JP2009138995A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger improved in the heat exchange efficiency of a peripheral area of a fin elongated hole hard to perform heat exchange inside the adjacent refrigerant pipes, also improved in heat exchange performance, and coping with the thinning of a material and rationalization. <P>SOLUTION: In this heat exchanger 1, a zigzag refrigerant pipe 4 having straight pipe parts and bent pipe parts is pressed in elongated holes formed in plate fins 6. Only the straight part of the elongated hole formed in the plate fin 6 is provided with a drift 7, whereby heat exchange efficiency is improved, and the performance of the heat exchanger 1 is heightened to cope with the thinning of the material and rationalization. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a heat exchanger used as a cooler or the like in refrigeration equipment such as a refrigerator.

  In recent years, for example, in refrigerators, there is a tendency to increase the internal capacity by fixing the outer dimensions of the main body, and as a result, the cooling system-related parts are required to be more compact year by year.

  In this, the heat exchanger is also required to be compact, and the demand for a thin heat exchanger is increasing.

  On the other hand, the demand for rationalization of component materials has increased due to soaring raw materials, and in addition to improving the performance of heat exchangers, there has been a demand for rationalization of thin materials.

  As an example, a heat exchanger in which plate fins are processed is known in order to improve performance in a heat exchanger used for a refrigeration apparatus or the like (see, for example, Patent Document 1).

  16 to 19 show a conventional heat exchanger described in Patent Document 1.

The configuration of the conventional heat exchanger 101 is a serpent type heat exchanger in which the refrigerant pipe 102 is bent in a meandering manner, and the bent refrigerant pipe 102 is inserted into a long hole 104 provided in the plate fin 103. The burring portion 105 having an angle with respect to the plate fin 103 is provided by cutting and raising the edge of the long hole 104.
Japanese Patent No. 2811601

  However, in the above-described conventional configuration, for example, in the case of a refrigerator, when frosting occurs on the plate fins 103 of the heat exchanger during operation, frost concentrates on the burring 105 portion provided in the long hole 104, and mutual plates There was a problem that frost was clogged between the fins 103 and the air volume was reduced.

  Further, in the above-described conventional configuration, drain water tends to remain in the burring 105 portion provided in the long hole 104 during defrosting. As a result, the drain water is frozen after the operation of the refrigerator, and frost is concentrated on the drain water. The clogging due to frost in the plate fins 103 is accelerated, and this causes a problem that the airflow is rapidly reduced.

  The present invention solves the above-described conventional problems, and an object of the present invention is to provide a high-efficiency heat exchanger in which frost does not concentrate on the plate fins and the air volume does not decrease during operation of the cooler.

  In order to solve the above-described conventional problems, the heat exchanger of the present invention has a long hole-like through-hole formed in a plate fin with a refrigerant pipe processed into a meandering shape in which straight pipe portions and curved pipe portions are alternately continuous. A heat exchanger configured to be press-fitted into a hole, provided with a drifting portion that protrudes from the surface of the plate fin toward the long side of the through hole so that the center of the long side is at the highest position. It is.

  By forming the drift portion, the tensile strength in the plate fin surface direction can be improved, the adhesion between the refrigerant pipe and the plate fin can be improved, the heat transfer performance can be improved, and the thin material of the plate fin can be rationalized. Can also respond.

  In addition, the formation of the drifting portion turbulent airflow, reducing the water stop area, and facilitating the flow of airflow to adjacent fins, thereby improving the heat transfer rate on the air side and improving the performance of the heat exchanger. Can do.

  The heat exchanger of the present invention can provide a heat exchanger that improves the heat exchange performance by improving the tensile strength in the surface direction of the plate fins, and further supports the rationalization of the thin material.

  The invention according to claim 1 is a plurality of plates in which a refrigerant pipe processed into a meandering shape in which straight pipe portions and curved pipe portions are alternately continuous, and an elongated through hole through which the refrigerant pipe passes are formed. A heat exchanger in which the straight pipe part is in close contact with the plate fin by passing through the through hole by the bent pipe part of the refrigerant pipe, the rectangular hole and the circular part And having a circular hole shape in which the circular portions are continuously formed on both short sides of the rectangular portion, and in the plate fin, from the surface thereof toward the long side of the rectangular portion in the through hole, A drifting portion that protrudes so that the center of the long side is at the highest position is provided.

  By setting it as this structure, the tensile strength of the plate fin surface direction improves with formation of the said drift part, and the adhesive force of a refrigerant | coolant pipe and a plate fin can be improved. As a result, the heat transfer performance can be improved, the plate fin can be further thinned, and the material rationalization can be dealt with.

  In addition, the formation of the drift portion causes turbulence in the airflow passing between the plate fins. As a result, the water stop area in the plate fins is reduced, and the airflow easily flows to the adjacent fins. The heat transfer rate is improved, and the heat exchanger performance can be improved.

  According to a second aspect of the present invention, in the heat exchanger according to the first aspect, the drift portion is provided on the same surface with the through hole interposed therebetween.

  As a result, the water stop area in the plate fin is further reduced, the tensile strength in the surface direction on both sides sandwiching the through hole is improved, and the adhesion with the refrigerant pipe can be further improved, and as a result, the heat transfer performance Can be further improved.

  Moreover, the flow of the airflow to adjacent fins also becomes wider, and the heat transfer coefficient on the air side can be further improved.

  According to a third aspect of the present invention, in the heat exchanger according to the first or second aspect, the drift portions are provided on the front and back surfaces, respectively.

  With such a configuration, a complicated turbulent flow is generated by the airflow passing between the plate fins. As a result, the water stop area in the plate fins is further reduced, and the airflow flowing to the adjacent fins also flows over a wider range. As a result, the heat transfer coefficient on the air side can be further improved, and the heat exchanger performance can be further improved.

  The invention according to claim 4 is the heat exchanger according to any one of claims 1 to 3, wherein the through hole is formed so that the straight pipe portion of the refrigerant pipe does not overlap with the flow of wind. The central axis is provided to be inclined with respect to the wind flow.

  By setting it as this structure, the airflow which flows between plate fins can be passed over a wider range, and the performance of a heat exchanger can be improved more.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a front view of a heat exchanger according to Embodiment 1 of the present invention. FIG. 2 is a left side view of the heat exchanger according to the first embodiment. FIG. 3 is a right side view of the heat exchanger according to the first embodiment. FIG. 4 is a front view of plate fins in the heat exchanger. FIG. 5 is a side view of plate fins in the heat exchanger. Drawing 6 is a mimetic diagram from the front showing the state of the air current which flows through the plate fin of the heat exchanger. FIG. 7 is a schematic view from the side showing the state of airflow flowing through the plate fins of the heat exchanger.

  1, 2, and 3, the heat exchanger 1 is used as a cooler in a refrigerator refrigeration system, for example, and is processed into a meandering shape in which straight pipe portions 2 and curved pipe portions 3 are alternately continuous. And a plurality of plate fins 6 each having an elongated through hole 5 through which the refrigerant pipe 4 passes.

  The straight pipe part 2 of the refrigerant pipe 4 is in close contact with the plate fin 6 by the curved pipe part 3 of the refrigerant pipe 4 passing through the through hole 5.

  The through hole 5 has a rectangular portion 5a and a circular portion 5b, and is formed in a long hole shape in which the circular portions 5b are continuously formed on both short sides of the rectangular portion 5a.

  Further, the plate fin 6 has a drift portion 7 protruding from the surface thereof toward the long side of the rectangular portion 5a in the through hole 5 so that the center portion of the long side is at the highest position. It is provided so as to face each other.

  Each drifting portion 7 is formed so as to be a substantially triangular pyramid in the first embodiment because the ridgeline is formed to be a straight line. The drift portion 7 is formed by mold processing after the through hole 5 is formed.

  In the heat exchanger 1 configured as described above, the flow of wind passing between the plate fins 6 will be described.

  As shown in FIGS. 6 and 7, the airflow for heat exchange passes from below the plate fin 6 upward. This flow is the same as shown by the arrows in FIG.

  As shown in FIG. 6, in the airflow flowing on the left side in the figure, the airflow A that passes through the part away from the refrigerant pipe 4 travels substantially straight when viewed in plan, and the airflow B that passes through the part close to the drift portion 7 is After passing through the refrigerant pipe 4 in the previous stage, the direction is changed so as to pass through the drift portion 7 side by an attracting action generated in the space immediately after passing through the refrigerant pipe 4, and the drift portion 7 is ridden. When passing through the drifting portion 7, the ridgeline of the drifting portion 7 is inclined, so that it drifts slightly outward and passes through the plate fin 6.

  Further, in the airflow flowing on the right side in the figure, the airflow C passing through a portion away from the refrigerant pipe 4 travels substantially straight as viewed in a plan view, and the airflow D passing through the drift portion 7 rides on the drift portion 7. When the refrigerant pipe 4 is passed through the latter stage, the refrigerant pipe 4 is divided as a boundary, and the airflow on the right side in the figure bypasses the right side of the refrigerant pipe 4 and passes through the plate fins 6. Bypasses the left side of the refrigerant pipe 4.

  In particular, when viewed three-dimensionally, the airflow that bypasses the left side of the airflow D, as shown in FIG. 7, is an airflow that passes between the plate fins 6 and a through-hole of the plate fin 6 that is adjacent from between the plate fins 6. 5 (dashed line portion), and is roughly classified into an airflow that merges with an airflow that flows on the surface of the adjacent plate fin 6.

  The merged airflow is affected by the airflow over the drifting portion 7 and passes through the through hole 5, and the air does not stagnate around the through hole 5 due to the airflow.

  As a result, the water stop area in the plate fin 6 is reduced, the air flow is complicated, the heat transfer rate on the air side is improved, the heat exchange action is activated, and the heat exchange performance can be improved.

  In the heat exchanger 1 shown in FIG. 1, the air flow is fast in the portion where the fin pitch at the front stage is large, and the wind speed flowing between the plate fins 6 is fast, and the air pressure loss is small. In a portion where the fin pitch is small, the wind speed is lowered, the ventilation pressure loss is increased, and a large turbulent action can be expected.

  Therefore, in a portion where the fin pitch is small, a larger heat exchange action can be expected, and an improvement in heat exchange capability can be expected.

  Furthermore, since the drift portion 7 protrudes three-dimensionally in a substantially triangular pyramid shape around the through-hole 5, the bending strength is increased and the tensile strength in the surface direction of the plate fin 6 is improved, so that the refrigerant pipe 4 and the plate fin 6 can be improved and the heat transfer performance can be maintained and improved. In addition, since the adhesion force can be maintained even when the plate fin 6 is thinned, it is possible to cope with rationalization of material costs accompanying the thinning.

  Furthermore, since the stagnation of the airflow generated around the through-hole 5 is suppressed, frost formation partially concentrated like the conventional burring shape is suppressed, and the plate fin 6 can be frosted substantially uniformly. . As a result, the residual drain water after defrosting can be suppressed, and stable heat exchange performance can be ensured.

(Embodiment 2)
FIG. 8 is a front view of the plate fins of the heat exchanger according to Embodiment 2 of the present invention. FIG. 9 is a side view of plate fins in the heat exchanger. The same constituent elements as those in the first embodiment will be described with the same reference numerals.

  The plate fins 16 shown in FIGS. 8 and 9 are attached to the refrigerant pipe 4 in the same manner as the plate fins 6 in the first embodiment, and the drifting portion 7 is provided only on one side of the through hole 5. This is different from the first embodiment.

  Therefore, the plate fins 16 can also cause turbulence in the airflow passing between the plate fins 16 by the drift portion 7, and the airflows that pass through the through holes 5 and divert to the surface of the adjacent plate fins 16. Can be generated.

  As a result, as in the first embodiment, the water stop area in the plate fins 16 can be reduced, the air flow is complicated, the air-side heat transfer coefficient is improved, and the heat exchange action is also activated. The heat exchange performance can be improved.

  Further, the three-dimensional protrusion of the drift portion 7 improves the tensile strength in the surface direction of the plate fin 16, improves the adhesion between the refrigerant pipe 4 and the plate fin 16, maintains the heat transfer performance, and improves the plate fin 16. It is possible to cope with rationalization of material costs accompanying the thinning of the material.

  Further, as in the first embodiment, since the stagnation of airflow generated around the through hole 5 is suppressed, the plate fins 16 can be frosted substantially uniformly, and the residual drain water after defrosting is suppressed. Thus, stable heat exchange performance can be ensured.

(Embodiment 3)
FIG. 10 is a front view of a plate fin of the heat exchanger according to Embodiment 3 of the present invention. FIG. 11 is a side view of plate fins in the heat exchanger. The same constituent elements as those in the first embodiment will be described with the same reference numerals.

  The plate fins 26 shown in FIGS. 10 and 11 are attached to the refrigerant pipe 4 in the same manner as the plate fins 6 in the first embodiment, and the drift portions 7a and 7b are disposed on both sides of the through hole 5 therebetween. Although the point which is located is the same, it differs from Embodiment 1 by the point which provided the one drift part 7a on the surface side, and the other drift part 7b each protruded in the back surface side.

  Therefore, even with such plate fins 26, turbulent flow can be generated in the airflow passing between the plate fins 26 by the drift portion 7, and the airflow diverted to the surface of the adjacent plate fins 26 through the through holes 5 can be generated. Can be generated.

  In particular, each of the drift portions 7a and 7b is in a state in which the projecting direction is different from the front surface side and the back surface side, so that the complexity increases due to the airflow passing through the through holes 5 of the adjacent plate fins 26. It can be expected that the water stop area in the plate fin 26 is reduced more than the first embodiment, the air flow becomes more complicated, the heat exchange action is further activated, and the heat exchange performance can be further improved.

  Furthermore, due to the three-dimensional protrusions of the drift portions 7a and 7b, the tensile strength in the surface direction of the plate fin 26 is improved as in the first embodiment, the adhesion between the refrigerant pipe 4 and the plate fin 26 is improved, and the transmission is improved. The maintenance and improvement of the thermal performance and the rationalization of the material cost associated with the thinning of the plate fin 26 can be dealt with.

  Further, as in the first embodiment, since the stagnation of the airflow generated around the through hole 5 is suppressed, the plate fin 26 can be frosted substantially uniformly, and the residual drain water after defrosting is suppressed. Thus, stable heat exchange performance can be ensured.

(Embodiment 4)
FIG. 12 is a front view of a plate fin of the heat exchanger according to Embodiment 4 of the present invention. FIG. 13 is a side view of plate fins in the heat exchanger. The same constituent elements as those in the first embodiment will be described with the same reference numerals.

  The plate fins 36 shown in FIGS. 12 and 13 are attached to the refrigerant pipe 4 in the same manner as the plate fins 6 in the first embodiment, and the drift portions 17 are located on both sides of the through hole 5. Although the point which protrudes from the surface side is the same, as shown in FIG. 12, it differs from Embodiment 1 by the point which formed the drift part 17 so that it might become a substantially trapezoid seeing from a plane.

  Therefore, the plate fin 36 can also cause turbulent flow in the airflow passing between the plate fins 36 by the drifting portion 17, and the airflow that passes through the through hole 5 and is divided to the surface of the adjacent plate fin 36. Can be generated.

  As a result, similarly to the first embodiment, it can be expected that the water stop area in the plate fin 36 is reduced, and the heat transfer coefficient on the air side is improved. Further, the air flow becomes complicated, the heat exchange action is activated, and the heat exchange performance can be improved.

  Further, the three-dimensional protrusion of the drift portion 17 improves the tensile strength in the surface direction of the plate fin 36 as in the first embodiment, improves the adhesion between the refrigerant pipe 4 and the plate fin 36, and heat transfer performance. Therefore, it is possible to cope with the rationalization of the material cost accompanying the improvement and maintenance of the thickness of the plate fin 36.

  Further, as in the first embodiment, since the stagnation of the airflow generated around the through hole 5 is suppressed, the plate fin 36 can be frosted substantially uniformly, and the residual drain water after defrosting is suppressed. Thus, stable heat exchange performance can be ensured.

  Needless to say, the drift portion 17 may be configured such that one protrudes on the front side of the plate fin 36 and the other protrudes on the back side, as in the third embodiment. Therefore, it can be expected that the heat exchange performance is further improved.

(Embodiment 5)
FIG. 14 is a front view of a plate fin of the heat exchanger according to Embodiment 5 of the present invention. FIG. 15 is a side view of plate fins in the heat exchanger. The same constituent elements as those in the first embodiment will be described with the same reference numerals.

  The plate fins 46 shown in FIGS. 14 and 15 are attached to the refrigerant pipe 4 in the same manner as the plate fins 6 in the first embodiment, and the drift portions 27 are located on both sides of the through hole 5. However, as shown in FIGS. 14 and 15, the first embodiment is different from the first embodiment in that the drifting portion 27 is curved and formed so as to form a part of a hemispherical surface. Is different.

  Therefore, even with such plate fins 46, the turbulent flow can be generated in the airflow passing between the plate fins 46 by the drifting portion 27, and the airflow diverting to the surface of the adjacent plate fins 46 through the through holes 5 can be generated. Can be generated.

  As a result, as in the first embodiment, it can be expected that the water stop area in the plate fins 46 is reduced, the heat transfer rate on the air side is improved, and the air flow is complicated, and the heat exchange action is also active. The heat exchange performance can be improved.

  Further, the three-dimensional protrusion of the drift portion 27 improves the tensile strength in the surface direction of the plate fin 46 as in the first embodiment, improves the adhesion between the refrigerant pipe 4 and the plate fin 46, and heat transfer performance. It is also possible to cope with rationalization of the material cost accompanying the maintenance improvement of the plate fin 46 and the thinning of the plate fin 46.

  Further, as in the first embodiment, since the stagnation of the airflow generated around the through-hole 5 is suppressed, the plate fin 46 can be frosted substantially uniformly, and the residual drain water after defrosting is suppressed. Thus, stable heat exchange performance can be ensured.

  Needless to say, the drift portion 27 may be configured such that one protrudes on the front surface side of the plate fin 46 and the other protrudes on the back surface side, as in the third embodiment. Therefore, it can be expected that the heat exchange performance is further improved.

  Since the heat exchanger according to the present invention can ensure stable heat exchanger performance, it can be widely used as a refrigerator or a radiator of refrigeration equipment ranging from household use to industrial use such as refrigerators and vending machines. Is.

The front view of the heat exchanger in Embodiment 1 of this invention Left side view of the heat exchanger of the same embodiment Right side view of the heat exchanger of the same embodiment Front view of plate fin in heat exchanger of same embodiment Side view of plate fin in heat exchanger of same embodiment Schematic view from the front showing the state of airflow flowing through the plate fins in the heat exchanger of the same embodiment The schematic diagram from the side surface which shows the state of the airflow which flows through the plate fin in the heat exchanger of the embodiment The front view of the plate fin of the heat exchanger in Embodiment 2 of this invention Side view of plate fin in heat exchanger of same embodiment The front view of the plate fin of the heat exchanger in Embodiment 3 of this invention Side view of plate fin in heat exchanger of same embodiment The front view of the plate fin of the heat exchanger in Embodiment 4 of this invention Side view of plate fin in heat exchanger of same embodiment The front view of the plate fin of the heat exchanger in Embodiment 5 of this invention Side view of plate fin in heat exchanger of same embodiment Front view of conventional heat exchanger Side view of the conventional heat exchanger The front view which expanded the principal part of the plate fin in the conventional heat exchanger An enlarged side view of the main part of the plate fin in the conventional heat exchanger

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Straight pipe part 3 Curved pipe part 4 Refrigerant pipe 5 Through-hole 5a Rectangular part 5b Circle part 6 Plate bun 7 Drift part 7a Drift part 7b Drift part 16 Plate fin 17 Drift part 26 Plate fin 27 Drift part 36 Plate Fin 46 Plate fin

Claims (4)

  A straight pipe portion and a curved pipe portion that are alternately processed in a meandering manner, and a plurality of plate fins each having an elongated through hole through which the refrigerant pipe passes. A heat exchanger in which the straight pipe part is in close contact with the plate fin by passing through the bent pipe part of the refrigerant pipe, the through hole having a rectangular part and a circular part, and a short side on both sides of the rectangular part. In the plate fin, the center part of the long side is the highest position from the surface to the long side of the rectangular part in the through hole. A heat exchanger provided with a drifting portion protruding so as to become.   The heat exchanger according to claim 1, wherein the drifting portion is provided on the same surface with the through hole interposed therebetween.   The heat exchanger according to claim 1 or 2, wherein the drift portions are provided on the front and back surfaces, respectively.   The through-hole is provided so that the central axis thereof is inclined with respect to the wind flow so that the straight pipe portion of the refrigerant pipe does not overlap with the wind flow. The heat exchanger according to item.

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