JP2018162953A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger that can inhibit a porous heat transfer pipe from being curved even when a length in a flow direction of a refrigerant flow passage of the porous heat transfer pipe is long.SOLUTION: A heat exchanger includes: a pair of header pipes 11a, 11b; and a plurality of porous heat transfer pipes 15 having a plurality of refrigerant flow passages 16. The heat transfer pipes 15 are connected in parallel with each other along an axial direction (x direction) of the header pipes 11a, 11b and provided with an auxiliary member 20 extending along an arrangement direction (z direction) of the refrigerant flow passages 16 between the porous heat transfer pipe 15 and the porous heat transfer pipe 15 adjacent to that.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a heat exchanger, in particular, a pair of header pipes and a plurality of multi-hole heat transfer tubes having a plurality of refrigerant flow paths, and air flowing between the plurality of multi-hole heat transfer tubes, The present invention relates to a heat exchanger that exchanges heat with a refrigerant flowing in a multi-hole heat transfer tube.

Conventionally, it is composed of a pair of header pipes and a plurality of multi-hole heat transfer tubes having a plurality of refrigerant flow paths, and the air flowing between the plurality of multi-hole heat transfer tubes and the refrigerant flowing in the multi-hole heat transfer tubes Heat exchangers that perform heat exchange are known.
As this type of heat exchanger, for example, a heat exchanger that does not have heat transfer fins that promote heat exchange between air and the multihole heat transfer tube is disclosed (for example, see Patent Document 1).
FIG. 8 is a configuration diagram showing a conventional heat exchanger described in Patent Document 1. As shown in FIG. As shown in FIG. 8, the heat exchanger 100 includes a pair of header pipes 101 and a plurality of multi-hole heat transfer tubes 102 having a plurality of refrigerant flow paths. It arrange | positions so that a flow direction may turn into a perpendicular direction.
As a result, when the heat exchanger 100 functions as an evaporator, the evaporation temperature of the refrigerant flowing in the multi-hole heat transfer tube 102 is lowered, so that moisture in the air adheres to the surface of the multi-hole heat transfer tube 102 and is generated. It is possible to drop the condensed water smoothly and improve the drainage of the condensed water.

WO2015 / 005352

However, in the conventional technique, when the heat exchanger is applied to a large-size air conditioner or the like, the size of the heat exchanger increases, and the flow direction length of the refrigerant flow path of the multi-hole heat transfer tube increases. Therefore, since the heat transfer fin is not provided between the multi-hole heat transfer tube and the multi-hole heat transfer tube, the multi-hole heat transfer tube cannot be held, and the multi-hole heat transfer tube is likely to be bent. .
The present invention has been made in view of the above-described points, and even when the length of the flow direction of the refrigerant flow path of the multi-hole heat transfer tube is long, the bending of the multi-hole heat transfer tube can be suppressed. An object is to provide a heat exchanger.

In order to solve the conventional problem, the heat exchanger of the present invention includes a pair of header pipes and a plurality of multi-hole heat transfer tubes having a plurality of refrigerant flow paths, and the plurality of multi-hole heat transfer tubes includes: In the heat exchangers connected in parallel to each other along the axial direction of the header pipe, between the multi-hole heat transfer tube and the adjacent multi-hole heat transfer tube, in the arrangement direction of the refrigerant flow path An auxiliary member extending along the line is provided.
As a result, even if the multi-hole heat transfer tubes are deformed due to the influence of gravity, the assembly error of the heat exchanger, or the difference in the expansion amount due to the temperature difference of the refrigerant flowing through the refrigerant flow path, the adjacent multi-hole heat transfer tubes are Contact can be suppressed.

According to the heat exchanger of the present invention, even if the multi-hole heat transfer tube is deformed due to the influence of gravity, the assembly error of the heat exchanger, or the difference in expansion due to the temperature difference of the refrigerant flowing in the refrigerant flow path, It can suppress that the matching multi-hole heat exchanger tube contacts.
As a result, the interval between adjacent multi-hole heat transfer tubes can be uniformly maintained, and clogging due to dirt and dust generated by the interval between adjacent multi-hole heat transfer tubes being narrowed can be suppressed, By suppressing the increase in ventilation resistance, it is possible to prevent a decrease in the air volume and improve the heat exchange performance of the heat exchanger.

The perspective view which shows the heat exchanger in 1st Embodiment of this invention. Sectional drawing which shows the heat exchanger in the xz plane of FIG. The perspective view which shows the outdoor unit at the time of heat exchanger mounting of 1st Embodiment. The perspective view which shows the heat exchanger in the modification of 1st Embodiment of this invention. The front view of FIG. The perspective view which shows the auxiliary member in the modification of 1st Embodiment. The enlarged view of the frame part of FIG. Sectional drawing which shows the conventional heat exchanger.

The first invention includes a pair of header pipes and a plurality of multi-hole heat transfer tubes having a plurality of refrigerant flow paths, and the plurality of multi-hole heat transfer tubes are parallel to each other along the axial direction of the header pipe. In the heat exchanger connected to, an auxiliary member extending along the arrangement direction of the refrigerant flow path is provided between the multi-hole heat transfer tube and the multi-hole heat transfer tube adjacent thereto.
According to this, since the auxiliary member extending along the arrangement direction of the refrigerant flow path is provided between the multi-hole heat transfer tube and the multi-hole heat transfer tube adjacent thereto, the influence of gravity, the heat exchanger Even if the multi-hole heat transfer tubes are deformed due to the difference in the expansion amount due to the assembly error or the temperature difference of the refrigerant flowing in the refrigerant flow path, it is possible to suppress the adjacent multi-hole heat transfer tubes from contacting each other.
As a result, the interval between adjacent multi-hole heat transfer tubes can be uniformly maintained, and clogging due to dirt and dust generated by the interval between adjacent multi-hole heat transfer tubes being narrowed can be suppressed, By suppressing the increase in ventilation resistance, it is possible to prevent a decrease in the air volume and improve the heat exchange performance of the heat exchanger.

Moreover, since the front edge part of the multi-hole heat exchanger tube with a high local heat transfer rate is not covered with an auxiliary member, the reduction of a heat exchange area can be suppressed and the heat exchange performance of a heat exchanger can be further improved. Can do.
In addition, in the case where the heat exchanger functions as an evaporator, condensed water is generated at the front edge of the multi-hole heat transfer tube, but it is possible to suppress the gap between adjacent multi-hole heat transfer tubes from being narrowed. And it can suppress that dew condensation water contacts the both surfaces of each multi-hole heat exchanger tube between multi-hole heat exchanger tubes. As a result, it is possible to prevent an increase in ventilation resistance and a decrease in the air volume due to condensed water, and to further improve the heat exchange performance of the heat exchanger.

In the second invention, the auxiliary member is in contact with the surface of the multi-hole heat transfer tube, and is connected to the downstream side in the air flow direction of the multi-hole heat transfer tube.
According to this, the multi-hole heat transfer tube is held in the three directions on the surface of the multi-hole heat transfer tube along the arrangement direction of the refrigerant flow path and the rear edge portion side of the multi-hole heat transfer tube. Even if the multi-hole heat transfer tube is deformed due to an influence, an assembly error of the heat exchanger or a difference in expansion amount due to a difference in temperature of the refrigerant flowing through the refrigerant flow path, it is possible to suppress the bending of the multi-hole heat transfer tube.
Moreover, since the front edge part of the multi-hole heat exchanger tube with a high local heat transfer rate is not covered with an auxiliary member, the reduction of a heat exchange area can be suppressed and the heat exchange performance of a heat exchanger can be further improved. Can do.

In a third aspect of the invention, the auxiliary member is provided at a substantially central portion in the flow direction of the refrigerant flow path of the multi-hole heat transfer tube.
According to this, the length in the flow direction of the refrigerant flow path from the upper end portion of the heat exchanger to the auxiliary member and the length in the flow direction of the refrigerant flow path from the lower end portion of the heat exchanger to the auxiliary member are both the shortest. Thus, the bending of the multi-hole heat transfer tube from the upper end portion of the heat exchanger to the auxiliary member and the multi-hole heat transfer tube from the lower end portion of the heat exchanger to the auxiliary member can be minimized.
In addition, the narrowing of the interval between adjacent multi-hole heat transfer tubes is minimized, clogging caused by narrowing the interval and increase in ventilation resistance are further suppressed, and the reduction in air volume can be prevented. The heat exchange performance can be further improved.

In a fourth aspect of the invention, the pair of header pipes are installed so as to extend in the horizontal direction, and the multi-hole heat transfer tube is installed so as to extend in the vertical direction.
According to this, since the curvature of the multi-hole heat transfer tube due to the influence of gravity is eliminated, it is possible to suppress the adjacent multi-hole heat transfer tubes from contacting each other.
Further, when the heat exchanger functions as an evaporator, the condensed water generated at the front edge of the multi-hole heat transfer tube can be quickly dropped, and the drainage of the condensed water can be improved.
Furthermore, the condensed water generated in the multi-hole heat transfer tube falls vertically downward and accumulates in the auxiliary member, and is quickly pushed away to the rear edge of the multi-hole heat transfer tube by the air flow. And the heat exchange performance can be further improved.

  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.

(First embodiment)
FIG. 1 is a perspective view showing a heat exchanger in the first embodiment of the present invention. FIG. 2 is a cross-sectional view of the heat exchanger in the xz plane of FIG.
As shown in FIG. 1, the heat exchanger 10 includes a pair of header pipes 11 a and 11 b, a plurality of multi-hole heat transfer tubes 15, and an auxiliary member 20.
Each header pipe 11a, 11b is installed in a substantially horizontal direction (x direction) with a predetermined interval. The plurality of multi-hole heat transfer tubes 15 are installed so as to extend in the vertical direction (y direction), respectively.

The header pipes 11a and 11b are formed in a substantially cylindrical shape by extruding a metal material such as aluminum, for example.
The refrigerant pipe 12a is connected to one end of one header pipe 11a, and the refrigerant pipe 12b is connected to one end of the other header pipe 11b. Each of the refrigerant pipes 12a and 12b is configured to function as a refrigerant inlet or outlet.

Moreover, as shown in FIG. 2, the multi-hole heat exchanger tube 15 is formed in plate shape by extruding metal materials, such as aluminum, for example. Inside the multi-hole heat transfer tube 15, a plurality of refrigerant flow paths 16 penetrating along the longitudinal direction of the multi-hole heat transfer tube 15 are formed in parallel.
The multi-hole heat transfer tubes 15 are arranged so that the side surfaces thereof face each other, and the multi-hole heat transfer tubes 15 are arranged in parallel to each other along the axial direction of the header pipes 11a and 11b. The refrigerant flow path 16 of each multi-hole heat transfer tube 15 is communicated with the inside of each header pipe 11a, 11b.

Then, the refrigerant that has flowed into the one header pipe 11a from one refrigerant pipe 12a flows in the vertically downward direction (−y direction) through each refrigerant flow path 16 of each multi-hole heat transfer tube 15, and the other header. It is sent to the inside of the pipe 11b. When the refrigerant flows through each refrigerant flow path 16 of the multi-hole heat transfer tube 15, heat exchange is performed with air flowing in the + z direction between the multi-hole heat transfer tubes 15. Then, the refrigerant sent to the other header pipe 11b flows out from the other refrigerant pipe 12b.
In addition, as a refrigerant | coolant, the mixed refrigerant | coolant containing R410A, R32, and R32 etc. are used, for example.

As shown in FIG. 2, the auxiliary member 20 is located between the multi-hole heat transfer tube 15 and the multi-hole heat transfer tube 15 adjacent to the multi-hole heat transfer tube 15 and extends in the arrangement direction of the refrigerant flow paths of the multi-hole heat transfer tube 15. A plurality of existing gap holding portions 21 and a connection extending in a direction substantially orthogonal to the gap holding portions 21 and connecting the downstream side (rear edge side) of the air flow direction of the multi-hole heat transfer tube 15 of each gap holding portion 21. Part 22. The auxiliary member 20 is formed of a metal material such as aluminum, for example, similarly to the multi-hole heat transfer tube 15.
In the present embodiment, the gap holding portion 21 of the auxiliary member 20 is in contact with the surface of the multi-hole heat transfer tube 15 along the arrangement direction of the refrigerant flow path 16, and the connecting portion 22 is connected to the multi-hole heat transfer tube 15. It is formed in a comb shape protruding from the downstream side (rear edge side) in the air flow direction. That is, the auxiliary member 20 is not provided on the upstream side of the multi-hole heat transfer tube 15 in the air flow direction.

In the present embodiment, the auxiliary member 20 is provided at a substantially central portion in the refrigerant flow direction (y direction) of the multi-hole heat transfer tube 15.
And in the heat exchanger 10 comprised as mentioned above, in the both directions of the multi-hole heat exchanger tube 15 along the arrangement direction of the refrigerant | coolant flow path 16, and the three edge directions of the rear edge part side of the multi-hole heat exchanger tube 15 The multi-hole heat transfer tube 15 is held.
In this case, the auxiliary member 20 may be fixed to each multi-hole heat transfer tube 15 by fitting the gap holding portion 21 or may be fixed by brazing, for example.

Next, the installation position of the auxiliary member 20 will be described.
As shown in FIGS. 1 and 2, the length of the refrigerant flow path 16 of the multi-hole heat transfer tube 15 in the y direction is L (mm), and the interval between the adjacent multi-hole heat transfer tubes 15 is S (mm).
The multi-hole heat transfer tube 15 is prone to bend due to its length becoming longer in manufacturing, and a maximum of 0.2% (L × 0.2%) bend with respect to L occurs. When the heat exchanger 10 is assembled using the curved multi-hole heat transfer tube 15, the interval between adjacent multi-hole heat transfer tubes 15 becomes more conspicuous.

Therefore, when the interval S between adjacent multi-hole heat transfer tubes 15 is 1 mm, if the multi-hole heat transfer tubes 15 are curved by 1 mm, the adjacent multi-hole heat transfer tubes 15 come into contact with each other. Since the curvature of 1 mm occurs when L = 1 / 0.2% = 500 mm, in order to suppress the curvature of less than 1 mm that does not contact the adjacent multi-hole heat transfer tube 15, the auxiliary member 20 is provided every 500 mm. May be provided.
Thereby, the influence of the curvature which generate | occur | produces on manufacture of the multi-hole heat exchanger tube 15 is suppressed, and when the assembly as the heat exchanger 10 is assembled, narrowing of the space | interval of the adjacent multi-hole heat exchanger tube 15 can be suppressed to the minimum. it can.
In addition, in this embodiment, although the auxiliary member 20 is provided only in one place of the flow direction (y direction) of the refrigerant flow path 16 of the multihole heat exchanger tube 15, you may provide in two or more places.

Moreover, in the case of the heat exchanger 10 used for a large sized air conditioning system etc., the size of the heat exchanger 10 becomes large and the axial direction (x direction) length of header pipe 11a, 11b becomes long. As described above, when the length of the header pipe is increased, the flow rate of the refrigerant flowing from the header pipes 11a and 11b to the multi-hole heat transfer tubes 15 tends to be uneven.
When the flow rate of the refrigerant flowing through each multi-hole heat transfer tube 15 becomes uneven, the temperature of each multi-hole heat transfer tube 15 varies. Therefore, the amount of change ΔL1 due to thermal expansion generated in the multi-hole heat transfer tube 15 at the lowest temperature is different from the amount of change ΔL2 due to thermal expansion generated in the multi-hole heat transfer tube 15 at the highest temperature.

For example, if the temperature difference between the multi-hole heat transfer tube 15 having the lowest temperature and the multi-hole heat transfer tube 15 having the highest temperature is ΔT and the linear expansion coefficient of the material of the multi-hole heat transfer tube 15 is α, The difference can be obtained by ΔL2−ΔL1 = α · L · ΔT.
Here, the temperature difference ΔT between the multi-hole heat transfer tube 15 having the lowest temperature and the multi-hole heat transfer tube 15 having the highest temperature is 5K, L is 500 mm, and the material of the multi-hole heat transfer tube 15 is aluminum (linear expansion coefficient α: 23 × 10 ⁻⁶ / K), the difference ΔL2−ΔL1 in elongation due to thermal expansion is 0.0575 mm.

Since the pair of header pipes 11a and 11b are in a fixed state, the multi-hole heat transfer tube 15 having the highest temperature is 0. 0 in the flow direction (y direction) of the refrigerant flow path 16 from the multi-hole heat transfer tube 15 having the lowest temperature. Without extending by 0575 mm, the header pipes 11a and 11b are curved in the axial direction (x direction) by 2.8 mm (calculated from the elliptical circumference).
When S is 1 mm, the multi-hole heat transfer tube 15 having the highest temperature is brought into contact with the adjacent multi-hole heat transfer tube 15 due to the curvature.
Therefore, when L is 500 mm, a curvature of 2.8 mm is generated. Therefore, in order to suppress the curvature of less than 1 mm that does not contact the adjacent multi-hole heat transfer tube 15, The auxiliary members 20 may be provided at intervals of 175 mm at the longest in the flow direction (y direction). Thereby, even when the flow volume of the refrigerant | coolant which flows into the several multi-hole heat exchanger tube 15 becomes non-uniform | heterogenous, the curvature of the multi-hole heat exchanger tube 15 by thermal expansion can be suppressed.

Next, the operation of the present embodiment will be described by taking as an example the case where the heat exchanger 10 of the present embodiment is used for the outdoor unit 20 of the air conditioner.
FIG. 3 is a perspective view showing an outdoor unit to which the heat exchanger 10 is applied.
As shown in FIG. 3, the outdoor unit 30 includes a box-shaped housing 31, and the housing 31 includes a top plate 32 and a bottom plate 33. An upper frame 34 that is bent vertically downward is formed at the peripheral edge of the top plate 32, and a lower frame 35 that is bent vertically upward is formed at the peripheral edge of the bottom plate 33. A space is formed between the top plate 32 and the bottom plate 33, and the heat exchanger 10 is installed in this space portion.
Then, by rotating and driving a blower fan (not shown) installed inside the outdoor unit 30, the outside air of the outdoor unit 30 is sucked from between the multi-hole heat transfer tubes 15 of the heat exchanger 10. Heat exchange between the refrigerant flowing through the refrigerant flow path of the hole heat transfer tube 15 and the external air is performed.

First, when performing a cooling operation, the heat exchanger 10 functions as a condenser.
The gas refrigerant sent from the compressor (not shown) of the outdoor unit 30 flows into the gas side header pipe 11a from the gas side refrigerant pipe 12a. This gas refrigerant passes through the inside of the gas-side header pipe 11a, flows into the refrigerant flow path 16 of the plurality of multi-hole heat transfer tubes 15, flows in the vertically downward direction (−y direction), and in the multi-hole heat transfer tubes 15, It is condensed by releasing heat by exchanging heat with air. The condensed refrigerant flows into the liquid-side header pipe 11b, passes through the liquid-side header pipe 11b, and flows out from the liquid-side refrigerant pipe 12b toward the indoor unit.

Next, when performing heating operation, the heat exchanger 10 functions as an evaporator.
In contrast to the cooling operation, the liquid refrigerant sent from the indoor unit flows into the liquid side header pipe 11b from the liquid side refrigerant pipe 12b. This liquid refrigerant passes through the inside of the header pipe 11b on the liquid side, flows into the refrigerant flow path 16 of the plurality of multi-hole heat transfer tubes 15, flows in the vertical upward direction (+ y direction), and in the multi-hole heat transfer tubes 15, Heat is absorbed and evaporated by heat exchange. The evaporated refrigerant flows into the gas-side header pipe 11a, passes through the gas-side header pipe 11a, and flows out from the gas-side refrigerant pipe 12a toward the compressor.

  When the heat exchanger 10 functions as an evaporator, a low-temperature refrigerant flows through the refrigerant flow path 16 of the multi-hole heat transfer tube 15 to exchange heat with air, and the multi-hole transfer having a particularly high local heat transfer coefficient. At the front edge of the heat tube 15, moisture in the air adheres to generate dew condensation water. The generated condensed water flows to the rear edge of the multi-hole heat transfer tube 15 by the flow of air while dropping due to its own weight in the vertically downward direction (−y direction).

  At this time, the upper and lower portions of the header pipes 11 a and 11 b and the heat exchanger 10 are covered with the upper frame 34 and the lower frame 35. However, unlike the upper end portion of the heat exchanger 10 and the lower end portion of the heat exchanger 10, the central portion of the heat exchanger 10 has a faster air flow than the upper and lower portions of the heat exchanger 10, The auxiliary member 20 is located in a portion where the heat transfer rate is high and condensed water is likely to be generated. As a result, the condensed water quickly drops onto the auxiliary member 20 and easily discharges the condensed water. Therefore, an increase in ventilation resistance can be suppressed and a decrease in the air volume can be prevented. The heat exchange performance can be further improved.

As described above, in the present embodiment, a pair of header pipes 11a and 11b and a plurality of multi-hole heat transfer tubes 15 having a plurality of refrigerant flow paths 16 are provided, and the plurality of multi-hole heat transfer tubes 15 are provided as headers. The pipes 11a and 11b are connected in parallel to each other along the axial direction (x direction), and between the multi-hole heat transfer tube 15 and the multi-hole heat transfer tube 15 adjacent to the multi-hole heat transfer tube 15, the arrangement direction (z The auxiliary member 20 extending along the direction) is provided.
Thereby, since the auxiliary member 20 extended along the arrangement direction (z direction) of the refrigerant | coolant flow path 16 was provided between the multi-hole heat exchanger tube 15 and the multi-hole heat exchanger tube 15 adjacent to this, gravity is provided. Even if the multi-hole heat transfer tubes 15 are deformed due to the influence of the above, the difference in expansion due to the assembly error of the heat exchanger 10 or the temperature difference of the refrigerant flowing in the refrigerant flow path 16, the adjacent multi-hole heat transfer tubes 15 are Contact can be suppressed.
As a result, the interval between adjacent multi-hole heat transfer tubes 15 can be kept uniform, and clogging due to dirt and dust generated by the interval between adjacent multi-hole heat transfer tubes 15 being narrowed can be suppressed. In addition, by suppressing an increase in ventilation resistance, it is possible to prevent a decrease in the air volume, and to improve the heat exchange performance of the heat exchanger 10.
Moreover, since the front edge part of the multi-hole heat exchanger tube 15 with a high local heat transfer rate is not covered with the auxiliary member 20, the reduction | decrease of a heat exchange area can be suppressed, and the heat exchange performance of the heat exchanger 10 is further improved. Can be improved.

Further, in the case where the heat exchanger 10 functions as an evaporator, condensed water is generated at the front edge portion of the multi-hole heat transfer tube 15, but it is possible to suppress the gap between adjacent multi-hole heat transfer tubes 15 from becoming narrow. Therefore, it is possible to prevent the condensed water from coming into contact with both surfaces of each multi-hole heat transfer tube 15 between the multi-hole heat transfer tubes 15. As a result, it is possible to prevent an increase in ventilation resistance and a decrease in the air volume due to condensed water, and the heat exchange performance of the heat exchanger 10 can be further improved.
Further, the dew condensation water generated in the multi-hole heat transfer tube 15 falls in the vertically downward direction (−y direction) and accumulates in the auxiliary member 20, and is quickly pushed away to the rear edge side of the multi-hole heat transfer tube 15 by the air flow. Therefore, the heat resistance due to condensed water is reduced, and the heat exchange performance can be further improved.

In the present embodiment, the auxiliary member 20 contacts the surface of the multi-hole heat transfer tube 15 and is connected to the downstream side of the multi-hole heat transfer tube 15 in the air flow direction.
Thereby, the multi-hole heat transfer tube 15 is held in the three directions on the surface of the multi-hole heat transfer tube 15 along the arrangement direction of the refrigerant flow path 16 and the rear edge portion side of the multi-hole heat transfer tube 15, Even if the multi-hole heat transfer tube 15 is deformed due to an influence of gravity, an assembly error of the heat exchanger 10 or a difference in expansion due to a temperature difference of the refrigerant flowing through the refrigerant flow path 16, the multi-hole heat transfer tube 15 is bent. Can be suppressed.

Further, in the present embodiment, the auxiliary member 20 is provided at a substantially central portion in the flow direction of the refrigerant flow path of the multi-hole heat transfer tube 15.
Thereby, the length of the refrigerant flow path 16 from the upper end of the heat exchanger 10 to the auxiliary member 20 in the flow direction (y direction) and the refrigerant flow path 16 from the lower end of the heat exchanger 10 to the auxiliary member 20 Both the lengths in the flow direction (y direction) are the shortest, the multi-hole heat transfer tube 15 from the upper end of the heat exchanger 10 to the auxiliary member 20, and the many from the lower end of the heat exchanger 10 to the auxiliary member 20. The curvature of the hole heat transfer tube 15 can be minimized.
Further, the narrowing of the interval between the adjacent multi-hole heat transfer tubes 15 is minimized, the clogging generated by the interval being narrowed, the increase in the ventilation resistance is further suppressed, the decrease in the air volume can be prevented, and the heat exchanger The heat exchange performance of 10 can be further improved.

In the present embodiment, the auxiliary member 20 is provided so as to be inclined so that the downstream side in the air flow direction of the multi-hole heat transfer tube 15 is lowered.
Thereby, in the case where the heat exchanger 10 functions as an evaporator, condensed water is generated at the front edge portion of the multi-hole heat transfer tube 15, but the auxiliary member 20 is located downstream of the multi-hole heat transfer tube 15 in the air flow direction. Since it is provided so as to be lowered, the condensed water dropped on the auxiliary member 20 can be efficiently sent to the rear edge portion side of the multi-hole heat transfer tube 15.

In the present embodiment, the pair of header pipes 11a and 11b are installed so as to extend in the horizontal direction, and the multi-hole heat transfer tube 15 is installed so as to extend in the vertical direction.
Thereby, when the heat exchanger 10 functions as an evaporator, the condensed water generated at the front edge portion of the multi-hole heat transfer tube 15 can be quickly dropped, and the drainage of the condensed water can be improved. .

In addition, this invention is not limited to the said embodiment, A various change is possible in the range which does not deviate from the meaning of this invention.
For example, in the above-described embodiment, the auxiliary member 20 is disposed so as to be horizontal (parallel to the xz plane), but is inclined so as to become lower toward the downstream side in the air flow direction (+ z direction). May be arranged.
Thereby, since the dew condensation water collected on the auxiliary member 20 can be easily drained more quickly, an increase in ventilation resistance can be suppressed, and a decrease in the air volume can be prevented, so that the performance of the heat exchanger 10 can be further improved.

In the embodiment, the front end portion of the gap holding portion 21 of the auxiliary member 20 extends to the front edge portion of the multi-hole heat transfer tube 15, but from the intermediate position in the arrangement direction (z direction) of the refrigerant flow paths 16. As long as it is between the front edge portion of the multi-hole heat transfer tube 15, the front end portion of the gap holding portion 21 may be in any position.
Thereby, since the part which covers the multi-hole heat exchanger tube 15 with the auxiliary member 20 can be reduced while ensuring the holding of the multi-hole heat exchanger tube 15, the heat exchange area can be ensured, and the heat exchange performance can be further increased. Can be improved.

Moreover, in the said embodiment, the surface of the auxiliary member 20 does not need to be flat.
FIG. 4 is a perspective view showing the heat exchanger 10 in a modification of the first embodiment. FIG. 5 is a front view of FIG. FIG. 6 is a perspective view showing the auxiliary member 20 in a modification of the first embodiment. FIG. 7 is an enlarged view of the frame portion in FIG. In addition, the same code | symbol is attached | subjected to the same part as 1st Embodiment shown in FIGS. 4-7, and the description is abbreviate | omitted.

As shown in FIGS. 4 to 7, a groove 23 extending in the air flow direction (z direction) is formed on the upper surface of the gap holding portion 21 of the auxiliary member 20. The groove 23 is formed in a V-shaped cross section.
Thereby, in the case where the heat exchanger 10 functions as an evaporator, dew condensation water is generated at the front edge of the multi-hole heat transfer tube 15, but this dew condensation water is accumulated in the groove 23, and due to the flow of air, Since it is sent to the rear edge of the multi-hole heat transfer tube 15, it becomes easier to discharge condensed water more quickly, and since the condensed water that touches the surface of the multi-hole heat transfer tube 15 decreases, the thermal resistance due to the condensed water decreases, The heat exchange performance of the heat exchanger 10 can be further improved.
In addition, by forming the groove 23, a flow path of air flowing in the + z direction in the vicinity of the auxiliary member 20 can be secured, and an increase in ventilation resistance due to the provision of the auxiliary member 20 is suppressed, thereby reducing the air volume Can be prevented, and the heat exchange performance can be further improved.
Although the auxiliary member 20 shown in FIGS. 4 to 7 is configured to form the groove 23 having a V-shaped cross section, the present invention is not limited to this. For example, you may make it form as an inclined surface other than cross-sectional shape U shape and cross-sectional shape W shape.

In the embodiment, the front end corner of the gap holding portion 21 of the auxiliary member 20 is formed at a substantially right angle. For example, the front end corner of the gap holding portion 21 is curved or flat chamfered. You may make it form in a shape.
Thereby, since the part which covers the multihole heat exchanger tube 15 with the auxiliary member 20 can be reduced, a heat exchange area can be ensured and heat exchange performance can further be improved.
Further, by chamfering the front end corner portion of the gap holding portion 21, when the auxiliary member 20 is inserted between the multi-hole heat transfer tube 15 and the multi-hole heat transfer tube 15, the heat exchanger 10 can be assembled. Time trouble can be reduced.

  Furthermore, in the said embodiment, although it arrange | positions so that the gap | interval holding | maintenance part 21 of the auxiliary member 20 may contact the surface of each multi-hole heat exchanger tube 15, the gap | interval holding | maintenance part 21 of the auxiliary member 20 is each multi-hole heat exchanger tube. If the minimum space | interval which 15 does not contact can be ensured, it does not necessarily need to contact the surface of the multi-hole heat exchanger tube 15. FIG.

  The present invention can suppress the bending of the multi-hole heat transfer tube 15 and improve the performance of the heat exchanger 10 in the heat exchanger 10 using the multi-hole heat transfer tube 15. It can be applied to other uses.

DESCRIPTION OF SYMBOLS 10 Heat exchanger 11a, 11b Header pipe 12a, 12b Refrigerant piping 15 Multi-hole heat exchanger tube 16 Refrigerant flow path 20 Auxiliary member 21 Gap holding part 22 Connection part 23 Groove 30 Outdoor unit 31 Case 32 Top plate 33 Bottom plate

Claims (4)

A heat exchange comprising a pair of header pipes and a plurality of multi-hole heat transfer tubes having a plurality of refrigerant flow paths, wherein the plurality of multi-hole heat transfer tubes are connected in parallel to each other along the axial direction of the header pipe In the vessel
A heat exchanger characterized in that an auxiliary member extending along the arrangement direction of the refrigerant flow path is provided between the multi-hole heat transfer tube and the multi-hole heat transfer tube adjacent thereto.   2. The heat exchanger according to claim 1, wherein the auxiliary member is in contact with a surface of the multi-hole heat transfer tube, and is connected to a downstream side in the air flow direction of the multi-hole heat transfer tube.   The heat exchanger according to claim 1 or 2, wherein the auxiliary member is provided at a substantially central portion in a flow direction of the refrigerant flow path of the multi-hole heat transfer tube.   The pair of header pipes are installed so as to extend in a horizontal direction, and the multi-hole heat transfer tubes are installed so as to extend in a vertical direction. The heat exchanger according to one item.

Images