JP4762266B2 - Heat exchanger and refrigerator-freezer equipped with this heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger and a refrigerator-freezer equipped with the heat exchanger.

  In order to reduce the power consumption of the refrigerator-freezer, a heat exchanger that has a high effect of preventing clogging due to frost formation and a high cooling performance is desired. In order to realize such a demand, various heat exchangers have been conventionally proposed. For example, “1 indicates a heat exchanger main body as an evaporator for a refrigerator-freezer, A plurality of fins 4p, 4q, and 4r arranged in parallel between 3 and the end plates 2 and 3, and a refrigerant pipe 5 penetrating perpendicularly to the fins 4p, 4q, and 4r. The fins 4p, 4q, and 4r are air. The flow direction (indicated by arrows) is independent for each row p, q, r with a small interval l so that the air flows gradually from the air inflow side toward the outflow side. "It is arranged" (for example, refer to Patent Document 1) has been proposed.

However, in the heat exchanger described in Patent Document 1, if the fins on the air inflow side are made too sparse, the heat transfer area as the whole fins included in the heat exchanger is reduced, and the cooling performance of the heat exchanger is reduced. There was a problem.
In order to solve this problem, for example, “5 is an evaporator for a refrigerator, which includes a first evaporator 6 and a second evaporator 7, which are juxtaposed in the longitudinal direction. The two evaporators 7 are formed by crossing a large number of small fins 6b and 7b on meandering pipes 6a and 7a, and the fin width of the second evaporator 7 is set narrow on the airflow inflow side. The cool air duct constitutes a cool air circulation passage and houses the evaporator 5. The cool air duct 8 forms a step portion 8a in the middle of the first evaporator 6 so that the cool air also flows from the side of the first evaporator 6. Thus, the cold air flows in as shown by the arrow and exchanges heat with the evaporator 5. However, frost is generated at the inlet side of the first evaporator 6 and the second evaporator 7. Inflow of cold air from the inlet side is hindered, and cold air flows from the side surface having the step 8a and the narrow fin portion. In this way, frost is generated, and heat exchange efficiency can be made uniform in the first evaporator 6 and the second evaporator 7 in this way. Yes.
Further, for example, “8 is an air passage, which is formed in the vicinity of the center portion of the fin 1 in the air inflow direction by a rectangular notch along the air inflow side direction, and frost adheres to the first half of the refrigeration heat exchanger. However, a heat exchanger has been proposed that “the amount of ventilation is ensured” (see, for example, Patent Document 3).

Japanese Utility Model Publication No. 61-43113 (first page, FIG. 1) JP-A-60-016278 (2nd page, FIG. 3) Japanese Patent No. 3040198 (paragraph 0009, FIG. 1)

  When the heat exchanger is not frosted, the air flowing through the heat exchanger described in Patent Document 2 tends to flow through the bypass air passage (step 8a) that has less obstruction of the air flow than between the fins. However, since the air flowing through the bypass air passage provided on the side of the heat exchanger is in contact with the fins on only one side, air that circulates without being sufficiently cooled is generated. For this reason, there existed a problem that the air volume effective for cooling decreased and the cooling performance of the heat exchanger fell.

  Moreover, although the heat exchanger of patent document 3 can ensure the air volume which flows through the inside of a heat exchanger by providing a notch in a fin, the heat-transfer area as the whole fin with which a heat exchanger is provided reduces, There was a problem that the cooling performance of the exchanger fell.

  The present invention has been made to solve the above-described problems, and obtains a heat exchanger that is highly effective in preventing clogging due to frost formation and has high cooling performance, and a refrigerator-freezer equipped with this heat exchanger. For the purpose.

The heat exchanger according to the present invention is a heat exchanger comprising a plurality of fins laminated at a predetermined interval and a heat transfer tube penetrating the fins in the lamination direction, wherein the fins are in a direction perpendicular to the lamination direction. by and column direction is the direction of air flow, and are each of a plurality juxtaposed in the column direction is a stacking direction and a column direction perpendicular to the direction, stage direction gap is formed between the fins adjacent the column direction, the air flow The stepwise gap of the fin located on the downstream side is formed smaller than the stepwise gap of the fin located on the upstream side of the air flow, and the stepwise gap is a width in the stepwise direction of the fin. It is formed by adjusting .

  Moreover, the refrigerator-freezer which concerns on this invention mounts said heat exchanger.

According to the present invention, since the gap in the step direction is formed between the fins adjacent in the step direction, the effect of preventing clogging due to frost formation is improved. The air that has flowed into the heat exchanger easily flows through the gap in the step direction with little pressure loss, so that it can come into contact with the fins on both sides, increasing the effective air volume and improving the refrigeration performance of the heat exchanger. Moreover, since the front edge part of a fin increases by arrange | positioning a several fin in a row direction, the cooling performance of a heat exchanger improves. For this reason, it is possible to suppress the decrease in the cooling performance of the heat exchanger caused by the reduction in the heat transfer area of the fin, which is caused by forming the stepwise gap. In addition, since the fin gap in the fins located on the downstream side of the air flow is formed smaller than the fin gap in the fins located on the upstream side of the air flow, the heat exchanger has air from the upstream side of the air flow. Uniform frost formation on the downstream side of the flow. Further, since the stepwise gap is formed by adjusting the width of the fin in the step direction, the width of the heat exchanger can be unified, and the installation of the heat exchanger becomes easy. Therefore, it is possible to obtain a heat exchanger having a high effect of preventing clogging due to frost formation and a high cooling performance, and a refrigerator-freezer equipped with this heat exchanger.

Embodiment 1 FIG.
1 is an external perspective view of the refrigerator-freezer according to Embodiment 1, and FIG. 2 is a cross-sectional view taken along the line DD ′ of FIG. 3 and 4 are a cross-sectional view taken along line EE ′ of FIG. 2 and a cross-sectional view taken along line FF ′ of FIG. 2, respectively. FIG. 3 also shows a refrigeration cycle mounted on the refrigerator-freezer 50. In addition, although the installation position of the condenser 13 and the expansion device 14 is not shown in FIG. 3, for example, it can be installed at an arbitrary position such as the back surface of the refrigerator 50. The refrigerator-freezer 50 is demonstrated using these FIGS. 1-4.

  The refrigerator-freezer 50 is provided with a refrigerator compartment 100, a freezer compartment 200, a vegetable compartment 300, a switching room 400, and an ice making room 500 as temperature zone rooms. The refrigerator compartment 100 is provided in the uppermost part of the refrigerator 50, and the switching room 400 and the ice making room 500 are provided along with the refrigerator compartment 100 below. A vegetable room 300 is provided below the switching room 400 and the ice making room 500, and a freezing room 200 is provided below the vegetable room 300. In the switching chamber 400, the room temperature can be switched between a freezing temperature zone (about −12 to −22 ° C.) and a refrigeration temperature zone (about 0 to 5 ° C.). For example, if the refrigerator / freezer 50 is a refrigerator / freezer with a total capacity of 450 L, the capacity of each temperature zone room is about 240 L for the refrigerator compartment 100, 80 L for the freezer compartment 200, and about 90 L for the vegetable compartment 300.

  The housing of the refrigerator-freezer 50 is composed of, for example, an outer box made of steel plate and an inner box made of synthetic resin, and a heat insulating material or the like is filled between them. And each temperature zone room is comprised by partitioning the inside of this housing | casing with a heat insulating material etc.

  On the back side of the refrigerator compartment 100, vegetable compartment 300, switching room 400 and ice making room 500, a partition wall 6 is provided as a back wall of each temperature zone room. An air passage 20 is formed between the partition wall 6 and the back wall 7 of the housing. The heat exchanger 1 is provided in the air path 20 in the range facing the back side of the vegetable room 300 (hereinafter, the air path 20 in the range in which the heat exchanger 1 is provided is referred to as the cooling chamber 8). Further, the air passage 20 is provided with a blower 11 at the top of the heat exchanger 1.

  Each temperature zone chamber is provided with an inlet for allowing the air cooled by the heat exchanger 1 to flow into each temperature zone, and an outlet for allowing the air to flow out of each temperature zone. As shown in FIG. 2, an inlet 101 and an outlet 102 are provided on the back side of the refrigerator compartment 100. On the back side of the freezer compartment 200, inlets 201a and 201b and outlets 202a and 202b are provided. An inlet 301 and an outlet 302 are provided on the back side of the vegetable compartment 300. An inflow port 401 and an outflow port 402 are provided on the back side of the switching chamber 400. An inflow port 501 and an outflow port 502 are provided on the back side of the ice making chamber 500.

  Among these inlets and outlets, the outlet 102 of the refrigerator compartment 100 and the inlet 301 of the vegetable compartment 300 are communicated with each other through a rear air passage 21 provided on the back side of the switching chamber 400. One end of an air passage 22 provided on the rear surface side of the vegetable compartment 300 is connected to the rear air passage 21 in communication. The other end of the air passage 22 is connected to the return port 23 to the air passage 20, and an outlet 302 of the vegetable compartment 300 is provided in the air passage 22. In addition, the outlet 402 of the switching chamber 400 and the outlet 202a of the freezing chamber 200 communicate with each other through an air passage (not shown), and the outlet 502 of the ice making chamber 500 and the outlet 202b of the freezing chamber 200 are not shown. Communicated by

(Refrigeration cycle operation and internal air flow)
Next, the operation of the refrigeration cycle mounted on the refrigerator-freezer 50 and the air flow in the refrigerator-freezer 50 will be described.

  First, operation | movement of the refrigerating cycle mounted in the refrigerator-freezer 50 is demonstrated. As shown in FIG. 3, the refrigeration cycle installed in the refrigerator 50 includes a compressor 12 that compresses the refrigerant, a condenser 13 that condenses the refrigerant, a throttling device 14 that decompresses the refrigerant, and a heat exchanger that evaporates the refrigerant. 1 (evaporator) is sequentially connected by piping. The high-temperature and high-pressure gaseous refrigerant compressed by the compressor 12 flows into the condenser 13. Then, it condenses and liquefies while radiating heat to the air around the condenser 13 and becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant exiting the condenser 13 flows into the expansion device 14. The high-pressure liquid refrigerant is squeezed and expanded (depressurized) by the expansion device 14 to be in a low-temperature and low-pressure gas-liquid two-phase state. The low-temperature and low-pressure gas-liquid two-phase refrigerant that has left the expansion device 14 flows into the heat exchanger 1. And it absorbs heat from the air inside the refrigerator-freezer 50 and becomes a low-temperature and low-pressure vapor refrigerant. That is, the air inside the refrigerator-freezer 50 is cooled. The low-temperature and low-pressure vapor refrigerant exiting the heat exchanger 1 flows into the compressor 12 and is compressed.

Then, the air flow in the refrigerator-freezer 50 is demonstrated.
As shown in FIG. 4, a part of the air cooled by the heat exchanger 1 flows into the refrigerator compartment 100 from the inlet 101 through the air passage 20. Further, a part of the air cooled by the heat exchanger 1 flows into the ice making chamber 500 from the inlet 501 through the air passage 20, as shown in FIG. Similarly, part of the air cooled by the heat exchanger 1 flows into the switching chamber 400 from the inlet 401 through the air passage 20. A part of the air cooled by the heat exchanger 1 flows into the freezer compartment 200 from the inlets 201a and 201b through an air passage (not shown).

  As shown in FIG. 2, the air that has flowed into the refrigerator compartment 100 flows into the rear air passage 21 from the outlet 102. A part of this air flows into the vegetable compartment 300 from the inlet 301 and flows out from the outlet 302. On the other hand, the remainder of the air that has flowed into the refrigerator compartment 100 flows into the air passage 22. Then, it merges with the air flowing in from the outlet 302 and flows into the air flow upstream side of the cooling chamber 8 from the return port 23. Since the air flowing in from the return port 23 passes through the refrigerator compartment 100 and the vegetable compartment 300, it is hot and humid air.

  The air that has flowed into the freezing chamber 200 flows out from the inlets 201 a and 201 b, merges with the air that flows out from each of the switching chamber 400 and the ice making chamber 500, and flows upstream in the air flow of the cooling chamber 8. This air has a low humidity because of its low temperature.

Next, the details of the heat exchanger 1 will be described.
FIG. 5 is a front view of the heat exchanger according to the first embodiment (viewed from the vegetable compartment 300 side in FIG. 2). FIG. 6 is a side sectional view of FIG. Here, in the description of the heat exchanger 1, the drawing coordinates after FIG. 5 are defined as follows. The stacking direction of the fins 4, that is, the horizontal direction in FIG. The direction parallel to the air flow, that is, the direction perpendicular to the paper surface in FIG. A direction perpendicular to the stacking direction and the column direction, that is, a direction orthogonal to the paper surface in FIG.
In addition, the arrow shown in a figure is an air flow direction, 2 is an air flow upstream side, 3 becomes an air flow downstream side. In FIG. 5, area A is a range that does not face return port 23 in the stacking direction, and area B is a range that faces return port 23 in the stacking direction.

  The heat exchange 1 provided in the cooling chamber 8 includes fins 4 and tubes 5 that are heat transfer tubes. For example, the flat fins 4 are stacked in the stacking direction at intervals of the fin pitch p. The laminated fins 4 are arranged in parallel in seven rows (hereinafter referred to as fin groups when necessary). And this fin group is arranged in three steps in the step direction. In addition, for example, an aluminum tube 5 is penetrated in each of the fins 4 in the stacking direction while being bent in a meandering manner at the end thereof. By making the pipe 5 made of aluminum, the material cost can be reduced as compared with the copper pipe. Since aluminum is difficult to weld, the tube 5 is bent in advance after passing through the fins 4 into the tube 5 to form the heat exchanger 1 as shown in FIG. When the refrigerant flowing in the pipe is flammable, such as R600a, the smaller the welded portion, the less the risk of refrigerant leakage and the greater the safety.

  In the first embodiment, the fins 4 have a flat plate shape. However, in order to improve heat exchange performance, for example, the fins 4 may have a corrugated shape. A slit or the like may be formed in the fin 4. In the first embodiment, the number of penetrations of the pipe 5 in one fin 4 is one, but the pipe 5 may penetrate a plurality of places with respect to one fin 4.

As shown in FIG. 5, the fin pitch p has the largest fin pitch p between the fins 4 located on the air flow upstream side 2, and the fin pitch p decreases gradually toward the air flow downstream side 3. It has become.
Note that the fin pitch p does not have to be gradually reduced from the air flow upstream side 2 to the air flow downstream side 3, and the air flow downstream side 3 rather than the fin pitch p between the fins 4 located on the air flow upstream side 2. There may be a range in which the fin pitch p between the fins 4 located in the region is larger. The fin pitch p may be a constant size regardless of the upstream side and downstream side of the air flow.

  As shown in FIG. 6, a stepwise gap x is formed between the fins 4 adjacent in the stepwise direction. This stepwise gap x has the largest stepwise gap x between the fins 4 located on the upstream side 2 of the air flow, and the stepwise gap x gradually decreases toward the downstream side 3 of the airflow. . The size of the stepwise gap x is adjusted by changing the stepwise width y of the fins 4 for each row. By configuring the heat exchanger 1 in this manner, the width z of the heat exchanger 1 can be unified, so that the heat exchanger 1 can be easily installed. At this time, the fins 4 of the fin group provided on both outer sides in the step direction are arranged so as to contact the partition wall 6 and the back wall 7.

  Note that the stepwise gap x does not need to be sequentially reduced from the airflow upstream side 2 to the airflow downstream side 3, and is downstream of the airflow downstream than the stepwise gap x between the fins 4 located on the airflow upstream side 2. There may be a range where the stepwise gap x between the fins 4 located on the side 3 is larger. The stepwise gap x may be a constant size regardless of the upstream side and downstream side of the air flow.

  In the first embodiment, the row gap between the fins 4 adjacent to each other in the row direction is constant. However, the gap in the row direction between the fins 4 located on the upstream side 2 of the air flow is increased to increase the air flow. As it goes to the downstream side 3, the column-direction gaps may be sequentially reduced.

  Further, in the first embodiment, the stepwise width y of the fins 4 is adjusted for each row to form the stepwise gap x. However, as shown in FIG. The stepwise gap x may be formed by adjusting the parallel arrangement interval of the four stepwise directions. By configuring in this way, it is not necessary to arrange the fins 4 according to size when manufacturing the heat exchanger 1, and productivity is improved. Also at this time, the fins 4 of the fin group provided on both outer sides in the step direction are arranged so as to be in contact with the partition wall 6 and the back wall 7.

(Operation)
Next, the operation of the heat exchanger 1 will be described.
The air that has flowed into the heat exchanger 1 from the upstream side 2 of the air flow becomes frost as the moisture in the air is cooled by the fins 4 and the tubes 5 of the heat exchanger 1. At this time, the air on the upstream side 2 of the air flow contains more moisture than the air on the downstream side 3 of the air flow, so that frosting is likely to occur. Normally, the air path is blocked by frost formation on the upstream side 2 of the air flow, and the heat exchanger 1 cannot cool the air. However, since the heat exchanger 1 according to the first embodiment forms the stepwise gap x between the fins 4 adjacent to each other in the stepwise direction, even if the airflow frost is formed on the upstream side 2 of the airflow, the air passage is still present. Secured.

  Further, in the first embodiment, the stepwise gap x is the largest in the stepwise gap x between the fins 4 located on the upstream side 2 of the air flow, and sequentially toward the downstream side 3 of the airflow. The stepwise gap x is small. For this reason, the air flow upstream side 2 with a small amount of cooling material is difficult to form frost, and the heat exchanger 1 is uniformly frosted from the air flow upstream side 2 to the air flow downstream side 3.

  When the distance between the fins 4 of the fin group provided on both outer sides in the step direction and the partition wall 6 and the back wall 7 is large, the air easily flows between them, and the conventional one provided on the side wall of the heat exchanger. It will be the same as the bypass air passage. However, in the first embodiment, the fins 4 of the fin group provided on both outer sides in the step direction are arranged so as to contact the partition wall 6 and the back wall 7. For this reason, the air in the heat exchanger 1 tends to flow into the stepwise gap x. The air flowing through the bypass air passage has flowed through the side surface of the heat exchanger. However, since the air flowing through the stepwise gap x flows through the heat exchanger 1, the effective air volume increases more than through the bypass air passage. Since the air flowing through the bypass air passage is in contact with the fins on only one side, air that circulates without being sufficiently cooled is generated. However, the air flowing through the stepwise gap x is in contact with the fins on both sides, thereby improving the refrigerating capacity.

  Moreover, since the front edge part of the fin 4 increases by arrange | positioning the several fin 4 in a row direction, the temperature boundary layer formed in a heat exchanger is divided | segmented for every fin 4, and cooling of the heat exchanger 1 is carried out. Performance is improved.

  Since the heat exchanger 1 configured in this way forms a stepwise gap x between the fins 4 adjacent to each other in the stepwise direction, an air passage is secured even if frost is formed on the upstream side 2 of the airflow. Further, clogging due to frost formation can be prevented. In addition, the air that has flowed into the heat exchanger 1 easily flows through the step gap x with little pressure loss and comes into contact with the fins 4 on both sides, so that the effective air volume increases and the refrigeration performance of the heat exchanger 1 improves.

  In the first embodiment, the stepwise gap x is the largest in the stepwise gap x between the fins 4 located on the upstream side 2 of the air flow, and sequentially toward the downstream side 3 of the airflow. The stepwise gap x is small. For this reason, the air flow upstream side 2 with a small amount of cooling material is difficult to form frost, and the heat exchanger 1 is uniformly frosted from the air flow upstream side 2 to the air flow downstream side 3. Therefore, clogging due to frost formation is prevented and cooling performance is further improved.

  Moreover, since the front edge part of the fin 4 increases by arrange | positioning the several fin 4 in a row direction, the temperature boundary layer formed in a heat exchanger is divided | segmented for every fin 4, and cooling of the heat exchanger 1 is carried out. Performance is improved. For this reason, it is possible to suppress a decrease in the cooling performance of the heat exchanger 1 due to the decrease in the heat transfer area of the fins 4 caused by forming the stepwise gap x.

Moreover, since the refrigerator-freezer 50 comprised in this way is equipped with the heat exchanger 1 with the high effect which prevents the clogging by frost formation, and high cooling performance, the fall of the inside temperature becomes early and the compressor of the compressor The operation rate decreases because the operation time is shortened. Since most of the power consumption of the refrigerator / freezer 50 is the power of the compressor 12, reducing the operation rate of the compressor 12 saves energy. Moreover, since the lifetime of the compressor 12 will be extended if an operation rate falls, the refrigerator-freezer 50 can be used for a long term.
Here, the operation rate of the compressor is (compressor operation time) / (compressor operation time and stop time).

In the first embodiment, the stepwise gaps x formed in the same row are the same. However, the stepwise gap x of the area B through which the hot and humid air that has passed through the refrigerator compartment 100 and the vegetable compartment 300 flows is provided. , It may be larger than the stepwise gap x in area A.
FIG. 8 is a side sectional view (area B) showing another example of the heat exchanger according to the first embodiment. Similar to the area A (FIG. 6), a stepwise gap x is formed between the fins 4 adjacent in the stepwise direction. This stepwise gap x has the largest stepwise gap x between the fins 4 located on the upstream side 2 of the air flow, and the stepwise gap x gradually decreases toward the downstream side 3 of the airflow. .

  The air returning from the refrigerator compartment 100 and the vegetable compartment 300 has a high temperature of about 3 to 10 ° C. and contains a large amount of moisture in the food. It is easy to form frost in the heat exchanger 1. For this reason, the stepwise gap x formed in area B is larger than the stepwise gap x formed in area A of the same row. In this way, by increasing the stepwise gap x in the area B where frost formation is likely to occur, the heat exchanger 1 can be more uniformly frosted, so that the cooling performance of the heat exchanger 1 can be maintained. Further, since the number of fins 4 is reduced, the heat exchanger 1 and the refrigerator / freezer 50 can be reduced in weight.

  Further, as shown in FIG. 9, even if the fin pitch p formed in the area B is made larger than the fin pitch p formed in the area A of the same row, the frost formation can be made uniform and the cooling performance can be maintained. it can.

Embodiment 2. FIG.
In the first embodiment, each fin group has the same configuration, but the configuration may be changed for each fin group.
In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

  FIG. 10 is a plan sectional view of the heat exchanger according to the second embodiment. The fin pitch p between the fins 4 provided in the fin group located in the center part in the step direction is larger than the fin pitch p between the fins 4 provided in the fin group located on both outer sides in the step direction. .

  By comprising in this way, the air which flowed in into the heat exchanger 1 becomes easy to flow through the fin group of the stage direction center part with few pressure losses. For this reason, compared with the conventional heat exchanger which provided the bypass air path in the side part side of the heat exchanger, an effective air volume increases. Further, since the space near the central portion of the heat exchanger 1 is increased, frost can easily reach the downstream side, so that clogging can be prevented.

Embodiment 3 FIG.
In the first embodiment and the second embodiment, the heat exchanger 1 that has a high effect of preventing clogging due to frost formation and high cooling performance by forming the stepwise gap x between the fins 4 adjacent in the stepwise direction. Got. Even if the notch is formed in the fin 4 instead of the stepwise gap x, it is possible to obtain the heat exchanger 1 having a high effect of preventing clogging due to frost formation and high cooling performance.
In Embodiment 3, items that are not particularly described are the same as those in Embodiments 1 and 2, and the same functions and configurations are described using the same reference numerals.

  FIG. 11 is a side cross-sectional view of the heat exchanger according to the third embodiment. The heat exchange 1 provided in the cooling chamber 8 includes fins 4 and tubes 5 that are heat transfer tubes. For example, the flat fins 4 are arranged in 7 rows in the row direction. Each of these fins 4 is formed with a notch 10 on the upstream side 2 of the air flow. In addition, for example, an aluminum tube 5 is penetrated in each of the fins 4 in the stacking direction while being bent in a meandering manner at the end thereof.

  In the heat exchanger 1 configured in this manner, the notch 10 is formed in the air flow upstream side 2 between the fins 4. Clogging due to frost can be prevented. Moreover, since the air which flowed into the heat exchanger 1 flows through the notch 10 with little pressure loss and contacts the fins 4 on both sides, the effective air volume increases and the refrigeration performance of the heat exchanger 1 is improved.

  Moreover, since the front edge part of the fin 4 increases by arrange | positioning the several fin 4 in a row direction, the temperature boundary layer formed in a heat exchanger is divided | segmented for every fin 4, and cooling of the heat exchanger 1 is carried out. Performance is improved. For this reason, it is possible to suppress a decrease in the cooling performance of the heat exchanger 1 due to the decrease in the heat transfer area of the fins 4 due to the formation of the notches 10.

  Moreover, compared with the case where the plurality of fins 4 are arranged in the step direction (Embodiment 1 and Embodiment 2), the step of arranging the fins 4 in the manufacturing process can be reduced. Further, when the pipe 5 is bent after passing through the pipe 5 through the fin 4, the pipe 5 is fixed in the step direction, so that a plurality of pipes 5 can be bent at the same time. For this reason, the productivity of the heat exchanger 1 is improved.

  Moreover, since the refrigerator-freezer 50 comprised in this way is equipped with the heat exchanger 1 with the high effect which prevents the clogging by frost formation, and high cooling performance, the fall of the inside temperature becomes early and the compressor of the compressor The operation rate decreases because the operation time is shortened. Since most of the power consumption of the refrigerator / freezer 50 is the power of the compressor 12, reducing the operation rate of the compressor 12 saves energy. Moreover, since the lifetime of the compressor 12 will be extended if an operation rate falls, the refrigerator-freezer 50 can be used for a long term.

  In the third embodiment, as in the first embodiment, the notch 10 of the fin 4 provided in the area B through which the hot and humid air flows is replaced by the notch 10 of the fin 4 provided in the area A. May be larger.

  FIG. 12 is a side sectional view (area B) showing another example of the heat exchanger according to the third embodiment. Similar to the area A (FIG. 11), a notch 10 is formed between the fins 4 on the upstream side 2 of the air flow. The width w of the notch 10 formed in the area B is larger than the width w of the notch 10 formed in the area A. In the third embodiment, the size of the notch 10 is adjusted by the width w of the notch 10, but the size of the notch 10 may be adjusted by the depth d of the notch 10. The size of the notch 10 may be adjusted by both the width w of the notch 10 and the depth d of the notch 10. The depth d of the notch 10 corresponds to the width of the notch in the row direction in the present invention.

  The air returning from the refrigerator compartment 100 and the vegetable compartment 300 has a high temperature of about 3 to 10 ° C. and contains a large amount of moisture in the food. It is easy to form frost in the heat exchanger 1. For this reason, the notch 10 of the fin 4 provided in the area B is larger than the notch 10 of the fin 4 provided in the area A of the same row. Thus, by enlarging the notch 10 in the area B where frost formation is likely to occur, the heat exchanger 1 can be more uniformly frosted, so that the cooling performance of the heat exchanger 1 can be maintained.

  Similarly to the first embodiment, the size of the notches 10 formed in the fins 4 located on the air flow upstream side 2 is increased, and the sizes of the notches 10 are sequentially increased toward the air flow downstream side 3. May be reduced.

FIG. 13 is a side sectional view showing another example of the heat exchanger according to the third embodiment. The width w and depth d of the notch 10 formed in the fin 4 located on the air flow upstream side 2 side are the largest, and the width w and the depth of the notch 10 are sequentially increased toward the air flow downstream side 3. The depth d is small.
In the third embodiment, the size of the notch 10 is adjusted by both the width w and the depth d of the notch 10. However, the size of the notch 10 is adjusted by the depth w of the notch 10. Also good. The size of the notch 10 may be adjusted by the depth d of the notch 10. The size of the notch 10 does not have to be sequentially reduced from the air flow upstream side 2 to the air flow downstream side 3, and the air flow downstream of the size of the notch 10 of the fin 4 located on the air flow upstream side 2. There may be a range in which the size of the notch 10 of the fin 4 located on the side 3 is larger.

  In this way, the notch 10 on the upstream side 2 of the air flow that is likely to be frosted is made larger, and the notch 10 on the downstream side 3 of the air flow that is hard to be frosted is made smaller, so 2 to the air flow downstream side 3 are uniformly frosted. Therefore, clogging due to frost formation is prevented and cooling performance is further improved.

  In the third embodiment, the shape of the notch 10 is substantially rectangular, but various shapes are possible. Further, it may not be provided on the air flow upstream side 2. For example, a hole may be formed in the fin 4 to form the notch 10. By doing in this way, it is possible to prevent the fins 4 from being bent during production or transportation of the heat exchanger 1 and to suppress variations in performance of the heat exchanger 1.

1 is an external perspective view of a refrigerator-freezer according to Embodiment 1. FIG. It is D-D 'sectional drawing of FIG. FIG. 3 is a cross-sectional view taken along line E-E ′ of FIG. 2. FIG. 3 is a cross-sectional view taken along the line F-F ′ in FIG. 2. 3 is a front view of the heat exchanger according to Embodiment 1. FIG. It is side surface sectional drawing of FIG. It is side surface sectional drawing which shows another example of the heat exchanger which concerns on Embodiment 1. FIG. It is side surface sectional drawing (area B) which shows another example of the heat exchanger which concerns on Embodiment 1. FIG. It is a front view of another example of the heat exchanger which concerns on Embodiment 1. FIG. 3 is a plan sectional view of a heat exchanger according to Embodiment 2. FIG. FIG. 6 is a side cross-sectional view of a heat exchanger according to Embodiment 3. It is side surface sectional drawing (area B) which shows another example of the heat exchanger which concerns on Embodiment 3. FIG. FIG. 6 is a side cross-sectional view showing another example of a heat exchanger according to Embodiment 3.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Heat exchanger (evaporator), 2 Air flow upstream, 3 Air flow downstream, 4 Fin, 5 pipe, 6 Partition wall, 7 Back wall, 8 Cooling chamber, 10 Notch, 11 Blower, 12 Compressor, 13 condenser, 14 throttle device, 20 air passage, 21 back air passage, 22 air passage, 23 return port, 50 refrigerator-freezer, 100 refrigerator compartment, 101 inlet, 102 outlet, 200 freezer compartment, 201a, 201b inlet 202a, 202b Outlet, 300 Vegetable room, 301 Inlet, 302 Outlet, 400 Switching room, 401 Inlet, 402 Outlet, 500 Ice making room, 501 Inlet, 502 Outlet, p fin pitch, x-stage direction Gap, y Stepwise width of the fin 4, z Stepwise width of the heat exchanger 1, w Notch width, d Notch depth.

Claims (6)

A heat exchanger comprising a plurality of fins laminated at a predetermined interval and a heat transfer tube penetrating the fins in the lamination direction,
The fin is
Plurally arranged in a row direction that is a direction perpendicular to the stacking direction and the air flow direction, and a step direction that is a direction perpendicular to the stacking direction and the row direction,
A stepwise gap is formed between the fins adjacent in the stepwise direction ,
The stepwise gap of the fin located on the air flow downstream side is formed smaller than the stepwise gap of the fin located on the air flow upstream side,
The stepwise gap is formed by adjusting the stepwise width of the fin . 2. The heat exchanger according to claim 1 , wherein the stepwise gap is gradually reduced from an air flow upstream side to an air flow downstream side. A fin group consisting of the fins stacked in a row at a predetermined interval and arranged in a row direction,
In the same row, the stacking interval of the fins in the fin group excluding the fin group on both outer sides in the step direction is larger than the stacking interval of the fins in the fin group on both outer sides in the step direction. The heat exchanger according to claim 1 or 2 . A refrigerator-freezer comprising the heat exchanger according to any one of claims 1 to 3 . An outlet is provided through which air that flows through at least one of the refrigerator compartment and the vegetable compartment flows out,
The heat exchanger is provided on the downstream side of the air flow of the outlet,
The stepwise gap of the fin located in a range facing the outflow port in the stacking direction is
5. The refrigerator-freezer according to claim 4 , wherein the gap is larger than the gap in the step direction of the fins in the same row located in a range not facing the outlet in the stacking direction. The stacking interval of the fins located in a range facing the outlet in the stacking direction is
6. The refrigerator-freezer according to claim 4 , wherein the refrigerator interval is larger than a stacking interval of the fins in the same row located in a range not facing the outlet in the stacking direction.

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