 21 and 22, in addition to widening the fin pitch S <b> 1, the opening 2 b having a relatively long longitudinal length L <b> 1 is formed. The amount of frost formation on the side can be further reduced, and air passage blockage can be prevented. Moreover, in the downstream fin row | line | columns 23-26, since the opening part 2b whose length L2 of a longitudinal direction is comparatively small is formed, the heat exchange amount in downstream can fully be ensured.

  FIG. 9 is a cross-sectional view showing another example of the heat exchanger 1 of the present embodiment. The width W1 in the short direction of the openings 2b of the fin rows 21 and 22 arranged on the upstream side in the airflow direction D1 with the fin pitch S1 is arranged on the downstream side with a fin pitch S2 narrower than the fin pitch S1. The width W2 in the short direction of the opening 2b of the fin rows 23 to 26 is larger. According to the configuration of FIG. 9, in the upstream fin rows 21 and 22, in addition to widening the fin pitch S1, the opening 2b having a relatively large width W1 is formed. The amount of frost can be further reduced, and the effect of preventing air passage blockage can be further enhanced. Moreover, in the downstream fin row | line | rows 23-26, since the width W2 of the opening part 2b is comparatively small, the effect of frost amount reduction is small and sufficient heat exchange amount can be ensured.

  FIG. 10 is a cross-sectional view showing another example of the heat exchanger 1 of the present embodiment. The shortest distance Y1 from the longitudinal side of the opening 2b to the outer periphery of the straight pipe portion 3a in the fin rows 21 and 22 arranged at the fin pitch S1 on the upstream side in the air flow direction D1 is smaller than the fin pitch S1 on the downstream side. Is shorter than the shortest distance Y2 from the side in the longitudinal direction of the opening 2b in the fin rows 23 to 26 arranged at the narrow fin pitch S2 to the outer periphery of the straight pipe portion 3a. 10, in addition to widening the fin pitch S1 in the fin rows 21 and 22 on the upstream side, the opening 2b is provided at a position where the shortest distance Y1 to the outer periphery of the straight pipe portion 3a is relatively short. Since it forms, the amount of frost formation to an upstream side can be reduced more, and the prevention effect of an air path obstruction | occlusion can further be improved. Further, in the fin rows 23 to 26 on the downstream side, since the opening 2b is formed at a position where the distance Y2 to the outer periphery of the straight pipe portion 3a is relatively long, a sufficient heat exchange amount can be secured.

  As a modification of FIG. 8, regardless of the fin pitch size, the length of the opening 2 b of the fin row located on the upstream side in the airflow direction D <b> 1 is the length of the opening 2 b of the fin row located on the downstream side. It can be set as the structure set as the above magnitude | size. For example, the length of the opening 2b of the upstream fin rows 21 to 23 can be made larger than the length of the opening 2b of the downstream fin rows 24 to 26. Further, for example, the length of the opening 2b can be increased stepwise from the fin row 26 located at the most downstream side to the fin row 21 located at the most upstream side.

  As a modification of FIG. 9, regardless of the fin pitch size, the width in the short direction of the opening 2b of the fin row located on the upstream side in the airflow direction D1 is set to the opening 2b of the fin row located on the downstream side. It can be set as the structure more than the width | variety of the transversal direction. For example, the width in the short-side direction of the opening 2b of the upstream fin rows 21 to 23 can be made larger than the width in the short-side direction of the opening 2b of the downstream fin rows 24 to 26. In addition, for example, the width of the opening 2b can be increased stepwise from the fin row 26 located on the most downstream side to the fin row 21 located on the most upstream side.

  As a modification of FIG. 10, the shortest distance from the side in the longitudinal direction of the opening 2b of the fin row located on the upstream side in the airflow direction D1 to the outer periphery of the straight pipe portion 3a is set downstream, regardless of the size of the fin pitch. It can be set as the length more than the shortest distance from the edge of the longitudinal direction of the opening part 2b of the fin row located in the side to the outer periphery of the straight pipe part 3a. For example, the distance in the upstream fin rows 21 to 23 can be longer than the distance in the downstream fin rows 24 to 26. Further, for example, the distance from the fin row 26 located on the most downstream side to the fin row 21 located on the most upstream side may be shortened stepwise.

  According to these modified examples, since the amount of frost formation in the heat exchanger 1 can be finely adjusted stepwise from the downstream to the upstream in the airflow direction D1, the frost distribution in the entire heat exchanger 1 can be made more uniform. Further, the effect of preventing air passage blockage due to frost formation can be further enhanced.

Embodiment 5. FIG.
In the following, different parts from the first embodiment will be mainly described.
FIG. 11 is a cross-sectional view showing an example of the heat exchanger 1 of the present embodiment. In the fin rows 21 and 22 arranged on the upstream side in the airflow direction D1, the pipe 3 is provided at a position shifted from the center position F1 in the short direction of the fin 2 to the downstream side in the airflow direction D1. An opening 2b is formed on the upstream side in the airflow direction D1 of the fins 2 of the fin rows 21 and 22. Moreover, in the fin row | line | columns 23-26 arrange | positioned downstream of the airflow direction D1, the three piping 3 is provided along with the center position F2 of the transversal direction of the fin 2. As shown in FIG. No openings are formed in the fins 2 of the fin rows 23 to 26.

  According to this configuration, on the upstream side in the airflow direction D1, the cooling effect by the refrigerant flowing through the pipe 3 is relatively far from the pipe 3 in the fins 2 of the fin rows 21 and 22, that is, in the upstream area in the airflow direction D1. Since it weakens, the amount of frost formation can further be reduced compared with the case of only the opening 2b. On the other hand, in the fin rows 23 to 26 on the downstream side in the airflow direction D1, the cooling effect of the refrigerant flowing through the pipe 3 extends to the upstream and downstream peripheral portions of the fin 2, and no opening is provided. A sufficient amount of heat exchange can be secured. For example, if the fin pitch S1 of the upstream fin rows 21 and 22 cannot be widened due to restrictions in design specifications or cost requirements, the configuration shown in FIG. 11 prevents the air passage from being blocked due to frost formation on the upstream side. However, since a sufficient amount of heat exchange is ensured on the downstream side, high cooling quality can be obtained.

Embodiment 6 FIG.
FIG. 12 is a perspective view of the fin 2 of the heat exchanger 1 of the present embodiment. The fin 2 is provided with a cut-and-raised portion 2c. The cut-and-raised portion 2 c is formed by making two parallel cuts on the surface of the fin 2 and standing the center of the cut in a direction perpendicular to the surface of the fin 2. The cut-and-raised portion 2c includes two cut-and-raised surfaces 2c1 and 2c2 that are inclined in opposite directions, and has a V shape. As shown in FIG. 12, the cut-and-raised portion 2c can be provided, for example, at the upstream side and the downstream side of the insertion hole 2a and at an intermediate position between the two insertion holes 2a adjacent to each other.

  The heat transfer coefficient between the inflowing air and the fins 2 is increased by the leading edge effect of the cut-and-raised portions 2 c raised in the direction perpendicular to the surface of the fins 2. According to such a configuration, it is possible to compensate for the heat exchange amount reduced by providing the opening 2b in the fin 2. For example, the opening 2b is provided in the fins 2 of the upstream fin rows 21 and 22 where the amount of frost formation increases, and the opening 2b is not provided in the fins 2 of the downstream fin rows 23 to 26 where the amount of frost formation is small. It can be set as the structure which provided the cut-and-raised part 2c. According to such a configuration, a sufficient heat exchange amount is secured on the downstream side while preventing air passage blockage due to frost formation on the upstream side, so that high cooling quality can be obtained. In any configuration of the first to fifth embodiments, the cut and raised portion 2c of the present embodiment can be provided. Further, the cut-and-raised portion 2 c is not limited to the shape of the example of FIG. 12, and may have a structure that is perpendicular or inclined with respect to the surface of the fin 2.

Embodiment 7 FIG.
FIG. 13 is a schematic cross-sectional view in the depth direction of the cooling / heating device 10 including any one of the heat exchangers 1 of Embodiments 1 to 6 and FIG. FIG. 14 is a cross-sectional view illustrating an example of the heat exchanger 1 used in the refrigerator 10 of the present embodiment. FIG. 15 is a schematic cross-sectional view in the horizontal direction of the refrigerator 10 of the present embodiment. In the present embodiment, the cooling / heating device 10 will be described as the refrigerator 10. The heat insulation box 11 is partitioned by storage room partition plates 19a and 19b, and three storage rooms 13-a to 13-c are formed. The chambers 13-a to 13-c can be opened and closed by front doors 12-a to 12-c, respectively. For example, the storage room 13-a is a refrigerator compartment, the storage room 13-b is a vegetable room, and the storage room 13-c is a freezing room. The heat exchanger 1 is installed in the back space 17 partitioned by the back side partition plate 16 of the warehouse 13-c. The heat exchanger 1 operates as a cooler, and constitutes a refrigerant circuit together with the compressor 14, a condenser (not shown), and a capillary tube (not shown). The cool air generated by the refrigerant circuit is supplied to the compartments 13-a to 13-c by the fan 15 provided above the rear side partition plate 16. The fan 15 is provided above the rear side partition plate 16, and blows air sucked from an air inlet 18 below the rear side partition plate 16 to the compartments 13-a to 13-c via the heat exchanger 1. To do. The cold air circulates through the ducts 30 provided on the back surface of the heat insulating box 11 and the openings 31 to 35 communicating with the storage chambers 13-a to 13-c as indicated by the dashed arrows.

  The heat exchanger 1 is provided so that the longitudinal direction of the fins 2 in the fin rows 21 to 26 is perpendicular to the surface of the rear partition plate 16. The circulating air flows into the back space 18 from the air inlet 17 below the back side partition plate 16 in an obliquely upward direction. The openings 2b of the fin rows 21 to 26 are provided on the upstream side in the airflow direction D1 when viewed from the straight pipe portion 3a of the pipe 3. The openings 2 b of the fin rows 21 and 22 on the upstream side in the airflow direction D <b> 1 are provided such that the longitudinal direction thereof is inclined with respect to the longitudinal direction of the fins 2. As a result, the short direction of the opening 2 b of the fin rows 21 and 22 is directed to the air inlet 17. On the other hand, the opening 2b of the fin rows 23 to 26 on the downstream side in the airflow direction D1 is provided such that the longitudinal direction thereof coincides with the longitudinal direction of the fins 2. In one fin 2, only the straight pipe portion 3a1 of one pipe 3 is inserted in the airflow direction D1. Since heat transfer from the pipe 3 to the upstream region in the airflow direction D1 when viewed from the position of the opening 2b is hindered, according to the configuration of FIG. 14, the air along the airflow direction D1 in the heat exchanger 1 The temperature of the fin area | region on the flow path D4 (broken line) becomes higher, and the effect of the amount of frost formation is raised more.

  Since the refrigerator 10 in the present embodiment includes any one of the heat exchangers 1 of Embodiments 1 to 6 and FIG. 14, air passage blockage due to frost formation can be prevented and high cooling quality can be obtained. . Even in the case of other refrigeration equipment such as a freezer, the same effect can be achieved. In the refrigerator 10, the heat exchanger 1 is provided in a space formed between the back-side partition plate 16 and the box body back wall 11a. In a general refrigerator, the distance K1 between the rear side partition plate 16 and the box rear wall 11a is narrow, and when the heat exchanger 1 is provided between them, the wind in the heat exchanger 1 is formed by frost formation. When the path is blocked, the amount of air passing from the air inlet 17 to the fan 15 is extremely reduced, and the cooling performance is significantly reduced. According to the first to sixth embodiments and the heat exchanger 1 of FIG. 14, the amount of frost formation can be reduced to prevent the air passage from being blocked, which is particularly effective when applied to the refrigerator 10.

  Although Embodiment 1-7 is an example in case the length of the longitudinal direction of the fins 21 and 22 differs from the length of the longitudinal direction of the fins 23-26, the length of the longitudinal direction of the fins 21-26 is the same. It can also be set as the structure made into. Even in this case, the same effect is obtained. Moreover, although Embodiment 1-7 is an example when the position of the edge part of the longitudinal direction of the fins 21-26 is not uniform, it is the structure which aligned the position of the edge part of the longitudinal direction of the fins 21-26, and You can also Even in this case, the same effect is obtained. When the heat exchanger 1 of Embodiment 7 in which the lengths in the longitudinal direction of the fins 21 to 26 are different and these end portions are not aligned is applied to the refrigeration equipment 10, the heat exchanger 1 is frosted. In some cases, the heat exchanger 1 can be prevented from blocking the flow of cool air in the duct 30. In general, the duct 30 of the refrigerator 10 is provided in a narrow space between the rear-side partition plate 16 and the rear wall of the heat insulating box 11, so that the air flow path in the duct 30 is narrow. In a general refrigerator, the flow of air in the duct tends to be disturbed particularly when the heat exchanger is frosted. Therefore, it is particularly effective to apply to the refrigerator 10 the heat exchanger 1 according to the first to seventh embodiments, in which the lengths of the fins 21 to 26 in the longitudinal direction are different and the ends thereof are not aligned.

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Fin 2a Insertion part 2b Opening part 2c Cut-and-raising part 21-26 Fin row | line | column 3 Piping 3a Straight pipe part 3b Curved pipe part 4 Side plate 10 Cooling equipment 11 Heat insulation box 11a Box body rear wall 12-a 12-b, 12-c, 12-d Front doors 13-a, 13-b, 13-c, 13-d Storage room 14 Compressor 15 Fan 16 Rear side partition plate 17 Air inlet 18 Back space 19a, 19b Warehouse partition plate 30 Ducts 31-35 Opening

Claims (22)

A plurality of fins laminated at intervals, and the fins are penetrated in the lamination direction,
In a heat exchanger that includes at least two fin rows composed of a pipe through which refrigerant flows, and that exchanges heat between the air flowing between the fins and the refrigerant,
The position of the end of the fin in the longitudinal direction for each fin row is not aligned,
At least one opening having a flat peripheral edge is formed in at least one of the fins in an upstream region in the airflow direction of the air from a position where the pipe penetrates the fin.
A plurality of the fin rows are provided on the upstream side in the airflow direction,
The opening formed in the fin of each fin row on the upstream side in the airflow direction is inclined with respect to the longitudinal direction of the fin in which the opening is formed in the upstream fin row , and the short side thereof. The hand direction is provided facing the upstream side,
The heat exchanger characterized in that the angles of inclination of the openings of the upstream fin rows adjacent to each other are different from each other.   The heat exchanger according to claim 1, wherein the fins have different lengths in the longitudinal direction for each fin row.   The heat exchanger according to claim 1, wherein the opening has a slit shape.   The length of the opening in a direction perpendicular to the airflow direction is 0.5 times or more of the diameter of the pipe passing through the fin. A heat exchanger according to claim 1.   The shortest distance from the pipe penetration position on the fin to the opening is ½ or less of the shortest distance from the pipe penetration position on the fin to the upstream side of the fin in the airflow direction. It exists, The heat exchanger as described in any one of Claims 1-4 characterized by the above-mentioned.   The distance between the opening of the fin and the center of the pipe is smaller than the pitch of the pipes of the fin rows adjacent to each other. Heat exchanger.   5. The heat exchanger according to claim 1, wherein the opening has a slit shape, and two or more long sides are formed at positions parallel to each other. A plurality of the fin rows are provided along the air flow direction of the air,
The fin pitch in the fin row on the upstream side in the airflow direction is wider than the fin pitch in the fin row on the downstream side in the airflow direction,
The heat exchanger according to any one of claims 1 to 4, wherein the opening is formed only in the fin row on the upstream side. A plurality of the fin rows are provided along the air flow direction of the air,
The plurality of fin rows are composed of an upstream group and a downstream group, and the openings are formed only in the fin rows belonging to the upstream group. A heat exchanger according to claim 1. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The fin pitch in the fin row on the upstream side in the airflow direction is wider than the fin pitch in the fin row on the downstream side in the airflow direction,
The length in the longitudinal direction of the opening in the fin row on the upstream side is longer than the length in the longitudinal direction of the opening in the fin row on the downstream side. A heat exchanger according to claim 1. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The fin pitch in the fin row on the upstream side in the airflow direction is wider than the fin pitch in the fin row on the downstream side in the airflow direction,
The width in the short direction of the opening in the fin row on the upstream side is larger than the width in the short direction of the opening in the fin row on the downstream side. The heat exchanger as described in any one. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The fin pitch in the fin row on the upstream side in the airflow direction is wider than the fin pitch in the fin row on the downstream side in the airflow direction,
The shortest distance from the side in the longitudinal direction of the opening in the upstream fin row to the outer periphery of the pipe is from the side in the longitudinal direction of the opening in the downstream fin row to the outer periphery of the pipe. The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger is shorter than the shortest distance. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The length in the longitudinal direction of the opening portion increases stepwise from the fin row on the most downstream side in the airflow direction to the fin row on the most upstream side. A heat exchanger according to claim 1. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The width in the short direction of the opening is gradually increased from the fin array on the most downstream side in the airflow direction to the fin array on the most upstream side. A heat exchanger according to claim 1. The opening has a slit shape,
A plurality of the fin rows are provided along the air flow direction of the air,
The shortest distance from the longitudinal side of the opening to the outer periphery of the pipe is gradually reduced from the fin row on the most downstream side in the airflow direction to the fin row on the most upstream side. The heat exchanger according to any one of claims 1 to 4. The shape of the fin is rectangular in plan view,
A plurality of the fin rows are provided along the air flow direction of the air,
In the fin row on the upstream side in the airflow direction, the pipe is provided at a position shifted from the center position in the short direction of the fin to the downstream side in the airflow direction. The heat exchanger according to any one of 4.   The heat exchanger according to any one of claims 1 to 16, wherein the fin is provided with a structure perpendicular to or inclined with respect to a surface of the fin.   18. The heat exchanger according to claim 1, wherein only one of the pipes is inserted in the airflow direction in one of the fins.   A cold-heating apparatus provided with the heat exchanger as described in any one of Claims 1-18. The cooler is provided in a back space formed between the back chamber and the back side partition plate provided on the back side of the store room, and between the back side partition plate and the back wall of the store room, and operates as a cooler. A heat exchanger, a compressor, a condenser, and a capillary tube constituting a refrigeration circuit together with the heat exchanger, and an upper side of the rear side partition plate, and sucked from an air inlet below the rear side partition plate A fan that blows air to the chamber through the heat exchanger,
The heat exchanger includes at least two fin rows including a plurality of fins stacked at intervals, and a pipe that penetrates the fins in the stacking direction and through which a refrigerant flows.
Heat exchange between the air flowing between the fins and the refrigerant,
The positions of the end portions in the longitudinal direction of the fins for each fin row are not aligned with each other,
At least one opening having a flat peripheral edge is formed in at least one of the fins in an upstream region in the airflow direction of the air from a position where the pipe penetrates the fin.
A plurality of the fin rows are provided on the upstream side in the airflow direction,
The opening formed in the fin of each fin row on the upstream side in the airflow direction is inclined with respect to the longitudinal direction of the fin in which the opening is formed in the upstream fin row , and the short side thereof. A hand direction is provided facing the air inlet;
The cooling apparatus according to claim 1, wherein the angles of inclination of the openings of the upstream fin rows adjacent to each other are different from each other. A heat insulating box having a refrigerator compartment, a rear partition plate provided on the rear side of the refrigerator compartment, and a rear space formed between the rear partition plate and the rear wall of the refrigerator compartment. A heat exchanger that operates as a cooler; a compressor, a condenser, and a capillary tube that constitute a refrigeration circuit together with the heat exchanger; and the air that has been sucked in from the air inlet below the rear-side partition plate. And a fan that blows out from above the back side partition plate via,
The heat exchanger includes at least two fin rows including a plurality of fins stacked at intervals, and a pipe that penetrates the fins in the stacking direction and through which a refrigerant flows.
Heat exchange between the air flowing between the fins and the refrigerant,
The positions of the end portions in the longitudinal direction of the fins for each fin row are not aligned with each other,
At least one opening having a flat peripheral edge is formed in at least one of the fins in an upstream region in the airflow direction of the air from a position where the pipe penetrates the fin.
A plurality of the fin rows are provided on the upstream side in the airflow direction,
The opening formed in the fin of each fin row on the upstream side in the airflow direction is inclined with respect to the longitudinal direction of the fin in which the opening is formed in the upstream fin row , and the short side thereof. A hand direction is provided facing the air inlet;
The refrigerator characterized in that the angles of inclination of the openings of the upstream fin rows adjacent to each other are different from each other.   The refrigerator according to claim 21, wherein lengths of the fins in the longitudinal direction of the fin rows are different from each other.

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