KR20180095501A - Heat exchanger for refrigerator and refrigerator with refrigerator - Google Patents

Abstract

The present invention relates to a heat exchanger for a refrigerator and a refrigerator having the heat exchanger, wherein the heat exchanger for a refrigerator includes a plurality of heat transfer fins arranged in a continuous arrangement in opposed relation and arranged in multiple stages from the windward side to the downwind side, The heat transfer fins are offset in either the column direction and the width direction when the heat transfer pins are seen as a plan view.

Description

Heat exchanger for refrigerator and refrigerator with refrigerator

The present invention relates to a heat exchanger for a refrigerator and a refrigerator having the same.

BACKGROUND OF THE INVENTION 1. Field of the Invention [0002] The present invention relates to a heat exchanger for a refrigerator and a refrigerator having the same, and as disclosed in JP-A-2014-159884, a heat exchanger for refrigerant, Lt; / RTI >

In such a heat exchanger, there is a heat exchanger in which heat transfer fins are arranged in multiple stages from the windward side (windward side) on the upstream side in the air flow direction to the windward side (windward side) on the downstream side in the air flow direction.

In this heat exchanger, each of the heat transfer fins has a body portion disposed opposite to each other, and an inclined portion formed by bending the windward side end portion and the windward side end portion of the body portion in parallel with each other.

According to this structure, when the air flows from the inclined portion on the windward side to the body portion or from the body portion to the inclined portion on the downwind side, the flow of air is disturbed, thereby improving the heat exchange efficiency between the heat transfer pin and the air.

In the heat exchanger constructed as described above, when the heat transfer fins positioned at the upper and lower ends adjacent to each other are examined in detail, the air flows along the windward side inclined portion of the lower heat transfer fin, then flows along the windward side inclined portion of the upper heat transfer fin, The flow direction is changed by the body portion of the upper heat transfer fin.

As described above, since the inclined portion on the windward side and the inclined portion on the windward side are formed parallel to each other, before the air reaches the body portion, the windward side inclined portion on the lower- And flows in the same direction along the inclined portion, so that a temperature boundary layer is developed therebetween.

Therefore, even if the flow direction of the air in the body portion is changed, the already developed temperature boundary layer can not be effectively broken down and the heat exchange efficiency can not be greatly improved in practice.

SUMMARY OF THE INVENTION The present invention provides a heat exchanger for a refrigerator and a refrigerator having the heat exchanger.

As described above, the refrigerator heat exchanger according to the present invention and the refrigerator equipped with the heat exchanger include a plurality of heat transfer fins arranged in a continuous arrangement in a row and arranged in multiple stages from the windward side to the downwind side, The heat transfer fins are offset in either the column direction and the width direction when the heat transfer fins are seen as a plan view.

Further, the heat transfer fins disposed at the upper and lower ends adjacent to each other are offset by a first distance in the column direction, and offset by a second distance in the width direction.

The heat transfer fins positioned on the windward side are spaced apart from each other at a first fin pitch, and the heat transfer fins at a plurality of stages located on the downwind side are spaced apart from each other with a second fin pitch smaller than the first fin pitch.

The heat transfer fins disposed at upper and lower ends adjacent to each other among the heat transfer fins spaced apart at the second fin pitch are offset a predetermined distance in either the column direction or the width direction.

Also. The offset distance in the width direction is not more than 1/2 of the height of the heat transfer fin.

Also, the downstream end of the downstream end of the heat transfer fins is folded obliquely with respect to the air flow direction.

The heat transfer fins may include a body portion located on the windward side and a folded portion formed by folding from the windward side end portion of the body portion. The folded portion may be folded at an angle of not less than 5 degrees and not more than 20 degrees with respect to the body portion.

In the heat transfer fins disposed at the upper and lower ends adjacent to each other among the heat transfer fins arranged at the second fin pitch, the windward side end of the upper heat transfer fins and the lower end of the heat transfer fin at the lower end are vertically Direction.

In addition, the heat transfer fin includes a heat generating portion cut toward the heat transfer fin facing the heat transfer fin in the heat direction.

Further, the height from the proximal end to the distal end of the season portion is smaller than the fin pitch between the heat transfer fins which are continuously opposed to each other.

At least one of the upper end portion and the lower end portion of the season portion forms a concavo-convex shape.

The heat transfer tubes may further include a pair of heat transfer tubes penetrating the heat transfer fins, wherein a first center line in the width direction of the heat transfer fins and a second center line between the pair of heat transfer tubes are spaced apart from each other by a predetermined distance.

The heat transfer fins may include first heat transfer fins in which the first center line is located at one side in the width direction of the second center line and second heat transfer fins at which the first center line is located at the other side in the width direction of the second center line do.

The heat transfer fins disposed at the upper ends of the heat transfer fins disposed at the upper and lower ends of the heat transfer fins may be formed of any one of the first heat transfer fins and the second heat transfer fins, And the other of the first heat transfer fin and the second heat transfer fin.

The first centerline of the heat-transfer fins positioned at one of the upper and lower ends of the heat-transfer fins disposed at the upper and lower ends of the heat-transfer fins may coincide with the second centerline, The heat transfer fins positioned on the first heat transfer fin are formed of one of the first heat transfer fin and the second heat transfer fin.

The heat exchanger for a refrigerator and the refrigerator having the same according to the present invention configured as described above can further improve the heat exchange efficiency.

1 is a schematic view of a heat exchanger for a refrigerator according to a first embodiment of the present invention.
2 is a schematic view showing a part of a heat exchanger for a refrigerator according to a first embodiment of the present invention.
FIG. 3 is a view illustrating a fin pitch and a separation distance of heat transfer fins applied to a heat exchanger for a refrigerator according to the first embodiment of the present invention.
4 is experimental data showing the presence or absence of offset and the correlation of the bridge in the heat exchanger for a refrigerator according to the first embodiment of the present invention.
5 is experimental data showing a correlation between the distance and the bridge in the heat exchanger for a refrigerator according to the first embodiment of the present invention.
6 is a schematic view of a heat transfer fin applied to a heat exchanger for a refrigerator according to a first embodiment of the present invention.
7 is experimental data showing the correlation between the presence or absence of the surface finishing of the heat transfer fin and the bridge in the heat exchanger for a refrigerator according to the first embodiment of the present invention.
8 is a schematic view of a heat transfer fin according to a modification of the heat exchanger for a refrigerator according to the first embodiment of the present invention.
9 is a schematic view of a heat transfer fin according to another modification of the heat exchanger for a refrigerator according to the first embodiment of the present invention.
10 is a schematic view of a heat transfer fin applied to a heat exchanger for a refrigerator according to a second embodiment of the present invention.
11 is experimental data showing the effect of the heat transfer fin applied to the heat exchanger for a refrigerator according to the second embodiment of the present invention.
12 is a schematic view of a heat transfer fin according to a modification of the heat exchanger for a refrigerator according to the second embodiment of the present invention.
13 is a schematic view of a heat transfer fin applied to a heat exchanger for a refrigerator according to a third embodiment of the present invention.
14 is a schematic view of a folded portion of a heat transfer fin applied to a heat exchanger for a refrigerator according to a third embodiment of the present invention.
15A and 15B are schematic views of a heat transfer fin according to a modification of the heat exchanger for a refrigerator according to the third embodiment of the present invention.
16A and 16B are schematic views of a heat transfer fin according to another modification of the heat exchanger for a refrigerator according to the third embodiment of the present invention.
17 is a schematic view showing a part of a heat exchanger for a refrigerator according to a fourth embodiment of the present invention.
18 is a schematic view of a heat transfer fin applied to a heat exchanger for a refrigerator according to a fourth embodiment of the present invention.
19 is a schematic view of a heat transfer fin according to a modification of the heat exchanger for a refrigerator according to the fourth embodiment of the present invention.
20A and 20B are schematic views of a heat transfer fin according to another modification of the heat exchanger for a refrigerator according to the fourth embodiment of the present invention.
FIG. 21 is a schematic view of a heat transfer fin according to still another modification of the heat exchanger for a refrigerator according to the fourth embodiment of the present invention. FIG.

Hereinafter, various embodiments of the heat exchangers for a refrigerator according to the present invention will be described in detail with reference to the drawings.

- First Embodiment

The heat exchanger 100 according to the first embodiment of the present invention is used in a refrigerator including a storage room such as a refrigerator compartment or a freezer compartment and constitutes a refrigeration cycle together with a compressor and a condenser to be used as an evaporator for cooling air to be sent to the storage compartment do.

Hereinafter, the refrigerator heat exchanger 100 will be referred to as an evaporator 100 for convenience of explanation.

In an embodiment of the present invention, a fan for circulating air is disposed above the evaporator 100, the air in the storage room is delivered to the evaporator 100 through the fan, the air cooled by the evaporator 100 is returned to the storage room As shown in Fig. Here, the position of the fan can be changed according to the design.

1, the evaporator 100 includes a heat transfer pipe 10 and a fin & tube heat exchanger including a plurality of heat transfer fins 20 provided in the heat transfer pipe 10, .

The heat transfer pipe (10) is configured so that the refrigerant passes through the heat transfer pipe (10) and heat exchange is performed between the refrigerant and the air. In this embodiment, the heat transfer pipe (10) is formed by an S-shaped pipe formed by folding in an S shape. In this embodiment, since the air flows upward and passes through the evaporator 100, the lower side of the evaporator 100 is on the upstream side in the direction of air flow, and the upper side of the evaporator is on the downstream side in the air flow direction . The heat transfer pipe (10) extends in an S-shape from the downwind side to the downwind side and extends in an S-shape from the windward side to the downwind side so that the low-temperature refrigerant flows along the heat transfer pipe (10) , And then flows backward from the windward side to the downward windward in an S-shape.

The refrigerant heat-exchanged with the air is separated into refrigerant in a liquid state and refrigerant in a gaseous state by an accumulator (A) disposed between the evaporator (100) and the compressor, and the gaseous refrigerant is sucked into the compressor.

The heat transfer fins 20 are disposed in the heat transfer tubes 10 to increase the heat exchange area between the evaporator 100 and the air and are formed in a thin plate shape having thermal conductivity. Respectively.

Here, the plurality of heat transfer fins 20 are continuously arranged parallel to each other along a portion extending in a straight line in the heat transfer tube 10, and the heat transfer fins 20 thus arranged continuously are arranged on the windward side And is formed in multiple stages toward the downwind side.

More specifically, the plurality of heat transfer fins 20 are arranged such that the fin pitch on the windward side is narrower than that on the windward side. In the present embodiment, the heat transfer fins 20 of the windward side lower end region SL (9th to 12th stages in the present embodiment) are sandwiched by the first fin pitch PL and the upper end region SH Between the lower end zone SL on the windward side and the upper end zone SH on the windward side and the second fin pitch PH between the heat transfer fins 20 on the windward side in the present embodiment, The heat transfer fins 20 of the heat sink SM (5 to 8 in this embodiment) are spaced apart from each other by a third fin pitch PM.

The term pin pitch refers to the distance from one side of one heat transfer fin 20 to one side of the adjacent heat transfer fin 20.

More specifically, for example, the first fin pitch PL is 10 mm to 15 mm, the second fin pitch PH is 5 mm to 7.5 mm smaller than the first fin pitch PL, and the third fin pitch PM is And may be formed to be 7.5 mm to 10 mm, which is intermediate between the first fin pitch PL and the second fin pitch PH.

3, the evaporator 100 of the present embodiment includes a plurality of heat transfer fins 20 disposed at upper and lower ends adjacent to each other at a plurality of stages in which the heat transfer fins 20 are spaced apart from each other at a second fin pitch PH Are offset a predetermined distance in the column direction.

That is, when the heat transfer fins 20 of the upper region SH are viewed in the vertical direction, the heat transfer fins 20 adjacent to each other in the vertical direction are arranged so as not to overlap each other.

In this embodiment, the offset distance X is set to be half of the second fin pitch PH. That is, when the heat transfer fins 20 provided at any one end of the upper region SH are viewed in the vertical direction, the heat transfer fins 20 are disposed at the upper end thereof in the middle of the two heat transfer fins 20 adjacent to each other in the column direction . In other words, in the upper region SH, when the heat transfer fins 20 in the k-th stage are viewed in the vertical direction, the heat transfer fins 20 in the k-th stage are connected to two heat transfer fins 20 adjacent to each other in the k- (20).

The heat transfer fins 20 disposed in the lower end region SL are formed so as to prevent the heat transfer fins 20 adjacent in the up and down direction from being blocked by the frost, Direction.

In this embodiment, the heat transfer fins 20 disposed in the intermediate region SM are offset in the column direction as in the heat transfer fins 20 of the upper region SH described above. However, The heat transfer fins 20 may not be offset in the column direction, or the offset distance may be suitably changed differently from that shown in the present drawings.

FIG. 4 shows experimental data comparing the case of offsetting the heat transfer fins 20 disposed in the upper region SH and the case of not offsetting.

It can be confirmed that a bridge (hereinafter referred to as an inter-pin-to-pin bridge) that can occur between the heat transfer fins 20 adjacent to each other in the column direction is suppressed by offsetting the heat transfer fins 20 through the above- have. This is because the water droplets generated in the heat transfer fins 20 adjacent to each other in the column direction are dragged downward to the upper ends of the heat transfer fins 20 located at the lower end thereof by the surface tension.

As described above, by offsetting the heat transfer fins 20, bridges can be generated between the heat transfer fins 20 disposed at the upper and lower ends adjacent to each other (hereinafter, this is referred to as upper and lower pin-to-pin bridges).

5 shows the heat transfer fins 20 in which the heat transfer fins 20 are arranged at a plurality of stages at the second fin pitch PH, that is, the heat transfer fins 20 at the plural stages located in the upper region SH And experimental data showing the correlation between the upper and lower pin-to-pin bridges and the spacing distance Z along the vertical direction of the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other.

The distance Z is the distance from the lower end of one heat transfer fin 20 to the upper end of the heat transfer fin 20 located at the lower end thereof.

As can be seen from the above experimental data, when the spacing distance Z is less than 1 mm in a state where the heat transfer fins 20 are offset, the upper and lower pin-to-pin bridge can be suppressed. Of course, as shown in Fig. 5, it is possible to suppress the upper and lower pin-to-pin bridge when the separation distance Z is increased (for example, 3 mm or more). In this case, however, So that it is not preferable.

As is evident from the above experimental results, in the plurality of stages in which the heat transfer fins 20 are arranged at the second fin pitch PH, the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other, And the spacing distance Z is less than 1 mm, it is possible to simultaneously suppress the upper and lower pin-to-pin bridges and the parallel pin-to-pin bridges.

Next, each heat transfer fin 20 will be described.

Each heat transfer fin 20 includes a through hole 21 through which the heat transfer pipe 10 is inserted without flowing, as shown in FIG. 6. In this embodiment, each heat transfer fin 20 has a pair of through holes The heat transfer tubes 10 installed in the respective stages including the heat transfer tubes 21 are installed through the heat transfer fins 20.

In this embodiment, each heat transfer fin 20 is formed in a rectangular shape, but the shape of each heat transfer fin 20 can be variously changed, such as an ellipse or a square.

The heat transfer fins 20 disposed at the second fin pitch PH in the present embodiment, that is, the heat transfer fins 20 disposed in the upper region SH, And is subjected to surface treatment to draw water droplets adhered to the heat transfer fins 20 disposed at the top.

Although the above-described surface treatment is not essential for the heat transfer fins 20 disposed in the intermediate region SM and the lower end region SL, in this embodiment, the heat transfer fin 20 can be easily managed The above-described surface treatment is performed on all the heat transfer fins 20 disposed in the upper area SH, the intermediate area SM and the lower area SL.

More specifically, each of the heat transfer fins 20 is provided with at least a ridge portion 22 for drawing water droplets by surface tension, at least on the outer-side portion of each heat transfer fin 20. In this embodiment, as shown in Fig. 6, the above-mentioned roughness portions 22 are formed on the entire surface and back surface of the heat transfer fin 20. [

It is preferable that the roughening portion 22 is formed by a vertical line or the like parallel to the direction of gravity having a predetermined roughness or predetermined width through, for example, hair line processing. Examples of the specific surface treatment method include a method of rolling the front and back surfaces of the heat transfer fin 20, a method of line trimming, and a method of sandblasting.

FIG. 7 shows experimental data showing the relationship between the presence or absence of the roughness portion 22 and the bridge.

As a result of the above experiment, it can be confirmed that the upper and lower pin-to-pin bridges are suppressed by forming the roughness portion 22 on the heat transfer fin 20.

The evaporator 100 configured as described above has a structure in which the heat transfer fins 20 of the upper region SH are offset to half of the second fin pitch in the column direction while improving the heat exchange efficiency by reducing the fin pitch on the downward wind side At the same time, when the separation distance Z is less than 1 mm, both the upper and lower pin-to-pin bridge and the inter-pin-to-pin bridge can be suppressed.

Further, since the ribs 22 are formed on the front and back surfaces of the heat transfer fins 20, the upper and lower pin-to-pin bridges can be more reliably suppressed.

In addition, since the tubular portion 22 is formed on the entire surface of the heat transfer fin 20, when the tubular portion 22 is formed by rolling, as an example, the tubular portion 22 Is advantageous from the economical point of view.

However, the present invention is not limited to the above embodiments.

In the above embodiment, the heat transfer fins are arranged in four stages in the upper region, the lower region, and the middle region. However, the present invention is not limited thereto. The lower region may be arranged in one stage. It is also possible to arrange four or more heat transfer fins in each region.

Also, in the above embodiment, the offset distance is half the fin pitch of the upper region, but the offset distance can be appropriately changed.

In the above embodiments, the coarse portion is formed on the entire surface and the back surface of the heat transfer fin, but the coarse portion may be formed on only one of the surface and the back surface.

Also, as in the present embodiment, it is not necessary to form a coarse portion on the entire surface of the heat transfer fin, and it is preferable that a coarse portion is formed on at least the outer side of the heat transfer fin through a mask or the like.

More specifically, as in the embodiment shown in FIG. 8, the tubular portion 22 is formed on the other side from one end of the upper end and the lower end of the heat transfer fin 20, and may be formed a predetermined distance inward from the upper end and the lower end.

Further, in addition to the upper end and the lower end, it is also possible to form a ridge on the side end of the heat transfer fin, or to form a ridge only on the upper end of the heat transfer fin.

8, the tubular portion 22 is formed from one end to the other end at the upper end and the lower end of the heat transfer fin 20. However, the present invention is not limited thereto, and the coarse portion may be limited to only a part of the central portion of the upper and lower portions of the heat- As shown in Fig.

9, the heat transfer fin 20 may be formed by machining or the like so that the outer periphery of the heat transfer fin 20 may be formed by machining or the like, It is also possible to include a plurality of slits 23 formed in the portion.

Here, the slits 23 may be spaced at regular intervals or spaced at irregular intervals.

It is also possible to perform the surface treatment on the heat transfer fins as described above without offsetting the heat transfer fins disposed on the upper and lower ends in the upper and lower portions like the above embodiment in the column direction.

With this configuration, the effect is smaller than that of the above embodiment, but the installation work of each heat transfer fin can be simplified while suppressing the bridge.

In addition, it is not always necessary to subject the heat transfer fin to the surface treatment shown in the above-described embodiment. When the surface finishing is not performed, the bridge can be suppressed while preventing an increase in cost.

- Embodiment 2

Hereinafter, a second embodiment of a heat exchanger for a refrigerator according to the present invention will be described.

The refrigerator heat exchanger of the second embodiment differs from the first embodiment in the heat transfer fin.

Hereinafter, a detailed configuration of the heat transfer fin applied to the second embodiment of the heat exchanger for a refrigerator according to the present invention will be described.

As shown in FIG. 10, the heat transfer fin 20 of the present embodiment is formed in a flat plate shape, and the wind side end portion is not folded. The wind side end portion is inclinedly folded with respect to the air flowing direction, To allow air to flow toward one side of the heat exchange fins located at the top thereof.

More specifically, each heat transfer fin 20 has a body portion 24 located on the windward side and a folded portion 25 folded at a predetermined angle from the windward side end portion 241 of the body portion 24 .

The body portion 24 is formed in a flat plate shape. The body portions 24 of the heat transfer fins 20 adjacent to each other in the column direction are spaced apart from each other at a predetermined fin pitch P. The body portions 24 of the heat transfer fins 20 located at the upper and lower ends adjacent to each other 24 are vertically overlapped with each other. That is, the heat transfer fins 20 arranged in the column direction are equidistantly spaced at a predetermined fin pitch P, and the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other are not offset in the column direction.

The folded portion 25 is formed by folding from the windward side end portion 241 of the body portion 24 through the R bending process and the folded portion 25 is formed by the extending direction of the folded portion 25 and the extending direction of the body portion 24, (Hereinafter also referred to as a folding angle?) Is 5 degrees or more and 20 degrees or less.

Here, the folded portions 25 of the respective heat transfer fins 20 are all folded at the same folding angle &thetas; and the tips 251 of the folded portions 25, that is, the upper ends of the heat transfer fins 20 Are positioned approximately midway between the top and adjacent heat transfer fins 20. The distance Z between the tip end 251 of the folded portion 25 and the lower end of the heat transfer fin 20 located at the upper end of the folded portion 25 is set to be less than 1 mm as in the first embodiment.

11 shows experimental data showing the correlation between the folding angle? Of the folded portion 25 and the pressure loss? P and the correlation between the folding angle? Of the folded portion 25 and the total heat quantity Q. As shown in FIG.

As can be seen from the above experimental data, the pressure loss? P gradually increases as the folding angle? Of the folded portion 25 is increased from zero degrees. On the other hand, it is found that the total heat quantity Q increases up to 15 degrees as the folding angle? Increases from 0 degree, and the heat exchange efficiency improves by about 3.5%, but does not increase more than that.

Therefore, in the evaporator for a refrigerator in which the air velocity of the inflow air is relatively small, it is preferable to set the folding angle? To 5 degrees or more and 15 degrees or less in order to suppress the pressure loss? P as much as possible while increasing the heat quantity Q.

In the evaporator 100 constructed as above, the windward side end portion of the heat transfer fin 20 is not bent, and the windward side end portion is bent toward the heat transfer fin 20 located at the upper end of the heat transfer fin 20 have. Therefore, after the air flows along the folded portion 25 of the heat transfer fin 20 at a certain position, the air is supplied to the body portion 24 of the heat transfer fin 20 located at the upper side thereof, ) Changes the flow direction.

Accordingly, the temperature boundary layer can be effectively broken through the heat transfer fins 20 at the upper end, and the heat exchange efficiency can be improved as compared with the conventional one.

The air flowing along the folded portion 25 of the heat transfer fins 20 located at one of the ends is inclined with respect to the body portion 24 of the heat transfer fins 20 located at the upper end thereof, It is easy to reach the front edge of the heat transfer fin 20 of the heat transfer fin 20 and the heat exchange efficiency due to the leading edge effect can be improved.

That is, according to the above-described structure, both of the effects of improving the heat exchange efficiency by the turbulence and improving the heat exchange efficiency by the leading edge effect can be obtained.

Further, since only the downstream end portion of the heat transfer fin 20 is folded, the manufacturing process is simplified.

The tip end 251 of the folded portion 25 is positioned substantially in the middle of the heat transfer fins 20 adjacent to the upper end thereof and the tip 251 of the folded portion 25 and the heat transfer pin Since the distance Z between the lower ends of the upper and lower pins 20 is set to be less than 1 mm, both of the upper and lower pin-to-pin and the pin-to-pin inter-bridge can be suppressed as in the first embodiment.

The heat transfer fins 20 disposed at the upper and lower ends adjacent to each other in the above embodiment are not offset in the column direction in the above embodiment, but the heat transfer fins 20 are not limited thereto, and the heat transfer fins 20 may be offset in the column direction Do.

At this time, the offset distance X is set such that the folding angle 25 of the folded portion 25 is 5 degrees or more and 20 degrees or less, and the heat transfer fins 20 disposed at the upper and lower ends adjacent to each other are offset in the column direction, It is preferable that the tip 251 of the heat transfer member 25 is positioned approximately in the middle of the heat transfer fins 20 adjacent to the upper side thereof.

Also, in the above embodiment, the angle of each of the heat transfer fins is set to be the same, but it is also possible that the angle of deflection of some heat transfer fins is set to be different from that of the other heat transfer fins.

Further, the folded portion of the above embodiment is formed to be folded with respect to the body portion, but may be curved from the body portion.

- Third Embodiment

Next, a third embodiment of the heat exchanger for a refrigerator according to the present invention will be described.

The heat exchanger for a refrigerator according to the third embodiment of the present invention differs from the above embodiments in the construction of heat transfer fins. Hereinafter, a detailed configuration of the heat transfer fin applied to the heat exchanger according to the third embodiment of the present invention will be described.

The heat transfer fin 20 of this embodiment is formed in a flat plate shape as shown in FIG. 13 and includes a cut-out portion 26 (cut-out portion) formed by being cut toward the heat transfer fin 20 facing in the column direction. Wherein each heat transfer fin 20 includes a pair of cutouts 26 on either side of its left and right sides and each cutout 26 is cut away from each heat transfer fin 20 in the same direction.

The cutout portions 26 are formed by forming grooves on the right and left sides of the heat transfer fin 20 and then forming the cutouts 26. The height L of the cutout portion 26, that is, the length from the proximal end portion to the distal end portion of the cutout portion 26 (L) is formed to be smaller than the fin pitch between the heat transfer fins (20) so that the cutout portion (26) does not interfere with the adjacent heat transfer fins (20) in the heat direction.

Each cutout portion 26 includes a face plate portion 261 formed parallel to the direction of air flow, that is, parallel to the up and down direction as shown in FIG. 14, and the cutout portion 26 And stands upright with respect to the face plate portion 201. The face plate portion 261 of the cutout portion 26 is not necessarily perpendicular to the face plate portion 201 of the heat transfer fin 20 and may be formed to be inclined with respect to the face plate portion 201 of the heat transfer fin 20 Do.

Each of the cut portions 26 of the present embodiment has a plurality of concavities and convexities at the upper end portion (the windward side end portion) and the lower end portion (the windward side end portion). More specifically, the upper end portion and the lower end portion of the cut-out portion 26 form a saw-tooth shape in which a plurality of triangular irregularities are formed. It is also possible to form a plurality of concavities and convexities only on the lower end portion of the cutout portion 26 without forming concave and convex portions on the upper end portion thereof.

In the evaporator 100 configured as described above, since the heat transfer fin 20 includes the cut-out portion 26, it is possible to increase the effect of the leading edge, thereby improving the heat exchange performance.

Further, since the lower end of the cutout portion 26 has a sawtooth shape, the leading edge effect can be further increased.

Further, since the upper end portion of the cut-out portion 26 is formed like a saw tooth in the same manner as the lower end portion, the work can be performed without worrying about the vertical direction when the heat transfer fin 20 is installed.

However, the present invention is not limited to the above embodiments.

It is also possible to form a shape in which a plurality of rectangular concavities and convexities such as a trapezoidal shape are formed at the upper and lower ends of the cutout portion 26 as shown in FIG. 15A.

In addition, the number of the cut-out portions 26 is not limited to the above embodiment, and it is also possible to appropriately change the number of the cut-out portions 26 by providing four cut-out portions 26 as shown in FIG. 15B.

In order to increase the leading edge effect, it is also possible to fold the cut-out portion 26 a plurality of times from the proximal end toward the distal end as shown in Fig. 16A.

16B, it is also possible to form the cut-out portion 26 by forming a groove on the upper end (windward side end) or the lower end (windward side end) of the heat transfer fin 20 and then raising it.

- Fourth Embodiment

Hereinafter, a heat exchanger for a refrigerator (hereinafter referred to as an evaporator) according to a fourth embodiment of the present invention will be described.

The evaporator 100 according to the fourth embodiment differs from the first embodiment in the direction of offsetting the heat transfer fins 20. 17, in the fourth embodiment, the heat transfer fins 20 have a width (width) when viewed from the plane of the heat transfer fins 20. In other words, in the first embodiment, the heat transfer fins 20 are offset in the column direction, Direction.

The width direction is perpendicular to the column direction and orthogonal to the up-down direction (air flow direction).

Hereinafter, a detailed configuration of the heat transfer fin 20 applied to the evaporator 100 according to the fourth embodiment of the present invention will be described.

The heat transfer fin 20 is for increasing the heat exchange area between the evaporator 100 and the air as in the first embodiment described above. As shown in FIG. 17, the heat transfer fin 20 has a thermally conductive . Further, the pair of heat transfer tubes 10 are spaced apart from each other in the width direction of the heat transfer fins 20 when the heat transfer fins 20 are viewed from a plan view.

The heat transfer fins 20 are continuously arranged in a state in which they are substantially parallel to each other in the axial direction of the heat transfer pipe 10. The heat transfer fins 20 thus arranged continuously are formed in multiple stages from the windward side to the windward side. In addition, as in the first embodiment, the heat transfer fins 20 are arranged such that the fin pitch on the downwind side is narrower than the windward side, that is, the heat transfer fins 20 located on the windward side are arranged at a predetermined first fin pitch, Are arranged at a predetermined fin pitch smaller than the first fin pitch.

18, the evaporator 100 of the present embodiment has a center line L1 (hereinafter, referred to as a first center line L1) of the heat transfer fins 20 when the heat transfer fin 20 is viewed from a plan view And a plurality of heat transfer pins (not shown) configured such that a center line L2 (hereinafter referred to as a second center line L2) of a pair of heat transfer tubes 10 passing through the heat transfer fins 20 is spaced by a predetermined distance? (20).

18, the first center line L1 is connected to the heat transfer fin 20 (hereinafter referred to as the first heat transfer fin 20) located on one side (right side) of the second center line L2 in the width direction, And a heat transfer fin 20 (hereinafter referred to as a second heat transfer fin 20B) located on the other side (left side) of the first center line L1 in the width direction of the second center line L2 Is installed. The distance L between the first center line L1 and the second center line L2 is equal to each other in the heat transfer fins 20 but is not limited thereto. It is also possible to appropriately change the separation distance DELTA L between the heat transfer fins 20 such that the two heat transfer fins 20B are spaced apart from each other by a different distance L from the center line L2 of the heat transfer tubes 10 .

In this embodiment, as shown in Figs. 17 and 18, the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other are offset by a predetermined distance Y in the width direction.

Here, the heat transfer fins 20 disposed at the upper and lower ends of the downstream side heat transfer fins 20 arranged at the second fin pitch are offset a predetermined distance Y in the width direction.

17, among the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other in the downward-direction heat transfer fin 20, for example, the heat transfer fins 20 Are formed as the first heat transfer fin 20A and the heat transfer fins 20 located at the lower end are both formed as the second heat transfer fin 20B.

The offset distance Y of the heat transfer fins 20 disposed at the upper and lower ends is twice the separation distance? L between the first center line L1 and the second center line L2.

In the first heat transfer fin 20A, the distance from the heat transfer pipe 10 on the right side to the right side end of the first heat transfer fin 20A becomes longer and the heat exchange on the right end becomes longer The heat exchange efficiency of the first heat transfer fin 20A is reduced. This is the same for the second heat transfer fin 20B.

Therefore, the separation distance? L is set to a predetermined value or less, and as an example, the separation distance? L is set so that the offset distance Y is 1/2 or less of the height in the vertical direction of the heat transfer fin 20 .

Since the heat transfer fins 20 disposed at the upper and lower ends adjacent to each other are offset a predetermined distance Y along the width direction of the evaporator 100 constructed as described above, The flow thereof is disturbed when it flows into the space between the heat transfer fins 20. Therefore, the temperature boundary layers developed when the air flows along the heat transfer fins 20 on the windward side can be collapsed before they are introduced into the heat transfer fins 20 on the downwind side, and the heat exchange efficiency can be improved.

Since the offset distance Y is set to be equal to or less than 1/2 of the vertical height of the heat transfer fin 20 so that the heat transfer fins 20 are offset in the width direction, The heat exchange efficiency can be ensured over a certain level.

However, the present invention is not limited to the above embodiments.

For example, in the above embodiment, the heat transfer fins 20 located at the upper end among the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other are all used as the first heat transfer fin 20A, All of the fins 20 are made of the second heat transfer fin 20B. However, it is not necessary to form all the heat transfer fins 20A and 20B as the first heat transfer fin 20A and the second heat transfer fin 20B. For example, A part of the fin 20 may be formed of the first heat transfer fin 20A and a part of the heat transfer fin 20 located at the lower end may be formed of the second heat transfer fin 20B.

More specifically, as shown in the example of FIG. 19, the heat transfer fins 20 located at the upper end are formed by the first heat transfer fins 20A one by one in the column direction, and the heat transfer fins 20 Are formed as second heat transfer fins 20B one by one in the column direction.

In the above embodiment, the heat transfer fins 20 located at the upper end among the heat transfer fins 20 disposed at the upper and lower ends adjacent to each other are formed as the first heat transfer fin 20A, and the heat transfer fins 20A and 20B, the heat transfer fin 20 located at the lower end of the heat transfer fin 20 has a first center line L1 and a second center line L2 ) Can be matched. In this case, the heat transfer fins 20 positioned at the upper end may be formed as the first heat transfer fin 20A, or may be formed as the second heat transfer fin 20B.

In the above embodiment, the heat transfer fins 20 disposed at the upper and lower ends adjacent to each other are offset only in the width direction. However, the heat transfer fins 20 can be offset in both the column direction and the width direction.

More specifically, as shown in Fig. 21, the heat transfer fins 20 arranged at the upper and lower ends adjacent to each other are offset by a predetermined first distance X in the column direction and at the same time, a predetermined second distance Y ) ≪ / RTI > In this case, the predetermined first distance X and the predetermined second distance Y may be equal to or different from each other.

In addition, the present invention is not limited to the first embodiment, the second embodiment, the third embodiment, and the fourth embodiment, and various modifications are possible without departing from the spirit of the present invention.

Claims (16)

And a plurality of heat transfer fins which are arranged in a continuous arrangement and arranged in multiple stages from the windward side to the downwind side,
Wherein the heat transfer fins disposed at the upper and lower ends adjacent to each other are offset in a row direction and a width direction when the heat transfer fins are seen as a plan view. The method according to claim 1,
Wherein the heat transfer fins disposed at the upper and lower ends adjacent to each other are offset by a first distance in the column direction and offset by a second distance in the width direction. The method according to claim 1,
The heat transfer fins positioned on the windward side are spaced apart from each other at a first fin pitch,
Wherein the plurality of heat transfer fins at the downstream side are spaced apart from each other at a second fin pitch smaller than the first fin pitch. The method of claim 3,
Wherein the heat transfer fins disposed at upper and lower ends adjacent to each other of the heat transfer fins spaced apart at the second fin pitch are offset a predetermined distance in either the column direction or the width direction. 5. The method of claim 4,
Wherein the offset distance in the width direction is equal to or less than half the height of the heat transfer fin. The method according to claim 1,
Wherein the downstream end of the heat transfer fins is folded obliquely with respect to the direction of air flow. The method according to claim 6,
Wherein the heat transfer fins include a body portion located on the windward side and a folded portion formed by being folded from the windward side end portion of the body portion,
Wherein the folded portion is folded at an angle of not less than 5 degrees and not more than 20 degrees with respect to the body portion. The method of claim 3,
The heat transfer fins disposed at the upper and lower ends of the heat transfer fins disposed at the second fin pitch are arranged such that the windward side end portions of the upper heat transfer fins and the lower end portions of the heat transfer fins at the lower end A heat exchanger for a refrigerator of less than 1 mm. The method according to claim 1,
Wherein the heat transfer fin includes a heat exchanger fin and a heat exchanger fin. 10. The method of claim 9,
Wherein the height from the proximal end to the distal end of the season portion is smaller than the fin pitch between the heat transfer fins successively disposed opposite to each other. 11. The method of claim 10,
Wherein at least one of an upper end portion and a lower end portion of the season portion forms a concavo-convex shape. The method according to claim 1,
Further comprising a pair of heat transfer tubes passing through the heat transfer fins,
Wherein a first center line in the width direction of the heat transfer fins and a second center line between the pair of heat transfer tubes are spaced apart from each other by a predetermined distance. 13. The method of claim 12,
Wherein the heat transfer fins include a first heat transfer fin in which the first center line is located on one side in the width direction of the second center line and a second heat transfer fin in which the first center line is located on the other side in the width direction of the second center line, Heat exchanger. 14. The method of claim 13,
The heat transfer fins positioned at the upper ends of the heat transfer fins disposed at the upper and lower ends adjacent to each other of the heat transfer fins are formed of any one of the first heat transfer fins and the second heat transfer fins, Wherein the heat transfer fin is formed of one of the heat transfer fin and the second heat transfer fin. 14. The method of claim 13,
The first centerline of the heat transfer fins positioned at one of the upper and lower ends of the heat transfer fins disposed at the upper and lower ends adjacent to each other of the heat transfer fins is aligned with the second centerline,
Wherein the heat transfer fins located at the other of the upper and lower ends are formed of one of the first heat transfer fin and the second heat transfer fin. 16. A refrigerator having a refrigerator heat exchanger according to any one of claims 1 to 15.

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