WO2012056790A1

WO2012056790A1 - Heat exchanger and air conditioner having same installed therein

Info

Publication number: WO2012056790A1
Application number: PCT/JP2011/068354
Authority: WO
Inventors: 良信山崎
Original assignee: シャープ株式会社
Priority date: 2010-10-25
Filing date: 2011-08-11
Publication date: 2012-05-03
Also published as: CN103180684A; CN103180684B

Abstract

A heat exchanger (1) is provided with: two header pipes (2, 3) disposed parallel to each other with a spacing therebetween; flat tubes (4) disposed between the header pipes and having therein refrigerant paths (5) connected to the insides of the header pipes; and fins (6) disposed between the flat tubes. Dam walls (12) for covering the lower ends of the fins from the outside are formed at ends of surfaces of the flat tubes, the surfaces being located on the side on which condensed water of the heat exchanger collects.

Description

Heat exchanger and air conditioner equipped with the same

The present invention relates to a side flow type parallel flow heat exchanger and an air conditioner equipped with the same.

A parallel flow type heat in which a plurality of flat tubes are arranged between a plurality of header pipes so that a plurality of refrigerant passages in the flat tubes communicate with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes. Exchangers are widely used in outdoor units of car air conditioners and building air conditioners.

An example of a conventional side flow type parallel flow type heat exchanger is shown in FIG. The heat exchanger 1 includes two

header pipes

2 and 3 and a plurality of flat tubes 4 arranged therebetween. In FIG. 11, the

header pipes

2 and 3 extend in the vertical direction and are arranged in parallel in the horizontal direction at intervals, and the flat tubes 4 extend in the horizontal direction and are arranged at a predetermined pitch in the vertical direction. Needless to say, the parallel flow type heat exchanger 1 is installed at various angles in accordance with design requirements at the stage of actually mounting on equipment, and there are many cases where exact “vertical” and “horizontal” do not apply.

The flat tube 4 is an elongated molded product obtained by extruding a metal, and a refrigerant passage 5 through which a refrigerant flows is formed. Since the flat tube 4 is disposed so that the extrusion direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 5 is also horizontal. A plurality of refrigerant passages 5 having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 11, and therefore, the vertical cross section of the flat tube 4 has a harmonica shape. Each refrigerant passage 5 communicates with the inside of the

header pipes

2 and 3. Fins 6 are arranged between adjacent flat tubes 4. Here, corrugated fins are used as the fins 6, but plate fins may be used.

The

header pipes

2 and 3, the flat tubes 4, and the fins 6 are all made of a metal having good heat conductivity such as aluminum, the flat tubes 4 are brazed to the

header pipes

2 and 3, and the fins 6 are brazed to the flat tubes 4. Or it is fixed by welding.

In the heat exchanger 1 of FIG. 11, the refrigerant inlets and outlets 7 and 8 are provided only on the header pipe 3 side. Two partition plates 9a and 9c are provided in the header pipe 3 at intervals in the vertical direction. Inside the header pipe 2, the partition plates are located at a height intermediate between the partition plates 9a and 9c. 9b is provided.

When the heat exchanger 1 is used as an evaporator, the refrigerant flows from the lower refrigerant inlet / outlet 7 as shown by the solid line arrows in FIG. The refrigerant entering from the refrigerant inlet / outlet 7 is blocked by the partition plate 9 a and travels toward the header pipe 2 via the flat tube 4. This refrigerant flow is represented by a left-pointing block arrow. The refrigerant that has entered the header pipe 2 is blocked by the partition plate 9 b and travels to the header pipe 3 via another flat tube 4. This refrigerant flow is represented by a right-pointing block arrow. The refrigerant that has entered the header pipe 3 is blocked by the partition plate 9c, and further travels toward the header pipe 2 via another flat tube 4. This refrigerant flow is represented by a left-pointing block arrow. The refrigerant that has entered the header pipe 2 is folded back and travels again to the header pipe 3 via another flat tube 4. This refrigerant flow is represented by a right-pointing block arrow. The refrigerant that has entered the header pipe 3 flows out from the refrigerant inlet / outlet 8. In this way, the refrigerant follows the zigzag path and flows from the bottom to the top. Although the case where the number of partition plates is 3 is shown here, this is only an example, and the number of partition plates and the number of times the resulting refrigerant flow may be folded may be set as desired. it can.

When the heat exchanger 1 is used as a condenser, the refrigerant flow is reversed. That is, the refrigerant enters the header pipe 3 from the refrigerant inlet / outlet 8 as shown by the dotted arrow in FIG. 11, is dammed by the partition plate 9c and goes to the header pipe 2 via the flat tube 4, and is dammed by the partition plate 9b in the header pipe 2. It heads to the header pipe 3 via another flat tube 4, and the header pipe 3 is dammed by a partition plate 9 a, then goes to the header pipe 2 again via another flat tube 4, and is folded back by the header pipe 2 to make another flat It flows from the top to the bottom following the zigzag path in which it goes to the header pipe 3 again via the tube 4 and flows out from the refrigerant inlet / outlet 7 as indicated by the dotted line arrow.

When a heat exchanger is used as an evaporator, moisture in the atmosphere condenses on the heat exchanger surface that has become low temperature, and condensed water is generated. In the parallel flow type heat exchanger, when the condensed water stays on the surface of the flat tube or the fin, the cross-sectional area of the air flow passage is narrowed by the water, and the heat exchange performance is deteriorated.

Condensate turns into frost on the surface of the heat exchanger when the temperature is low. Frost can travel to ice. In the present specification, the term “condensed water” is used to include water in which such frost and ice are melted, so-called defrosted water.

When the condensate is generated and stays in the side flow type parallel flow heat exchanger, the following problems occur. When the side flow type parallel flow heat exchanger 1 is tilted so that the surface on which condensed water is concentrated faces downward as shown in FIG. 12, the condensed water accumulated at the end of the fin 6 It drops from the corner of the fin 6 before it changes over to the fin 6 of the step. When the heat exchanger 1 is installed in an indoor unit of an air conditioner and a cross flow fan is installed under the heat exchanger 1, a water jump occurs in which water droplets are scattered by the air flow blown out by the cross flow fan. , Discomfort to the user.

Therefore, various measures for draining condensed water before water jumps have been proposed. Examples thereof can be seen in

Patent Documents

1 and 2.

In the heat exchanger described in Patent Document 1, a drainage guide that comes into contact with the fins is disposed on the condensate condensing side. The drainage guide is made of a linear member, is inclined with respect to the flat tube, and at least one of both ends is led to the lower end side or the side end side of the heat exchanger.

In the heat exchanger described in Patent Document 2, the guide plate is disposed in contact with the fins on the downstream side of the air blowing. The dew adhering to the surface of the heat exchanger moves downstream by blowing and adheres to the guide plate, and falls freely by its weight.

JP 2007-285673 A Japanese Patent Laid-Open No. 2001-263861

In the heat exchanger described in Patent Document 1, water is guided by bringing a drainage guide made of a linear member into contact with the heat exchanger. However, when the heat exchanger is installed in a tilted state or when dirt is attached to the drainage guide, a phenomenon such as water jumping may occur without water passing through the drainage guide. Even in the heat exchanger described in Patent Document 2, when installed in an inclined state, water jumps due to water bridged between the fins.

The present invention has been made in view of the above points, and prevents the occurrence of water jumping even when the heat exchanger is placed in an inclined state so that the surface on which condensed water is collected faces downward. With the goal.

According to the present invention, a plurality of header pipes arranged in parallel at intervals, and a plurality of flat pipes arranged between the plurality of header pipes and having a refrigerant passage provided therein communicated with the inside of the header pipe. In a side flow type parallel flow heat exchanger having a tube and a fin disposed between the flat tubes, a lower end of the fin is disposed at an end of the flat tube on a surface where condensed water is concentrated. A blocking wall is formed to cover the outside from the outside.

In the heat exchanger configured as described above, it is preferable that the blocking wall is formed integrally with the flat tube, and the refrigerant passage is provided only in the flat tube portion and not provided in the blocking wall. .

In the heat exchanger configured as described above, it is preferable that the flat tube has a higher middle portion in the length direction than both ends.

In the heat exchanger configured as described above, it is preferable that the flat tube has a curved shape that is convex upward.

In the heat exchanger configured as described above, it is preferable that the flat tube is highest at the central portion in the length direction.

In the heat exchanger configured as described above, the flat tube is preferably narrower than the fin in the direction in which air passes through the heat exchanger.

According to a preferred embodiment of the present invention, the heat exchanger configured as described above is mounted on an indoor unit of an air conditioner.

According to a preferred embodiment of the present invention, the heat exchanger configured as described above is mounted on an outdoor unit of an air conditioner.

According to the present invention, in the parallel flow type heat exchanger of the side flow type, a blocking wall that covers the lower end of the fin from the outside is formed at the end of the flat tube on the surface on the side where the condensed water is concentrated. The condensed water gathered is guided to the inside of the fin by the blocking wall and does not drip. As a result, it is possible to avoid a situation in which condensed water falls on the fan and a water jump occurs.

It is a schematic sectional drawing of the heat exchanger which concerns on 1st Embodiment of this invention. It is a partial expanded sectional view of the heat exchanger which concerns on 1st Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger which concerns on 2nd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 3rd Embodiment of this invention. It is a top view of the heat exchanger which concerns on 3rd Embodiment of this invention. It is a partial expanded sectional view of the heat exchanger which concerns on 3rd Embodiment of this invention. It is a partial expanded sectional view which shows the reference structure of a heat exchanger. It is a schematic block diagram of the air conditioner carrying the heat exchanger which concerns on this invention, and shows the state at the time of heating operation. It is a schematic block diagram of the air conditioner carrying the heat exchanger which concerns on this invention, and shows the state at the time of air_conditionaing | cooling operation. It is a schematic sectional drawing of the outdoor unit of the air conditioner carrying the heat exchanger which concerns on this invention. It is a vertical sectional view showing a schematic structure of a conventional side flow type parallel flow type heat exchanger. It is a schematic sectional drawing which shows the state which inclined and placed the conventional side flow type parallel flow type heat exchanger so that the surface on the side where condensed water collects may face down.

Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 and 2. Constituent elements that are functionally common to the conventional structure of FIG. 11 are denoted by the same reference numerals as those used in FIG.

The following structural changes are made to the side flow parallel flow heat exchanger 1. That is, the blocking portion 10 is formed at the end of the flat tube 4 on the surface on the side where condensed water is collected. The blocking portion 10 includes a base portion 11 that is an extension of the flat tube 4 and a blocking wall 12 that rises from the end of the base portion 11 and has an L-shaped cross section as a whole. The blocking wall 12 covers the lower end of the fin 6 from the outside. The blocking portion 10 may be molded separately from the flat tube 4 and may be joined to the flat tube 4 by brazing or welding, or may be integrally formed with the flat tube 4. In the case of molding separately from the flat tube 4, the material of the blocking portion 10 may be the same as that of the flat tube 4, but in that case, the blocking portion 10 itself is cooled and condensed, and the corner of the blocking portion 10 is formed. There is a possibility that condensed water will drip from the water. In order to prevent this, the blocking portion 10 may be molded from a material that is difficult to cool, such as a synthetic resin.

The blocking part 10 is provided with a drain hole (not shown) for promoting drainage. The drainage hole is provided at a position where the drainage hole is transferred to the lower fin 6. When the blocking portion 10 is integrally formed with the flat tube 4, the blocking passage 10 is not provided with the refrigerant passage 5. By doing in this way, it is possible to avoid a situation in which condensation occurs on the blocking portion 10 itself and condensed water drops from the corner.

Thus, since the blocking wall 12 which covers the lower end of the fin 6 from the outside is formed at the end of the flat tube 4 on the surface where condensed water is collected, the condensed water collected is blocked. Is guided into the inside of the fin 6 and does not drip. As a result, it is possible to avoid a situation in which condensed water falls on the fan and a water jump occurs.

FIG. 3 shows a second embodiment of the present invention. The heat exchanger 1 of the second embodiment is obtained by adding the following modifications to the heat exchanger 1 of the first embodiment. That is, in the heat exchanger 1 of the second embodiment, the

header pipes

2 and 3 are not the same height, and the header pipe 2 is lower than the header pipe 3. The flat tube 4 and the fin 6 and the blocking portion 10 (not shown in FIG. 3) are also inclined so that the header pipe 2 side is lowered.

In the heat exchanger 1 of the second embodiment, since the flat tube 4 and the blocking portion 10 are inclined so that the header pipe 2 side is lowered, the condensed water causes the flat tube 4 and the blocking portion 10 to be lowered. Since it flows along the header pipe 2 and then flows down along the header pipe 2, an even better drainage effect can be obtained. For this reason, it is difficult for water jumps to occur.

4 to 6 show a third embodiment of the present invention. In the heat exchanger 1 of the third embodiment, four refrigerant inlets / outlets 7 are provided in the header pipe 2, and four refrigerant inlets / outlets 8 are provided in the header pipe 3. The four refrigerant inlets / outlets 7 are combined into one by a flow divider (not shown), and the four refrigerant outlets / outlets 8 are also combined into one by a flow divider (not shown).

The characteristic feature of the heat exchanger 1 of the third embodiment is the shape of the flat tube 4. That is, when the heat exchanger 1 is arranged in such a manner that the

header pipes

2 and 3 are vertical and the flat tube 4 is horizontal, the flat tube 4 is higher in the middle in the length direction than both ends. In 3rd Embodiment, the intermediate part of the length direction is made high by making the flat tube 4 into the curved shape which protruded upwards. In addition, the height of the flat tube 4 is highest at the central portion in the length direction. The flat shape of the flat tube 4 is linear as shown in FIG.

As shown in FIG. 6, the heat exchanger 1 of the third embodiment also has a blocking portion 10 formed at the end of the flat tube 4 on the surface on the side where condensed water collects. The stop wall 12 is not in close contact with the lower end of the fin 6, and a gap 13 is provided between the stop wall 12 and the fin 6.

In the heat exchanger 1 of the third embodiment, since the intermediate portion in the length direction of the flat tube 4 is made higher than both ends, the condensed water generated on the surface of the flat tube 4 or the fin 6 is directed toward the both ends of the flat tube 4. Flowing into. Therefore, even if a fan is placed under the heat exchanger 1, the condensed water can be guided and drained to both ends of the flat tube 4 where the vertical position does not overlap with the fan. It is possible to avoid a situation in which condensed water drops from an intermediate portion in the length direction and water jumps.

In the direction in which air passes through the heat exchanger 1, in other words, in the direction perpendicular to the length direction and in the horizontal direction, the flat tubes 4 are narrower than the fins disposed between them. Thereby, condensed water will flow along the edge of a flat tube, and drainage efficiency will improve.

The shape of the flat tube 4 is not limited to the curved shape convex upward. It may be a “he” -shaped bent shape. Moreover, the structure where the height of the flat tube 4 is the highest in the center part of a length direction is not essential. You may comprise so that the highest point may come to the place which is biased to the left or right instead of the center.

It is not necessary for all the flat tubes 4 to have the same shape. The shape may be varied depending on the flat tube 4. For example, a configuration in which bending (bending) becomes deeper as the flat tube 4 positioned at the upper level, a configuration in which a bending tube and a bending tube are combined, and the like are possible.

In the heat exchanger 1 of the third embodiment, a groove 14 extending in the length direction is formed on the upper surface of the flat tube 4. The groove 14 is positioned substantially at the center of the flat tube 4 in a direction perpendicular to the length direction. The depth of the groove 14 may be 10% or less of the entire thickness of the flat tube 4. Since the condensed water is guided to the both ends of the flat tube 4 through the groove 14, the drainage efficiency is improved.

A reference structure of the heat exchanger 1 is shown in FIG. In the heat exchanger 1 of FIG. 7, the end of the fin 6 on the surface on the side where condensed water collects protrudes from the end of the flat tube 4, and the gap formed by the protruding portions of the fin 6 is at the end of the flat tube 4. A flange 15 is formed to protrude from the bottom. The flange 15 extends in the length direction of the flat tube 4 and is located at the center of the gap in the vertical direction.

When the flange 15 is present, it is the same as a gap between the flat tube 4 and the fin 6, and the condensed water easily flows along the flat tube 4. Thereby, drainage efficiency improves. The lowering of the hydrophilicity of the fin 6 due to the adhesion of oil does not have to be taken care of much.

8 and 9 show an example in which the heat exchanger 1 is mounted on an indoor unit of a separate type air conditioner. The outdoor unit of the separate type air conditioner shown in FIGS. 8 and 9 includes a compressor, a four-way valve, an expansion valve, an outdoor heat exchanger, an outdoor fan, etc., and the indoor unit is an indoor heat exchanger, an indoor side Includes a blower. The outdoor heat exchanger functions as an evaporator during heating operation and functions as a condenser during cooling operation. The indoor heat exchanger functions as a condenser during heating operation and functions as an evaporator during cooling operation.

FIG. 8 shows a basic configuration of a separate type air conditioner using a heat pump cycle as a refrigeration cycle. The heat pump cycle 101 includes a compressor 102, a four-way valve 103, an outdoor heat exchanger 104, a decompression / expansion device 105, and an indoor heat exchanger 106 connected in a loop. The compressor 102, the four-way valve 103, the heat exchanger 104, and the decompression / expansion device 105 are accommodated in the casing of the outdoor unit 110, and the heat exchanger 106 is accommodated in the casing of the indoor unit 120. An outdoor fan 107 is combined with the heat exchanger 104, and an indoor fan 108 is combined with the heat exchanger 106. The blower 107 includes a propeller fan 107a for forming a blown airflow, and the blower 108 includes a cross flow fan 108a for forming a blown airflow. The cross flow fan 108a is disposed below the heat exchanger 106 with its axis line horizontal.

The heat exchanger 1 according to the present invention can be used as a component of the heat exchanger 106 of the indoor unit. The heat exchanger 106 is a combination of three

heat exchangers

106A, 106B, and 106C like a roof that covers the blower 108, and any or all of the

heat exchangers

106A, 106B, and 106C are combined with the heat exchanger 1. It can be.

Fig. 8 shows the state during heating operation. At this time, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the indoor heat exchanger 106 where it dissipates heat and condenses. The refrigerant exiting the heat exchanger 106 enters the outdoor heat exchanger 104 from the decompression / expansion device 105 and expands there, takes heat from the outdoor air, and returns to the compressor 102. The airflow generated by the indoor fan 108 promotes heat dissipation from the heat exchanger 106, and the airflow generated by the outdoor fan 107 accelerates heat absorption of the heat exchanger 104.

FIG. 9 shows a state during cooling operation or defrosting operation. At this time, the four-way valve 103 is switched so that the refrigerant flow is reversed from that during the heating operation. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the outdoor heat exchanger 104, where it dissipates heat and condenses. The refrigerant exiting the heat exchanger 104 enters the heat exchanger 106 on the indoor side from the decompression / expansion device 105 and expands there, takes heat from the indoor air, and returns to the compressor 102. The airflow generated by the outdoor fan 107 promotes heat dissipation from the heat exchanger 104, and the airflow generated by the indoor fan 108 promotes heat absorption of the heat exchanger 106.

When the heat exchanger 1 according to the present invention is used as a constituent element of the heat exchanger 106 of the indoor unit, the surface that is the leeward side of the heat exchanger 1 and also the lower surface side depending on the posture of the heat exchanger 1 is condensed water. The rally side. When the heat exchanger 1 according to the present invention is used, even if condensed water collects on the surface on the leeward side, it does not drop on the cross flow fan 108a, and water splash does not occur. Moreover, in the heat exchanger 1, a bridge phenomenon can be suppressed and an increase in ventilation resistance can be suppressed.

The heat exchanger 1 according to the present invention can be mounted not only on an indoor unit of a separate air conditioner but also on an outdoor unit. FIG. 10 shows an example of mounting on an outdoor unit.

10 includes a sheet metal casing 20a having a substantially rectangular planar shape, and the long side of the casing 20a is a front face 20F and a back face 20B, and the short side is a left side face 20L and a right side face 20R. An exhaust port 21 is formed on the front surface 20F, a rear intake port 22 is formed on the rear surface 20B, and a side intake port 23 is formed on the left side surface 20L. The exhaust port 21 is made up of a set of a plurality of horizontal slit-like openings, and the rear intake port 22 and the side intake ports 23 are made up of lattice-like openings. A top plate and a bottom plate (not shown) are added to the four sheet metal members of the front surface 20F, the back surface 20B, the left side surface 20L, and the right side surface 20R to form a hexahedral-shaped housing 20a.

Inside the housing 20a, there is a heat exchanger 1 (any one of the first to third embodiments) having an L-shape in a planar shape just inside the rear intake port 22 and the side intake port 23. Be placed. The heat exchanger 1 is arranged so that the surface on the right side in FIG. 1, that is, the surface where the upper flat tube 4 is overhanging the lower flat tube 4 is on the leeward side.

In order to forcibly perform heat exchange between the heat exchanger 1 and the outdoor air, a blower 24 is disposed between the heat exchanger 1 and the exhaust port 21. The blower 24 is a combination of an electric motor 24a and a propeller fan 24b. In order to improve the blowing efficiency, a bell mouth 25 surrounding the propeller fan 24b is attached to the inner surface of the front surface 20F of the housing 20a. A space inside the right side surface 20R of the housing 20a is isolated by a partition wall 26 from an air flow flowing from the rear intake port 22 to the exhaust port 21, and a compressor 27 is accommodated therein.

The heat exchanger 1 according to the first embodiment mounted on the outdoor unit 20 prevents water jumping due to the presence of the blocking wall 12 and also promotes drainage by tilting the overhanging surface. Contributes to skip reduction.

In the heat exchanger 1 of the second embodiment mounted on the outdoor unit 20, water leakage is prevented by the presence of the blocking wall 12, and the flat tube 4 and the blocking portion 10 are arranged on one header pipe side. The fact that it is inclined so as to be low and a good drainage effect is obtained also contributes to the reduction of water jump.

In the heat exchanger 1 of the third embodiment mounted on the outdoor unit 20, water leakage is prevented by the presence of the blocking wall 12, and the flat tube 4 has a higher middle portion in the length direction than both ends. Moreover, the fact that a good drainage effect is obtained also contributes to the reduction of water splash.

The embodiment of the present invention has been described above, but the scope of the present invention is not limited to this, and various modifications can be made without departing from the spirit of the invention.

The present invention is widely applicable to side flow type parallel flow heat exchangers.

DESCRIPTION OF SYMBOLS 1

Heat exchanger

2, 3 Header pipe 4 Flat tube 5 Refrigerant passage 6 Fin 7, 8 Refrigerant inlet / outlet 10 Blocking part 11 Base part 12 Blocking wall 14 Groove 20 Outdoor unit 110 Outdoor unit 120 Indoor unit

Claims

A heat exchanger with the following configuration:
A plurality of header pipes arranged in parallel at intervals;
A flat tube disposed between the plurality of header pipes and having a refrigerant passage provided therein communicated with the inside of the header pipe;
A fin disposed between the flat tubes,
It is configured as a side flow parallel flow heat exchanger,
A blocking wall that covers the lower end of the fin from the outside is formed at the end of the flat tube on the surface where condensed water is collected.
The heat exchanger according to claim 1, comprising the following configuration:
The blocking wall is integrally formed with the flat tube, and the refrigerant passage is provided only in the flat tube portion and not in the blocking wall.
The heat exchanger according to claim 1, comprising the following configuration:
The flat tube has a higher middle portion in the length direction than both ends.
A heat exchanger according to claim 3, comprising:
The flat tube has a curved shape that is convex upward.
A heat exchanger according to claim 3, comprising:
The flat tube is highest at the center in the length direction.
The heat exchanger according to claim 1, comprising the following configuration:
In the direction that air passes through the heat exchanger, the flat tube is narrower than the fin.
The heat exchanger according to claim 1, comprising the following configuration:
A groove extending in the length direction is formed on the upper surface of the flat tube, and the groove is positioned substantially at the center of the flat tube in a direction perpendicular to the length direction.
Air conditioner indoor unit with the following configuration:
The heat exchanger according to any one of claims 1 to 7 is mounted.
An air conditioner outdoor unit having the following configuration:
The heat exchanger according to any one of claims 1 to 7 is mounted.