JP2015017738A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger using a plurality of flat heat transfer tubes, which can suppress a drift flow of a refrigerant with a simple configuration, which is cheap and which has high heat exchange performance.SOLUTION: The heat exchanger includes: a plurality of fins 4 coming into contact with air; a plurality of flat heat transfer tubes 3 connected to the fins; and at least one pair of header pipes 21, 22 to which both end parts of the flat heat transfer tubes are connected. Also, the heat exchanger includes; an upstream side flow passage in which a refrigerant flows from one header pipe of the pair of header pipes to the other header pipe; and a downstream side flow passage which is provided at an upper part of the flow passage and which flows the refrigerant flowed into the other header pipe to the one header pipe from the other header pipe. The upstream side flow passage and the downstream side flow passage are configured by the plurality of flat heat transfer tubes respectively. At least one part of the plurality of flat heat transfer tubes configuring the upstream side flow passage and at least one part of the plurality of flat heat transfer tubes configuring the downstream side flow passage are configured in such a manner that a connection position to the other header pipe is deviated to the opposite directions with each other with respect to a center line of a ventilation direction in the header pipe.

Description

  The present invention relates to a heat exchanger having a plurality of flat heat transfer tubes and a plurality of fins, and is particularly suitable as a heat exchanger for an air conditioner.

  As a heat exchanger for an air conditioner, a cross fin tube type heat exchanger composed of circular copper heat transfer tubes and aluminum strip fins is generally used. In addition, as a fluid for flowing in the circular copper heat transfer tube, a chlorofluorocarbon refrigerant is used.

  On the other hand, for the purpose of miniaturization, light weight, high performance, and low cost, a plurality of flat heat transfer tubes brazed with aluminum fins on the outer surface, and header tubes respectively provided at both ends of the plurality of flat heat transfer tubes There is a parallel flow type heat exchanger in which the refrigerant flows. This parallel flow type heat exchanger is widely used in automobile radiators and air conditioners for cooling only. As this kind of heat exchanger, there is one described in Patent Document 1 (Japanese Patent Laid-Open No. 7-127789).

  In order to improve the performance of the heat exchanger, it is effective to effectively use the areas of all the fins brazed to the plurality of flat heat transfer tubes. For this purpose, it is necessary to flow an appropriate amount of refrigerant to each of the plurality of flat heat transfer tubes connected to the header tube. In the heat exchanger for an air conditioner constituting the refrigeration cycle, the refrigerant flows in a gas-liquid two-phase flow while undergoing a phase change such as evaporation or condensation inside the heat exchanger. For this reason, among the refrigerant flowing in the header pipe, the liquid component (liquid refrigerant) has a higher density than the gas component (gas refrigerant), and therefore is easily affected by gravity depending on the flow velocity. In particular, when the header pipe is provided in the vertical direction, the liquid refrigerant flowing in the header pipe tends to hardly flow upward in the header pipe due to the action of gravity. Accordingly, the flat heat transfer tube connected to the upper part of the header pipe has a liquid component of the refrigerant, which is smaller than that of the flat heat transfer pipe connected to the lower part of the header pipe, so that a predetermined heat exchange heat amount is ensured. There is a problem that heat exchange performance is not improved.

  Accordingly, in order to improve such refrigerant drift, Patent Document 2 (Japanese Patent Application Laid-Open No. 5-223490) discloses that a spiral groove is provided in the header pipe to give a swirling component to the refrigerant in the header pipe. Have been described. In this Patent Document 2, a plurality of header tubes having different diameters are used in order to obtain an effective swirl component in accordance with the mass speed and dryness of the refrigerant. However, in this patent document 2, since it is necessary to use a plurality of header tubes provided with spiral grooves inside, there is a problem that the number of parts increases and the cost increases.

  In addition, in the heat exchanger using the flat heat transfer tube, as another conventional technique for improving the drift of the refrigerant, there is one described in Patent Document 3 (Japanese Patent Laid-Open No. 2010-25434). . In this Patent Document 3, the flat heat transfer tube connected to the header tube is inclined, and the swirled refrigerant is applied to the inclined surface of the flat heat transfer tube in the header tube so that the liquid refrigerant does not flow downward in the header tube. In this way, an upward flow is obtained. However, in the thing of this patent document 3, since the flat heat exchanger tube is inclined and connected to the header pipe | tube, the ventilation resistance in the case of flowing air perpendicularly | vertically with respect to the plane of a heat exchanger increases. The blast power increases and the heat exchange performance decreases. In addition, the process of providing the flat heat transfer tube obliquely becomes complicated and increases the cost. In addition, in the case where the flat heat transfer tube is twisted from a position away from the header tube by a predetermined distance to the end thereof, it is difficult to process the flat heat transfer tube, and the cost is increased. There is a problem that the ventilation resistance of the twisted portion to the position separated by the predetermined distance is still large.

Japanese Patent Laid-Open No. 7-127989 JP-A-5-223490 JP 2010-25434 A

  As described above, in the parallel flow type heat exchanger using a flat heat transfer tube as described in Patent Document 1, the liquid refrigerant flowing in the header tube hardly flows upward in the header tube due to the action of gravity. For this reason, there is a problem in that the refrigerant is likely to drift between the plurality of flat heat transfer tubes provided on the upper portion (downstream side), and the heat exchange performance is deteriorated.

  In order to improve this refrigerant drift, there are those described in Patent Documents 2 and 3 above, but in the case of using a plurality of header pipes having spiral grooves and different diameters, the number of parts increases. There is a problem of increasing costs. In addition, if the flat heat transfer tube connected to the header pipe is tilted so that the liquid refrigerant does not flow downward in the header pipe, the swirled refrigerant is applied to the inclined surface of the flat heat transfer pipe in the header pipe. However, the heat exchange performance is lowered and the cost is increased.

  An object of the present invention is to obtain a heat exchanger that can suppress the drift of refrigerant with a simple configuration, is inexpensive, and has high heat exchange performance, with respect to a heat exchanger that uses a plurality of flat heat transfer tubes.

  In order to achieve the above object, the present invention includes a plurality of fins in contact with air, a plurality of flat heat transfer tubes connected to the fins, and at least a pair of header tubes to which both ends of the flat heat transfer tubes are connected. In the heat exchanger, an upstream flow path that flows from one header pipe of the pair of header pipes to the other header pipe, and a refrigerant that is provided in the upper part of the flow path and flows into the other header pipe, A downstream flow path that flows from the header pipe to the one header pipe, wherein the upstream flow path and the downstream flow path are each composed of a plurality of flat heat transfer tubes, and a plurality of flats constituting the upstream flow path At least a part of the heat transfer tube and at least a part of the plurality of flat heat transfer tubes constituting the downstream-side flow path are connected to the other header pipe with respect to the center line in the ventilation direction of the header pipe. Not in opposite directions Characterized in that as the configuration.

  ADVANTAGE OF THE INVENTION According to this invention, with respect to the heat exchanger using a some flat heat exchanger tube, the drift of a refrigerant | coolant can be suppressed with a simple structure, and there exists an effect which can obtain a heat exchanger with high heat exchange performance at low cost.

The longitudinal cross-sectional view which shows Example 1 of the heat exchanger of this invention. Sectional drawing of the flat heat exchanger tube shown in FIG. The arrow sectional drawing in the AA line in the heat exchanger shown in FIG. 1, BB line, CC line, and DD line. The figure which looked at the header pipe | tube shown in FIG. 1 from the IV-IV line arrow direction of FIG. 1, and is a figure explaining the connection position to the header pipe | tube of a flat heat exchanger tube. The figure explaining the flow of the refrigerant | coolant in the header pipe | tube in Example 1 of this invention and the conventional heat exchanger. It is a figure explaining Example 2 of the heat exchanger of this invention, and is horizontal sectional drawing which shows the structure of the connection part of a header pipe and a flat heat exchanger tube. It is a figure explaining Example 3 of the heat exchanger of this invention, and is horizontal sectional drawing which shows the structure of the connection part of a header pipe and a flat heat exchanger tube. It is a figure explaining Example 4 of the heat exchanger of this invention, and is horizontal sectional drawing which shows the structure of the connection part of a header pipe and a flat heat exchanger tube. It is a figure which shows Example 5 of the heat exchanger of this invention, and is a figure explaining the connection structure of the flat heat exchanger tube and fin in a heat exchanger. It is a figure explaining Example 6 of the heat exchanger of this invention, and is a figure of the part corresponded in FIG. It is a figure explaining Example 7 of the heat exchanger of this invention, and is a figure which shows the part of the header pipe | tube in a heat exchanger. It is a figure explaining the structure of the conventional heat exchanger, and is a figure equivalent to (A) or (B) of FIG. The figure explaining the state of the refrigerant | coolant in a heat exchanger in the case of making a heat exchanger act as an evaporator.

  Hereinafter, specific examples of the heat exchanger of the present invention will be described with reference to the drawings. In each figure, the part which attached | subjected the same code | symbol has shown the part which is the same or it corresponds.

A heat exchanger according to a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a longitudinal sectional view showing a parallel flow type heat exchanger targeted by this embodiment. The heat exchanger 1 is a plurality of flat heat transfer tubes 3 arranged in parallel to the direction of gravity, and a plurality of aluminum fins 4 are fixed to the flat heat transfer tubes 3 by brazing. Both ends of the flat heat transfer tube 3 are fixed by brazing between a pair of header tubes, that is, a first header tube 21 and a second header tube 22.

  A refrigerant inlet pipe 25 and an outlet pipe 26 are attached to the first header pipe 21. In each of the first header pipe 21 and the second header pipe 22, partition plates 24a, 24b and 24c for partitioning spaces are provided as shown in the figure.

  Each of the plurality of flat heat transfer tubes 3 is configured as shown in FIG. That is, the flat heat transfer tube 3 is made of aluminum, and is formed with a refrigerant flow path 31 partitioned into a plurality of parts by extrusion or the like. The shape of the coolant channel 31 may be a circle or an ellipse in addition to the rectangle as shown in FIG. Further, it is possible to provide fins in the refrigerant flow path 31. For example, a plurality of refrigerant flow paths are formed by forming the refrigerant flow path in one horizontally long hole and providing corrugated fins in the hole. It is good also as a flat heat exchanger tube made to form.

  In the heat exchanger 1 in FIG. 1, the direction of ventilation of air or the like is a direction perpendicular to the paper surface. Further, the refrigerant enters the first header pipe 21 from the inlet pipe 25 and passes through the first flow path 52a formed by the flat heat transfer pipe 3 as indicated by the refrigerant flow 52 indicated by the white arrow. And then enters the second header pipe 22, flows from here through the second flow path 52b and enters the first header pipe 21, and similarly, through the third flow path 52c and the fourth flow path 52d. It is configured to flow out from the outlet pipe 26 provided in the first header pipe 21. And it is comprised so that heat exchange may be performed between the refrigerant | coolant which flows through the inside of the said flat heat exchanger tube 3, and the air which flows between the fins 4. FIG.

  The partition plate 24a is provided in the first header pipe 21 so as to partition the inlet side to the first channel 52a and the outlet side of the second channel 52b. The partition plate 24b is provided in the second header pipe 22 so as to partition the inlet side to the second channel 52b and the outlet side of the third channel 52c. The partition plate 24c is provided in the first header pipe 21 so as to partition the inlet side to the third flow path 52c and the outlet side of the fourth flow path 52d.

  In the air conditioner constituting the refrigeration cycle, the outdoor heat exchanger acts as an evaporator and the indoor heat exchanger acts as a condenser under heating conditions. Under cooling conditions, the refrigerant flows in the opposite direction, with the outdoor heat exchanger acting as a condenser and the indoor heat exchanger acting as an evaporator.

  The state of the refrigerant flowing in the heat exchanger 1 when the heat exchanger 1 acts as an evaporator will be described. After passing through an expansion valve (not shown) of the refrigeration cycle, the low-saturation refrigerant having a low dryness flows into the header pipe 21 from the inlet pipe 25 and is located in the lower part of the heat exchanger 1. In the plurality of flat heat transfer tubes 3 of the flow path 52a. The refrigerant in the heat exchanger 1 flows between the header pipe 21 and the header pipe 22 from the partition plates 24a, 24b, and 24c provided in the header pipes 21 and 22, and flows into the heat exchanger 1. It evaporates by exchanging heat with the air being ventilated and flows while increasing the dryness. The refrigerant is finally configured to flow out of the heat exchanger 1 from the outlet pipe 26 of the header pipe 21.

  When the heat exchanger 1 acts as a condenser, the flow of the refrigerant in the heat exchanger 1 flows in the opposite direction to the case where it acts as an evaporator. Further, when acting as a condenser, the refrigerant flows in a superheated gas state at the inlet portion of the heat exchanger 1 and is liquefied by a condensation action due to heat exchange with air, and most of the refrigerant flowing in the heat exchanger is saturated. In the vicinity of the outlet of the heat exchanger 1, a complete liquid state (supercooled state) is obtained.

The state of the refrigerant in the heat exchanger 1 when the heat exchanger acts as an evaporator will be described in more detail with reference to FIG.
FIG. 13A is a diagram illustrating a case where the refrigerant does not flow properly to each flat heat transfer tube 3 in the heat exchanger. A hatched portion 53 is a region where the refrigerant is at a saturation temperature (saturation region), and the refrigerant in the saturation region (saturation temperature) has a relatively high heat transfer coefficient and contributes to heat exchange. In the vicinity of the outlet of the heat exchanger 1, as indicated by 54, the refrigerant becomes a superheated gas region (superheated gas region). When the refrigerant does not flow properly to each flat heat transfer tube 3, as shown in FIG. (A), the superheated gas region 54 appears in the specific flat heat transfer tube 3 considerably before the outlet in the fourth flow path 52 d. That is, in the flat heat transfer tubes 3 arranged above the plurality of flat heat transfer tubes 3 constituting the fourth flow path 52d, the superheated gas region 54 is further spread from the outlet side to the inlet side of the fourth flow path 52d. ing.

  In the superheated gas region 54, the liquid component in the refrigerant is in a state of being lost, and compared to the liquid refrigerant in the saturated region 53, it is difficult to contribute to heat exchange. Moreover, the flat refrigerant | coolant tube 3 arrange | positioned below among the several flat heat exchanger tubes 3 which comprise the said 4th flow path 52d increases the ratio of a liquid refrigerant, and as shown to (A) figure, a 4th flow path is shown. The liquid refrigerant exists up to the outlet side of 52d. For this reason, the liquid component of the refrigerant | coolant supplied to the compressor (not shown) of a refrigerating cycle increases, and a possibility that a compressor will carry out liquid compression arises. Therefore, in the vicinity of the outlet of the heat exchanger 1, it is necessary to make a superheated gas state in order to prevent liquid compression due to the flow of liquid refrigerant to the compressor. In order to achieve this superheated gas state, it is possible to secure a superheated gas region by lowering the evaporation temperature (evaporation pressure), but there is a problem that the compressor power increases.

  FIG. 13B is a diagram for explaining a case where the refrigerant appropriately flows through the flat heat transfer tubes 3 in the heat exchanger 1 and the flow state of the refrigerant is ideal. In this ideal state, as shown in FIG. (B), a plurality of flats forming the fourth flow path 52d at a position where the superheated gas region 54 is close to the outlet of the fourth flow path 52d. It originates from the position where the heat transfer tubes 3 are aligned. Therefore, the liquid component of the refrigerant supplied to the compressor of the refrigeration cycle can be eliminated or reduced, and the compressor can be prevented from liquid compression. Further, since the refrigeration cycle can be operated at a higher evaporation temperature (evaporation pressure), an increase in compressor power can be suppressed.

  In order to achieve the state shown in FIG. (B), it is necessary to make the amount of liquid refrigerant flowing through the plurality of flat heat transfer tubes 3 constituting each flow path as uniform as possible. Accordingly, a description will now be given of this embodiment for making the amount of liquid refrigerant flowing through the plurality of flat heat transfer tubes 3 constituting each flow path as uniform as possible.

  First, the configuration of a conventional heat exchanger will be described with reference to FIG. The conventional heat exchanger also has substantially the same configuration as the heat exchanger shown in FIG. That is, also in the conventional heat exchanger, a plurality of fins 4 in contact with air, a plurality of flat heat transfer tubes 3 connected to the fins 4, and both ends of the flat heat transfer tubes 3 are connected so that the horizontal section is circular. A first header pipe 21 and a second header pipe 22 having a shape are provided. A plurality of the flat heat transfer tubes 3 are installed in the direction perpendicular to the paper surface of FIG.

  In the conventional heat exchanger, as shown in FIG. 12, the characteristic points are a center line X in the ventilation direction 51 in the first header pipe 21 and the second header pipe 22 and a center line in the flat heat transfer pipe 3. The flat heat transfer tube 3 is connected to the first header tube 21 and the second header tube 22 so that M matches. That is, the center line X in the ventilation direction 51 in the first header pipe 21 and the second header pipe 22 and the center line M of the flat heat transfer pipe 3 are configured to substantially coincide with each other within the range of processing accuracy. is there. Therefore, in each of the first to fourth flow paths 52a to 52d, among the refrigerants in the gas-liquid two-phase state, the liquid refrigerant easily flows to the flat heat transfer tube 3 below due to the influence of gravity, and the gas refrigerant is It becomes easy to flow to the flat heat transfer tube 3. For this reason, the flow rate of the liquid refrigerant flowing into the plurality of flat heat transfer tubes 3 constituting the flow path is likely to be non-uniform as the flow path on the downstream side where the ratio of the gas refrigerant increases, the refrigerant in the heat exchanger This is the state described with reference to FIG.

  On the other hand, as shown in FIG. 13B, the structure of the heat exchanger of the present embodiment that can ideally flow the refrigerant will be described with reference to FIGS. 3 is a cross-sectional view taken along the lines AA, BB, CC, and DD in the heat exchanger shown in FIG. 1, and FIG. 3A is an AA line in FIG. 1 is a cross-sectional view taken along line CC, FIG. 4B is a cross-sectional view taken along line BB or DD in FIG. 1, and FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. It is the figure seen from the arrow direction and is a figure explaining the connection position to the header pipe of a flat heat exchanger tube.

  In FIG. 3, X is the center line of the first header pipe 21 and the second header pipe 22 in the ventilation direction 51, and M is the center line of the flat heat transfer pipe 3 (center line in the ventilation direction).

  As shown in FIG. 3A, the flat heat transfer tubes 3 constituting the first flow path 52a and the third flow path 52c in FIG. With respect to the center line X of the ventilation direction 51 in the header pipe 21 and the second header pipe 22, within the range of the inner dimensions of the header pipes 21 and 22, it is shifted to the downstream side of the ventilation direction (air flow direction) 51, The header pipes 21 and 22 are connected.

  Further, as shown in FIG. 3B, the flat heat transfer tubes 3 constituting the second flow channel 52b and the fourth flow channel 52d in FIG. The header pipes are shifted to the upstream side of the ventilation direction 51 within the range of the inner dimensions of the header pipes 21 and 22 with respect to the center line X of the ventilation direction 51 in the first header pipe 21 and the second header pipe 22. 21 and 22 are connected.

  With reference to FIG. 4, the connection position of the flat heat transfer tube 3 in the first header pipe 21 arranged in the vertical direction (opening attachment position of the flat heat transfer tube 3 in the header pipe 21) will be described. 4 is a view seen from the direction of arrows IV-IV in FIG. 1, and the first header pipe 21 of the flat heat transfer tube 3 in the second flow path 52b to the fourth flow path 52d shown in FIG. The connection position (opening position) is shown. Moreover, the flow direction of the refrigerant | coolant in the 2nd-4th each flow path is also shown. Furthermore, the direction of the spiral in each part in the first header pipe 21 is also illustrated.

  As shown in FIG. 4, in each flow path in which the refrigerant flows in the same direction, the plurality of flat heat transfer tubes 3 constituting each flow path are attached to the same side with respect to the first header pipe 21. It has been. For this reason, a swirl flow (swirling upward flow) 521 in the same direction is generated in the first header pipe 21. As a result, the liquid refrigerant is wound up by the action of the swirl upward flow 521 larger than the gravity acting on the liquid refrigerant, and the liquid refrigerant can be transferred together with the gas refrigerant above the first header pipe 21.

  In the present embodiment, the plurality of flat heat transfer tubes 3 constituting the upstream flow path (second flow path 52b in FIG. 4) and the plurality constituting the downstream flow path (third flow path 52c in FIG. 4). 4, the connection position to the first header pipe 21 is shifted in the opposite direction with respect to the center line of the first header pipe 21 in the ventilation direction. That is, the flat heat transfer tube 3 constituting the second flow path is connected to the first header 21 while being shifted to the upstream side in the ventilation direction and the flat heat transfer tube 3 constituting the third flow path is shifted to the downstream side in the ventilation direction. Therefore, in the first header pipe 21, the swirl direction of the refrigerant flowing from the second flow path 52b matches the swirl direction of the refrigerant flowing into the third flow path 52c, and the strength of the swirl upward flow 521 is increased. Can be maintained further upward. As a result, since the liquid refrigerant can be sent upward together with the gas refrigerant, the liquid refrigerant flowing into the header pipe from the upstream flow path is also uniformly flown by the plurality of flat heat transfer tubes 3 constituting the downstream flow path. The effect which can be made is acquired.

Although only the configuration on the first header pipe 21 side has been described in FIG. 4, the second header pipe 22 side has the same configuration, and the same effects as those described above can be obtained.
That is, a plurality of flat heat transfer tubes 3 constituting the upstream flow passage in the second header pipe 22 connecting the third flow passage 52c and the fourth flow passage 52d, and a plurality constituting the downstream flow passage. The flat heat transfer tubes 3 are connected to the center line of the second header tube 22 while being shifted in opposite directions. In particular, the third flow path 52c and the fourth flow path 52d increase in dryness and the proportion of liquid refrigerant decreases, so that the liquid refrigerant is evenly distributed to the plurality of flat heat transfer tubes 3 constituting the fourth flow path 52d. Although it becomes more difficult to distribute, it becomes possible to distribute liquid refrigerant more uniformly by configuring as in the present embodiment.

  Further, the plurality of flat heat transfer tubes 3 constituting the upstream flow passage in the second header pipe 22 connecting the first flow passage 52a and the second flow passage 52b, and the plurality constituting the downstream flow passage. The flat heat transfer tubes 3 may be connected so as to be shifted in opposite directions with respect to the center line of the second header tube 22.

  In this embodiment, the connection position between the outlet side of the fourth flow path 52d and the header pipe 21 in the first header pipe 21 separated via the partition plate 24c, and the third flow path 52c The connection position between the inlet side and the header pipe 21 is shifted in the opposite direction with respect to the center line X in the ventilation direction 51 in the header pipe 21. The connection positions of the upstream flow path and the downstream flow path in each of the other partition plates 24a, 24b, and 24d are also shifted in opposite directions with respect to the center line X in the ventilation direction of each header pipe. It has a configuration.

  FIG. 5 is a diagram for explaining the flow of the refrigerant in the header pipe in the first embodiment and the conventional heat exchanger, and schematically showing the result of analyzing the flow of the refrigerant in the header pipe. In this analysis, the refrigerant is treated as a homogeneous flow and treated as a single-phase flow. The flow line of the refrigerant in the conventional heat exchanger is shown in FIG. 5 (A), and the flow line in the present embodiment is shown in FIG. 5 (B).

  (A) In the conventional heat exchanger shown in the figure, the refrigerant flows from each flat heat transfer tube 3 into the header tube 22 and flows from the header tube 22 to the upper flat heat transfer tube 3 (stream line 522). There is no regularity. Further, the number of streamlines 522 reaching the top of the header pipe 22 is reduced.

  On the other hand, in the case of the heat exchanger according to the present embodiment, as shown in FIG. 5B, a swirl flow 521 having a high speed is generated in the header pipe 22, and the swirl flow 521 reaches the upper part of the header pipe 22. You can see that That is, since the heat exchanger has the structure of the present embodiment, the refrigerant (particularly the liquid refrigerant) can be more uniformly distributed to the plurality of flat heat transfer tubes 3 forming the downstream flow path. It becomes possible to flow the refrigerant in the heat exchanger 1 in a state as shown in FIG. Therefore, according to the present Example, the drift of a refrigerant | coolant can be suppressed with a simple structure, using the some flat heat exchanger tube 3, and the effect which can obtain a heat exchanger with high heat exchange performance cheaply is acquired.

  Embodiment 2 of the heat exchanger of the present invention will be described with reference to FIG. 6A is a horizontal sectional view showing an outflow portion from the second flow path 53b in the first header pipe 21, and FIG. 6B is a view to the third flow path 53c in the first header pipe 21. It is sectional drawing of the horizontal direction which shows an inflow part. In addition, in the (B) figure, the inlet_port | entrance part of the flat heat exchanger tube 3 is shown in the cross section.

  In the second embodiment, the end opening portion of the flat heat transfer tube 3 connected to the first header tube 21 is bent in the surface direction of the flat heat transfer tube, that is, on the same plane, in a “<” shape. It is what. More specifically, the flat heat transfer tube 3 constituting the second flow path 52b (upstream flow path) and the first header pipe 21 of the flat heat transfer tube 3 constituting the third flow path 52c (downstream flow path). In the connecting portion, each flat heat transfer tube 3 is bent in the horizontal plane direction so that the opening direction of the flat heat transfer tube 3 in the first header tube 21 is opposite to the center line of the header tube. It is set as the structure which gives.

  With this configuration, the refrigerant that has flowed into the first header pipe 21 from the second flow path 52b swirls along the inner surface of the header pipe 21 as shown in FIG. And flows upward, which is the direction of flow of the refrigerant. The refrigerant that has flowed upward is flat heat transfer tubes from the inflow portion of the flat heat transfer tube 3 constituting the third flow path 52c formed along the swirl direction of the swirl flow 521, as shown in FIG. 3 can flow smoothly.

  Therefore, by configuring as in the present embodiment, the same swirl flow 521 as in the first embodiment can be generated, and the refrigerant is supplied to the plurality of flat heat transfer tubes 3 forming the downstream flow path. It can be distributed more uniformly. Therefore, the refrigerant can be flowed through the heat exchanger 1 in a state as shown in FIG. 13B, and the same effect as in the first embodiment can be obtained.

  Moreover, according to the second embodiment, the flat heat transfer tube 3 constituting the upstream flow path (second flow path 52b in the present embodiment) and the downstream flow path (third flow path 52c in the present embodiment) are provided. The ends of the flat heat transfer tubes are arranged so that the opening directions in the header tubes (first header tubes 21 in this embodiment) of the flat heat transfer tubes 3 are opposite to each other with respect to the center line of the header tubes. In addition, since it is configured to bend in the plane direction, there are the following effects. That is, it is not necessary for the flat heat transfer tubes 3 themselves constituting each flow path to be shifted in opposite directions with respect to the center line of the header tube, and from the flat heat transfer tubes 3 on the lower side to the flat heat transfer tubes on the upper side. Up to 3, the position of the through holes (through holes for penetrating the flat heat transfer tubes 3) formed in the fins 4 can be arranged in the airflow direction, for example, aligned with the center line of the header pipe. Therefore, it is possible to obtain a heat exchanger that is easy to process and assemble and has a good appearance.

  In FIG. 6, the outflow part from the second flow path 53b and the inflow part to the third flow path 53c on the first header pipe 21 side have been described, but the outflow part from the fourth flow path 52d is also described above (A ) The configuration is the same as that shown in the figure, and the second header tube 22 side has the same configuration as the first header tube 21 side described above.

  Embodiment 3 of the heat exchanger of the present invention will be described with reference to FIG. 7A is a horizontal sectional view showing an outflow portion from the second flow path 53b in the first header pipe 21, and FIG. 7B is a view to the third flow path 53c in the first header pipe 21. It is sectional drawing of the horizontal direction which shows an inflow part. In addition, in the (B) figure, a part of inlet part of the flat heat exchanger tube 3 is shown in cross section.

  In the third embodiment, the end of the flat heat transfer tube 3 connected to the first header tube 21 is bent in the horizontal plane direction as shown in FIG. 7, and the end of the flat heat transfer tube 3 in the header tube 21 is bent. The portion 3a is configured to be parallel to the portion (fin portion) 3b where the fins 4 are provided.

  That is, also in the third embodiment, as in the second embodiment, the flat heat transfer tube 3 constituting the second flow path 52b (upstream flow path) and the third flow path 52c (downstream flow path) are formed. In the connecting portion of the flat heat transfer tube 3 to the first header tube 21, the opening direction of the flat heat transfer tube 3 in the first header tube 21 is opposite to the center line of the header tube. The flat heat transfer tubes 3 are bent.

  In the third embodiment, the connection position of the flat heat transfer tube end portion 3a to the header tube is the same as that in the first embodiment, as shown in FIGS. The configuration is shifted in opposite directions with respect to the center line. Even when configured as in the third embodiment, the same effects as in the first and second embodiments can be obtained.

  Embodiment 4 of the heat exchanger of the present invention will be described with reference to FIG. 8A is a horizontal sectional view showing an outflow portion from the second flow path 53b in the first header pipe 21. FIG. FIG. 5B is a horizontal sectional view of the same portion as FIG. 5A in the first embodiment, and is a diagram for showing the fourth embodiment in comparison with the first embodiment.

  (B) In the case of Example 1 shown in the figure, the flat heat transfer tube 3 is an extruded tube manufactured by extrusion molding, and has the same cross-sectional shape from one end to the other end of the flat heat transfer tube 3. The refrigerant flow path 31 in the flat heat transfer tube is also formed from one end to the other end.

  On the other hand, the flat heat transfer tube 3 of the fourth embodiment shown in FIG. (A) has an aluminum case member 32 having one rectangular through hole, and an inner fin 33 is provided in the through hole of the case member 32. The case where it is set as the inner fin type which forms the some refrigerant | coolant flow path 31 by providing is shown. In this way, the flat heat transfer tube 3 can be configured as an inner fin type, and the same effect as in the case of the extruded tube of Example 1 can be obtained. Moreover, when it is set as such an inner fin type | mold, it becomes possible to provide the space part 34 without an inner fin in the edge part opening part side of the flat heat exchanger tube 3. FIG. Accordingly, by narrowing the space 34 in the direction toward the inner wall of the header pipe 21 as shown in FIG. 5A, the refrigerant can flow out in the direction of the inner wall of the header pipe, and the flow is reduced by the amount of the narrowed portion. Since the flow velocity of the refrigerant to be increased can be increased, an effect of generating a stronger swirl flow 521 in the header pipe 21 can be obtained. Therefore, the liquid refrigerant can be distributed more uniformly, and the drift of the refrigerant can be further suppressed, and a heat exchanger with high heat exchange performance can be obtained.

  In addition, it can be set as the same structure also about the connection part with the other flat heat exchanger tube 3 in the 1st, 2nd header pipes 21 and 22. FIG. However, with respect to the inflow portion side of the flat heat transfer tube 3 constituting the second to fourth flow paths, it is possible to smoothly flow in the refrigerant by not providing a restriction in the space portion 34. That is, in the fourth embodiment, the flat heat transfer tube 3 itself is configured to be shifted with respect to the center line in the ventilation direction in the header tube 21 as in the first embodiment. It is not essential to provide it.

  A fifth embodiment of the present invention will be described with reference to FIG. FIG. 9 is a diagram for explaining a connection configuration between the flat heat transfer tube and the fin. FIG. 9A is a configuration in which the fin is formed in a strip shape, and the flat heat transfer tube 3 is inserted by providing a through hole 41a in the strip fin. The figure which shows the penetration type | mold fin 41 which was shown, (B) figure is a figure which shows the insertion type | mold fin 42 which provided the notch 42a in the one end of a strip-shaped fin, and inserted the flat heat exchanger tube 3 in this notch 42a. (C) is a figure which shows the corrugated type fin 43 made into the structure which inserts between the flat heat exchanger tubes 3 which adjoined vertically the corrugated fin bent in the shape of a mountain valley (zigzag shape).

  As shown in these FIGS. (A) to (C), in the present embodiment, all the flat heat transfer tubes 3 constituting the respective flow paths in the vertical direction are attached to the same fin. For each flow path, the position of the through hole 41a is shown in FIG. 5A so that the connection position to the header pipes 21 and 22 can be shifted in the opposite direction with respect to the center line in the ventilation direction of the header pipe. The flow paths are shifted in the horizontal direction for each flow path, and in FIG. (B), the shapes of the cuts 42a are all the same, but the installation position of the flat heat transfer tube 3 is shifted in the horizontal direction in the drawing. Yes. Moreover, in the (C) figure, it is comprised so that it may shift to the left-right direction of a figure via the corrugated fin 43a for every said flow path.

With this configuration, a swirl flow can be formed in each of the header pipes 21 and 22 as shown in the drawings as shown in the lower diagrams of (A) to (C). That is, as shown in the above-mentioned drawings (A) to (C), each of the embodiments of the present invention described above can be realized with any of these types of fins.
In any type of fins shown in FIGS. (A) to (C), after the fins and the flat heat transfer tubes 3 are assembled, they can be integrally fixed by brazing or the like.

A sixth embodiment of the present invention will be described with reference to FIG. FIG. 10 is a diagram corresponding to FIG. 4 described above.
1 to 9 described above, for each of the first to fourth flow paths, all of the plurality of flat heat transfer tubes 3 constituting each flow path are ventilated in the header pipes 21, 22. The example in which each channel is configured to be shifted in the opposite direction with respect to the direction center line has been described. On the other hand, in Example 6 shown in FIG. 10, the plurality of flat heat transfer tubes 3 constituting each flow path are not aligned and shifted to one side. It is the structure which shifts only a part of them to one side.

That is, in the example shown in FIG. 10, among the eight flat heat transfer tubes 3 constituting the third flow path 52c, the uppermost and lowermost flat heat transfer tubes 3 are not shifted, and the other six Only the flat heat transfer tube 3 is shifted to one side.
The second channel 52b and the fourth channel 52d have the same configuration. 10 shows the first header pipe 21 side, the second header pipe 22 side has the same configuration.

  As described above, by adjusting the mounting position of the flat heat transfer tube connected to the header tube, the strength of the swirl flow generated in the header tubes 21 and 22 can be adjusted. By adjusting the strength, the liquid refrigerant can be evenly distributed to the flat heat transfer tubes 3. Further, in the case where the proper refrigerant amount is partially different depending on the wind speed distribution for the plurality of flat heat transfer tubes 3 constituting the heat exchanger, the distribution amount can be optimized accordingly.

  A seventh embodiment of the present invention will be described with reference to FIG. FIG. 11 is a view showing a portion of the first header pipe in the heat exchanger of the present embodiment. FIG. 11A shows a portion of the third flow path from the lower portion to which the inlet pipe of the first header pipe is connected. The side view which shows the structure until, (B) figure is the front view.

  In the seventh embodiment, the refrigerant inlet pipe 25 connected to the first header pipe 21 is connected to the lowermost part of the first header pipe 21, and the center line X in the ventilation direction 51 of the header pipe 21 is used. Are communicated with one side (the right side in FIG. 5A). The flat heat transfer tubes 3 constituting the first flow path 52a are also arranged so as to be shifted to the same side as the inlet tube 25 with respect to the center line X.

  In the seventh embodiment, the flat heat transfer tube 3 constituting the second flow path 52b is on the left side of the center line X, and the flat heat transfer tube 3 constituting the third flow path 52c is on the center line X. It is shifted to the right.

  As described above, the flat heat transfer tube 3 is connected to the first header tube 21 while being biased to one side, and at the same time, the refrigerant inlet tube 25 is also connected to the first header tube 21 so that the refrigerant is in the same turning direction. Therefore, a swirling flow can be generated also in the header pipe at the refrigerant inlet, and the refrigerant can be flowed more evenly into the flat heat transfer pipe 3.

  In the seventh embodiment, only the first header pipe 21 side has been described, but the connection position of the flat heat transfer pipe 3 is also the flat transmission in the first header pipe 21 on the second header pipe 22 (see FIG. 1) side. The heat pipe 3 is connected to the second header pipe 22 so as to be biased with respect to the center line X so as to correspond to the bias direction of the heat pipe 3.

  As described above, according to each embodiment of the heat exchanger of the present invention, the upstream flow path that flows from one header pipe of the pair of header pipes to the other header pipe and the upper part of the flow path are provided. A downstream flow path for flowing the refrigerant flowing into the other header pipe from the other header pipe to the one header pipe is provided, and each of the upstream flow path and the downstream flow path is a plurality of flat heat transfer tubes. And at least some of the plurality of flat heat transfer tubes constituting the upstream flow path and at least some of the plurality of flat heat transfer tubes constituting the downstream flow path are connected to the other header pipe Since the positions are shifted in opposite directions with respect to the center line of the ventilation direction in the header pipe, the refrigerant flow is suppressed with a simple structure with respect to the heat exchanger using a plurality of flat heat transfer pipes. Low cost and high heat exchange performance It can be obtained exchangers.

  That is, according to the present embodiment, since a swirling flow having a large refrigerant flow rate can be generated in the first and second header pipes, the liquid refrigerant can be flowed above each header pipe, and the heat exchanger Since an appropriate amount of refrigerant can be introduced into each of the flat heat transfer tubes, an effect that can be effectively used for heat exchange over the entire range of the heat exchanger is obtained. In particular, when the heat exchanger of the present embodiment configured in a parallel flow type is employed in an evaporator of an air conditioner, a particularly great effect can be obtained.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. Further, the above-described embodiments have been described in detail for easy understanding in the present invention, and are not necessarily limited to those having all the configurations described. Furthermore, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

1: heat exchanger,
21 and 22: header pipe (21: first header pipe, 22: second header pipe),
24, 24a to 24c: partition plates,
25: inlet pipe, 26: outlet pipe,
3: flat heat transfer tube, 3a: end, 3b: finned portion,
31: Refrigerant flow path, 32: Case member, 33: Inner fin, 34: Space part,
4: fins, 41: penetration type fins, 42: plug-in type fins, 43: corrugated type fins,
51: Ventilation direction (air flow),
52: refrigerant flow, 52a: first flow path, 52b: second flow path, 52c: third flow path,
52d: the fourth flow path,
521: Swirl flow (swirl upflow), 522: Streamline,
53: Saturated region, 54: Superheated gas region.

Claims (7)

In a heat exchanger comprising a plurality of fins in contact with air, a plurality of flat heat transfer tubes connected to the fins, and at least a pair of header tubes to which both ends of the flat heat transfer tubes are connected,
An upstream channel that flows from one header pipe of the pair of header pipes to the other header pipe;
Provided with a downstream flow path for flowing the refrigerant flowing into the other header pipe provided in the upper part of the flow path from the other header pipe to the one header pipe,
The upstream flow path and the downstream flow path are each composed of a plurality of flat heat transfer tubes,
At least a part of the plurality of flat heat transfer tubes constituting the upstream flow channel and at least a part of the plurality of flat heat transfer tubes constituting the downstream flow channel are connected to the other header tube, A heat exchanger characterized in that the header pipe is configured to be shifted in opposite directions with respect to the center line in the ventilation direction.   2. The heat exchanger according to claim 1, wherein the first flow path includes a plurality of flat heat transfer tubes for flowing from the header tube connected to the refrigerant inlet side to the header tube on the other side, and the first flow channel. A second flow path constituted by a plurality of flat heat transfer tubes for allowing the refrigerant flowing from the other flow path to the header pipe on the other side to flow from the header pipe on the other side to the header pipe disposed on the opposite side. And a plurality of flat heat transfer tubes configured to flow the refrigerant flowing into the header pipe from the second flow path from the header pipe to the header pipe disposed on the opposite side of the header pipe. 3, a plurality of flat heat transfer tubes constituting an upstream flow path in a header pipe connecting the second flow path and the third flow path, and a plurality of flats constituting a downstream flow path The heat transfer tubes are connected so as to be shifted in opposite directions with respect to the center line of the header tube. Heat exchanger according to claim.   2. The heat exchanger according to claim 1, wherein the first flow path includes a plurality of flat heat transfer tubes for flowing from the header tube connected to the refrigerant inlet side to the header tube on the other side, and the first flow channel. A second flow path constituted by a plurality of flat heat transfer tubes for allowing the refrigerant flowing from the other flow path to the header pipe on the other side to flow from the header pipe on the other side to the header pipe disposed on the opposite side. And a plurality of flat heat transfer tubes configured to flow the refrigerant flowing into the header pipe from the second flow path from the header pipe to the header pipe disposed on the opposite side of the header pipe. 3 and a plurality of flat heat transfer tubes for flowing the refrigerant flowing into the header pipe from the third flow path from the header pipe to the header pipe arranged on the opposite side of the header pipe A fourth flow path, and a head connecting the third flow path and the fourth flow path. A plurality of flat heat transfer tubes constituting the upstream flow path in the pipe and a plurality of flat heat transfer pipes constituting the downstream flow path are connected to each other while being shifted in opposite directions with respect to the center line of the header pipe. A heat exchanger characterized by   4. The heat exchanger according to claim 3, wherein the fourth flow path is connected to a refrigerant outlet side via a header pipe, and a connection position between the outlet side of the fourth flow path and the header pipe. And the connection position between the inlet side of the third flow path and the header pipe is shifted in opposite directions with respect to the center line of the header pipe, and further to the third flow path in the header pipe. A heat exchanger, wherein a partition plate is provided between an inlet side and an outlet side from the fourth flow path. In the heat exchanger according to any one of claims 1 to 4, the connection position of the flat heat transfer tube constituting the upstream flow channel and the flat heat transfer tube constituting the downstream flow channel to the header tube, Instead of a configuration in which the header pipe is shifted in opposite directions with respect to the center line in the ventilation direction,
The opening direction in the header pipe of the flat heat transfer tube constituting the upstream flow path and the flat heat transfer pipe constituting the downstream flow path is opposite to the center line of the ventilation direction in the header pipe. Further, the flat heat transfer tube is subjected to a bending process in a plane direction.   The heat exchanger according to any one of claims 1 to 4, wherein a flat heat transfer tube constituting the upstream flow channel and a connection portion of the flat heat transfer tube constituting the downstream flow channel to the header tube are bent. By processing, at least some of the plurality of flat heat transfer tubes constituting the upstream flow path, and at least some of the plurality of flat heat transfer tubes constituting the downstream flow path are connected to the header pipe, A heat exchanger characterized in that the header pipe is shifted in opposite directions with respect to the center line in the ventilation direction.   The heat exchanger according to any one of claims 1 to 4, wherein the plurality of fins are formed as strip-shaped fins, and the strip-shaped fins are provided with through holes or cuts to insert the flat heat transfer tubes. A heat exchanger characterized by

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