JP6123193B2 - Refrigerant heat exchanger - Google Patents

Description

  The present invention relates to a refrigerant heat exchanger, and more particularly, to a refrigerant heat exchanger configured by brazing and joining a longitudinal end portion of a flat tube having a channel hole to a header.

Conventionally, as shown in Patent Document 1 (Japanese Patent Application Laid-Open No. 2012-93075), refrigerant heat exchange configured by brazing and joining a longitudinal end portion of a flat tube in which a channel hole is formed to a header. There is a vessel. This refrigerant heat exchanger employs a header having a laminated structure in which a plurality of members are laminated. Patent Document 1 describes a header having a laminated structure, which includes a holding member, a fixing member , a second member (spacer member), and a first member (base member). Here, the holding member is a member in which a flat holding-side flat tube insertion hole for inserting a longitudinal end portion of the flat tube is formed. The fixing member is a member in which a flat fixed side flat tube insertion hole for inserting a longitudinal end portion of the flat tube inserted into the holding member is formed. The spacer member is a member in which a flat spacer-side flat tube facing hole facing the end in the longitudinal direction of the flat tube and the fixed- side flat tube insertion hole is formed. The base member is a member provided so as to sandwich the fixing member and the spacer with the holding member.

  In the refrigerant heat exchanger having the above-described conventional laminated structure header, when brazing and joining the end portion of the flat tube in the longitudinal direction to the header, an excessive brazing material is generated, and this surplus brazing material is formed in the flat tube. It may flow into the channel hole and the channel hole may be clogged with the brazing material.

In order to suppress the inflow of the brazing material into the passage-hole, it is conceivable to adopt a clearance is secured structure between the fixed-side flat tube insertion holes of the outer periphery and the fixed member of the flat tube. However, securing such a gap leads to an increase in the cavity area in the fixing member , and therefore stress due to the pressure of the refrigerant in the header tends to concentrate on the holding member and the fixing member side. If it does so, there exists a possibility that sufficient withstand pressure strength cannot be secured. As described above, in the refrigerant heat exchanger having the laminated structure header, it is required to ensure a sufficient pressure resistance while suppressing clogging of the flow path hole due to the brazing material.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a brazing material in adopting a header having a laminated structure in a refrigerant heat exchanger configured by brazing and joining a longitudinal end portion of a flat tube in which a channel hole is formed to a header. It is to be able to ensure sufficient pressure resistance while suppressing clogging of the flow path hole due to.

Refrigerant heat exchanger according to a first aspect, the refrigerant heat exchanger constructed by brazing the longitudinal ends of the channel flat tube having holes formed in the header, the holding member and the gap secured A laminated header having a member, a spacer member, and a base member is employed. Here, the holding member is a member in which a flat holding-side flat tube insertion hole for inserting a longitudinal end portion of the flat tube is formed. The gap securing member is a member in which a flat gap securing side flat tube insertion hole for inserting a longitudinal end portion of the flat tube in a state of being inserted into the holding member is formed. The spacer member is a member in which a flat spacer-side flat tube facing hole facing the end portion in the longitudinal direction of the flat tube and the gap securing side flat tube insertion hole is formed. The base member is a member provided so as to sandwich the gap ensuring member and the spacer member with the holding member. In this refrigerant heat exchanger, when the gap securing side flat tube insertion hole is viewed along the longitudinal direction of the flat tube, a gap is secured at any portion between the outer peripheral edge of the flat tube. The gap securing side flat tube insertion hole is formed in the gap securing member. Moreover, in this refrigerant heat exchanger, the dimension in the short side direction of the gap securing side flat tube insertion hole does not have a portion that exceeds the dimension in the short side direction of the spacer side flat tube facing hole.

In this refrigerant heat exchanger, a laminated structure header having a holding member, a gap securing member, a spacer member, and a base member is employed. Then, by forming the gap securing side flat tube insertion hole in the gap securing member so that a gap is secured at any part between the outer peripheral edge of the flat tube, the cavity region in the gap securing member is increased. ing. For this reason, when brazing the edge part of the longitudinal direction of a flat tube to a header, it can suppress that an excessive brazing material flows in into a flow-path hole. In addition, the cavity region in the spacer member becomes large by making the dimension in the short side direction of the gap securing side flat tube insertion hole not to be larger than the dimension in the short side direction of the spacer side flat tube opposing hole. I am doing so. For this reason, the stress by the pressure of the refrigerant | coolant in a header is disperse | distributed also to the spacer member and the base member side, and the stress concentration to the holding member and the clearance ensuring member side is suppressed.

Thereby, here, when adopting the header of the laminated structure having the holding member, the gap securing member, the spacer member, and the base member, it is possible to ensure sufficient pressure resistance strength while suppressing clogging of the flow path hole by the brazing material. .

The refrigerant heat exchanger according to the second aspect is the refrigerant heat exchanger according to the first aspect, in which the gap securing member is connected to the end on one side in the long side direction of the gap securing side flat tube insertion hole. A wax reservoir is formed of a space in which the material can be accumulated.

In the refrigerant heat exchanger, by forming a wax reservoir into the gap securing member further as cavity region is increased in the gap securing member, so that further suppress the clogging of the flow through holes by brazing material. For this reason, the stress due to the pressure of the refrigerant in the header tends to concentrate on the holding member and the gap securing member side.

However, since the dimension in the short side direction of the spacer side flat tube facing hole is made larger than the dimension in the short side direction of the gap securing side flat tube insertion hole, the solder pool portion is formed in the gap securing member. Nevertheless, the stress concentration on the holding member and gap ensuring member side can be suppressed.

The refrigerant heat exchanger according to the third aspect is the refrigerant heat exchanger according to the second aspect, wherein when the gap securing side flat tube insertion hole is viewed along the longitudinal direction of the flat tube, the outer peripheral edge of the flat tube than the gap between the gap between one end of the long side of the gap securing side flat tube insertion hole, the end portion of the other side of the longitudinal direction of the outer peripheral edge and the gap secured side flat tube insertion holes of the flat tubes As a result of increasing the size, a solder pool portion is formed in the gap securing member.

In this refrigerant heat exchanger, the end on one side in the long side direction of the gap securing side flat tube insertion hole is caused to function as a wax reservoir.

However, since the dimension in the short side direction of the spacer side flat tube facing hole is made larger than the dimension in the short side direction of the gap securing side flat tube insertion hole, such a solder pool portion is used as the gap securing member. Despite being formed, stress concentration on the holding member and the gap ensuring member side can be suppressed.

The refrigerant heat exchanger according to the fourth aspect is the refrigerant heat exchanger according to the third aspect, wherein one end in the long side direction of the gap securing side flat tube insertion hole has a long side and a short side. It has a shape connected via the R part.

In this refrigerant heat exchanger, by the shape of the shape of the end portion of one side of the longitudinal direction of the gap securing side flat tube insertion holes and long and short sides led via the R portion, a gap secured side The clearance gap between the edge part of the one side of the long side direction of a flat tube insertion hole and the outer periphery of a flat tube can be enlarged. For this reason, the brazing material reservoir can be enlarged.

  Thereby, here, clogging of the flow path hole by the brazing material can be further suppressed.

The refrigerant heat exchanger according to the fifth aspect is the refrigerant heat exchanger according to any one of the first to fourth aspects, wherein the flat tube in the thick part facing the spacer side flat tube facing hole in the base member is provided. The thickness in the longitudinal direction is larger than the thickness in the longitudinal direction of the flat tube in the thin portion of the holding member facing the gap securing side flat tube insertion hole.

In this refrigerant heat exchanger, since the thickness in the longitudinal direction of the flat tube in the thick portion of the base member is larger than the thickness in the longitudinal direction of the flat tube in the thin portion of the holding member, the stress due to the pressure of the refrigerant in the header Is preferably received on the spacer member and base member side having the thick portion. For this reason, by making the dimension in the short side direction of the spacer side flat tube facing hole larger than the dimension in the short side direction of the gap securing side flat tube insertion hole, the stress is applied to the holding member having the thin wall portion and the gap securing member side. Without concentrating, the stress can be concentrated on the spacer member and the base member side having the thick part.

  Thereby, the stress by the pressure of the refrigerant | coolant in a header is mainly received by the spacer member with a thick part and a base member side here, and the improvement of a pressure-resistant strength can be aimed at.

  As described above, according to the present invention, the following effects can be obtained.

In the refrigerant heat exchanger according to the first aspect, when adopting a header having a laminated structure having a holding member, a gap securing member, a spacer member, and a base member, sufficient pressure strength is provided while suppressing clogging of the flow path hole due to the brazing material. Can be secured.

In the second and refrigerant heat exchanger according to a third aspect, the brazing reservoir despite being formed in the gap securing member, it is possible to suppress stress concentration to the holding member and the gap secured member.

  In the refrigerant heat exchanger according to the fourth aspect, clogging of the flow path hole due to the brazing material can be further suppressed.

  In the refrigerant heat exchanger according to the fifth aspect, stress due to the pressure of the refrigerant in the header is mainly received on the spacer member and the base member side having the thick portion, so that the pressure resistance can be improved.

It is a schematic block diagram of the refrigerant | coolant heat exchanger concerning one Embodiment of this invention. It is the perspective view which expanded the A section of the refrigerant | coolant heat exchanger of FIG. It is the arrow line view which looked at the refrigerant | coolant heat exchanger of FIG. 1 from the B direction. It is a perspective view of a foundation member. It is II sectional drawing (only left edge part vicinity) of the refrigerant | coolant heat exchanger of FIG. It is II-II sectional drawing (only the edge part vicinity of a left side) of the refrigerant | coolant heat exchanger of FIG. It is III-III sectional drawing of the refrigerant | coolant heat exchanger of FIG. It is IV-IV sectional drawing of the refrigerant | coolant heat exchanger of FIG. It is VV sectional drawing of the refrigerant | coolant heat exchanger of FIG. It is VI-VI sectional drawing of the refrigerant | coolant heat exchanger of FIG. FIG. 7 is an enlarged view of FIG. 6. It is a figure which shows the refrigerant | coolant heat exchanger of the modification 1, Comprising: It is a figure corresponding to FIG. It is a figure which shows the refrigerant | coolant heat exchanger of the modification 1, Comprising: It is a figure corresponding to FIG. It is a figure which shows the refrigerant | coolant heat exchanger of the modification 2, Comprising: It is a figure corresponding to FIG. It is a figure which shows the refrigerant | coolant heat exchanger of the modification 2, Comprising: It is a figure corresponding to FIG.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a refrigerant heat exchanger according to the present invention and modifications thereof will be described with reference to the drawings. In addition, the specific structure of the refrigerant | coolant heat exchanger concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) Whole structure of refrigerant | coolant heat exchanger FIG. 1: is a schematic block diagram of the refrigerant | coolant heat exchanger 1 concerning one Embodiment of this invention. FIG. 2 is an enlarged perspective view of part A of the refrigerant heat exchanger 1 of FIG.

  The refrigerant heat exchanger 1 is provided, for example, in an outdoor unit of a split type air conditioner. In this case, the refrigerant heat exchanger 1 functions as an outdoor heat exchanger that performs heat exchange between the air supplied by the outdoor fan provided in the outdoor unit and the refrigerant. In addition, the use of the refrigerant | coolant heat exchanger 1 is not limited to an outdoor heat exchanger, It can be used also for another use.

  The refrigerant heat exchanger 1 is a heat exchanger configured by brazing and joining the longitudinal ends 12 and 13 of the flat tube 10 formed with a plurality of flow path holes 11a to 11i to the headers 20 and 30. is there.

  Specifically, the refrigerant heat exchanger 1 is a stacked heat exchanger mainly composed of a plurality of flat tubes 10 and a plurality of heat transfer fins 40. The flat tubes 10 are arranged in a plurality of stages at intervals in the vertical direction in FIG. 1 and FIG. 2 (that is, the direction along the longitudinal direction of the headers 20 and 30). 13 is brazed to the headers 20 and 30. 1 and 2, the heat transfer fins 40 are arranged in a ventilation space sandwiched between flat tubes 10 adjacent to each other in the vertical direction. The headers 20 and 30 are cylindrical members extending in the vertical direction in FIG. 1, and have a function of supporting the flat tube 10, a function of guiding the refrigerant to the flow channel holes 11 a to 11 i of the flat tube 10, and a flow channel hole 11 a. ˜11i have a function of collecting the refrigerants coming out of 11i.

(2) Flat tube As shown in FIG. 2, the flat tube 10 is a flat multi-hole tube having a flat cross-sectional shape, and a plurality of (here, nine) channel holes 11 a to 11 i are When the end portions 12 and 13 in the longitudinal direction of the flat tube 10 are viewed along the longitudinal direction of the flat tube 10, they are aligned in the long side direction of the flat cross-sectional shape (that is, the longitudinal direction in the drawing in FIGS. 1 and 2). Is arranged in.

  The channel holes 11 a to 11 i have a circular or polygonal hole shape, and penetrate between the end portions 12 and 13 in the longitudinal direction of the flat tube 10. The flat tube 10 is formed by extruding a metal material such as aluminum or an aluminum alloy. The number of flow path holes 11a to 1i is not limited to nine, and may be more or less than nine. The flat tube 10 is a clad material. Specifically, the flat tube 10 is a member in which a brazing material is bonded to the flat surface.

(3) Heat Transfer Fin Here, the heat transfer fin 40 is formed by corrugation formed by bending a sheet metal material such as aluminum or aluminum alloy into a corrugation in the longitudinal direction, as shown in FIGS. It is a fin. The heat transfer fin 40 has a valley 41, a mountain 42, and a heat transfer surface 43. The valley portion 41 and the mountain portion 42 are in contact with the flat surface of the flat tube 10 and are brazed and joined. Here, the heat transfer surface 43 is formed with a louver-like cut-and-raised portion 44 for improving heat exchange efficiency. That is, here, a corrugated fin type laminated heat exchanger is employed as the refrigerant heat exchanger 1.

(4) Header <Overall configuration of header>
Here, as shown in FIG. 1, the header 20 is divided into two internal spaces by a partition plate 21. When the refrigerant heat exchanger 1 functions as a refrigerant radiator, the refrigerant flows into the upper space of the header 20. The refrigerant that has flowed into the upper space of the header 20 flows into the header 30 through the flow passage holes 11a to 11b of the flat tube 10 disposed above. The refrigerant flowing into the header 30 is folded back and flows into the lower space of the header 20 through the flow passage holes 11a to 11b of the flat tube 10 installed below, and then exits the refrigerant heat exchanger 1. At this time, the refrigerant is cooled by heat exchange with air as a cooling source when passing through the flow path holes 11 a to 11 i of the flat tube 10. When the refrigerant heat exchanger 1 functions as a refrigerant evaporator, the refrigerant flows into the lower space of the header 20. The refrigerant that has flowed into the lower space of the header 20 flows into the header 30 through the flow passage holes 11a to 11b of the flat tube 10 disposed below. The refrigerant flowing into the header 30 is folded back and flows into the upper space of the header 20 through the flow passage holes 11a to 11b of the flat tube 10 disposed above, and then exits the refrigerant heat exchanger 1. At this time, the refrigerant evaporates by heat exchange with air as a heating source when passing through the flow path holes 11 a to 11 i of the flat tube 10. In addition, the pass removal of the refrigerant | coolant heat exchanger 1 including the number, arrangement | positioning, etc. of a partition plate is not limited to what is shown in FIG.

  Here, as shown in FIGS. 1 and 3, the headers 20 and 30 mainly have base members 22 and 32 and connecting portions 25 and 35. The flat tube 10 is brazed to the headers 20 and 30 via the connecting portions 25 and 35. Here, FIG. 3 is an arrow view of the refrigerant heat exchanger 1 of FIG. 1 viewed from the B direction. Note that the configuration of the header 20 is basically the same as the configuration of the header 30. Therefore, in the following description, only the configuration of the header 30 will be mainly described, and regarding the configuration of the header 20, the 30th code of the header 30 is replaced with the 20th code.

<Base material>
Here, as shown in FIGS. 3 and 4, the base member 32 is made of a metal material such as aluminum or an aluminum alloy, and mainly includes a cylindrical portion 33 and a communication hole forming portion 34. Here, FIG. 4 is a perspective view of the base member 32.

  The cylindrical portion 33 is an elongated and substantially cylindrical portion in which the main flow path 33a is formed. The main flow path 33 a is a refrigerant flow path formed inside the base member 32. The main flow path 33 a is a hole having a circular cross-sectional shape as viewed from the direction along the longitudinal direction of the cylindrical portion 33. The main flow path 33 a extends along the longitudinal direction of the header 30. The main flow path 33a communicates with a plurality of communication holes 34a formed in the communication hole forming part 34.

  The communication hole forming portion 34 is a substantially rectangular portion that is integrally connected to the side wall of the cylindrical portion 33. In addition, the communication hole forming portion 34 extends along the longitudinal direction of the header 30. In the communication hole forming portion 34, a plurality of (here, six) communication holes 34a are formed. The communication hole 34 a is formed side by side in the longitudinal direction of the communication hole forming part 34. The communication hole 34 a is disposed so as to face the end portion 13 of the flat tube 10 with the same arrangement interval as that of the flat tube 10. Here, the communication hole 34a is a substantially circular hole. Then, when the header 30 and the flat tube 10 are joined, the connecting portion 35 is joined to the communication hole forming portion 34.

<Connecting part>
Here, as shown in FIGS. 3, 5, and 6, the connecting portion 35 is an assembly of members that connect the header body 30 and the multi-hole tube 10. Here, FIG. 5 is a cross-sectional view taken along the line II of the refrigerant heat exchanger 1 of FIG. 1 (only in the vicinity of the left end). 6 is a cross-sectional view of the refrigerant heat exchanger 1 in FIG. 3 taken along the line II-II (only in the vicinity of the left end).

The connecting portion 35 mainly includes a spacer member 36, a gap ensuring member 37, and a holding member 38. The spacer member 36 is disposed so as to be in contact with the surface on the end 13 side of the flat tube 10 of the communication hole forming portion 34 (that is, the surface far from the cylindrical portion 33). The clearance securing member 37 is disposed so as to contact a surface on the end 13 side of the flat tube 10 of the spacer member 36 (that is, a surface far from the cylindrical portion 33). The holding member 38 is disposed so as to surround the communication hole forming portion 34, the spacer member 36, and the gap securing member 37 from the side far from the cylindrical portion 33. That is, the spacer member 36, the gap ensuring member 37, and the holding member 38 that form the connecting portion 35 are sequentially arranged from the base member 32 side.

  As shown in FIGS. 3 and 5 to 8, the spacer member 36 is an elongated, substantially rectangular member that extends in the longitudinal direction of the header 30. Here, FIG. 7 is a III-III sectional view of the refrigerant heat exchanger 1 of FIG. 8 is a IV-IV cross-sectional view of the refrigerant heat exchanger 1 of FIG. The spacer member 36 is formed with a plurality (here, 6) of counter holes 36a (spacer side flat tube counter holes). The counter holes 36 a are formed side by side in the longitudinal direction of the spacer member 36. The facing hole 36 a is disposed so as to face the communication hole 34 a and the end portion 13 of the flat tube 10 with the same arrangement interval as the communication hole 34 a and the flat tube 10. The counter hole 36a is a flat hole (more specifically, a substantially rectangular shape) whose cross-sectional shape seen from the direction along the longitudinal direction of the refrigerant pipe 10 communicates with all of the communication hole 34a and the flow path hole 11. Hole). That is, the counter hole 36a of the spacer member 36 is a flow path for distributing the refrigerant from the base member 32 to the flow path holes 11a to 11i of the flat tube 10 between the base member 32 and the flat tube 10, or A flow path for joining the refrigerant from the flow path holes 11a to 11i of the flat tube 10 is formed. Further, the dimension Ls in the long side direction of the facing hole 36a is smaller than the dimension Lt in the long side direction of the flat cross-sectional shape of the flat tube 10. For this reason, the spacer member 36 has an end portion 36b on the outer peripheral side in the long side direction of the facing hole 36a when the end portion 13 of the flat tube 10 is viewed along the longitudinal direction of the refrigerant tube 10. It arrange | positions so that a part (here end surface 13b of a long side direction) of the edge part 13 may be contacted. That is, the end portion 36 b of the spacer member 36 is in contact with the end portion 13 in the longitudinal direction of the flat tube 13 when the end portion 13 of the flat tube 13 is inserted into the header 30. The insertion depth of the portion 13 into the header 30 is limited. The spacer member 36 is a clad material. Specifically, the spacer member 36 is a member in which a metal material such as aluminum or aluminum alloy, which is the same as the base member 32 and the flat tube 10, is used as a core material, and a brazing material is bonded to the surface of the core material. The spacer member 36 is brazed and joined to the communication hole forming portion 34 of the base member 32 and the longitudinal end portion 13 of the flat tube 10.

As shown in FIGS. 3 and 5 to 9, the gap securing member 37 is an elongated, substantially rectangular member that extends in the longitudinal direction of the header 30. Here, FIG. 9 is a VV cross-sectional view of the refrigerant heat exchanger 1 of FIG. The clearance securing member 37 is formed with a plurality of (here, 6) insertion holes 37a (a clearance securing side flat tube insertion hole). The insertion holes 37 a are formed side by side in the longitudinal direction of the gap ensuring member 37. The insertion hole 37a is arranged to face the communication hole 34a and the counter hole 36a at the same arrangement interval as the communication hole 34a, the counter hole 36a, and the flat tube 10. And the insertion hole 37a is a flat hole (more specifically, the cross-sectional shape seen from the direction along the longitudinal direction of the flat tube 10 can insert the end 13 in the longitudinal direction of the flat tube 10 (more specifically, Substantially oblong holes). For this reason, the clearance securing member 37 supports the end portion 13 in the longitudinal direction of the flat tube 10 in a state of being inserted into the insertion hole 37a. The clearance securing member 37 is made of the same metal material as the base member 32 and the flat tube 10 such as aluminum or aluminum alloy. The gap securing member 37 is brazed to the spacer member 36 and the longitudinal end portion 13 of the flat tube 10 in a state where the longitudinal end portion 13 of the flat tube 10 is supported.

As shown in FIGS. 3 and 5 to 10, the holding member 38 is an elongated and substantially rectangular member extending in the longitudinal direction of the header 30. Here, FIG. 10 is a VI-VI sectional view of the refrigerant heat exchanger 1 of FIG. The holding member 38 has a substantially U shape when viewed along the longitudinal direction of the header 30. The holding member 38 is formed with a plurality of (here, six) insertion holes 38a (holding side flat tube insertion holes). The insertion hole 38 a is formed side by side in the longitudinal direction of the holding member 38. The insertion hole 38a is arranged to face the communication hole 34a, the counter hole 36a, and the insertion hole 37a with the same arrangement interval as that of the communication hole 34a, the counter hole 36a, the insertion hole 37a, and the flat tube 10. The insertion hole 38 a is a flat hole whose cross-sectional shape viewed from the direction along the longitudinal direction of the flat tube 10 can be inserted into the end 13 in the longitudinal direction of the flat tube 10. For this reason, the holding member 38 supports the end portion 13 in the longitudinal direction of the flat tube 10 inserted in the insertion hole 38a in the same manner as the gap securing member 37. That is, the gap securing member 37 is supported in a state where the end 13 in the longitudinal direction of the flat tube 10 inserted in the holding member 38 is inserted. Here, the dimensions in the short side direction and the long side direction of the insertion hole 38a are substantially the same as the dimensions in the short side direction and the long side direction of the flat cross-sectional shape of the refrigerant tube 10. The holding member 38 holds the spacer member 36, the gap securing member 37, and the flat tube 10, and the tip end portion 38 b on the base member 32 side of the holding member 38 forms the communication hole of the base member 32 in this holding state. The portion 34 is fixed by caulking. That is, the base member 32 is provided so as to sandwich the gap securing member 37 and the spacer member 36 between the holding member 38 and is fixed to the holding member 38 by caulking. The holding member 38 is also a clad material similar to the spacer member 36. The holding member 38 is brazed to the gap securing member 37 and the end portion 13 in the longitudinal direction of the flat tube 10.

As described above, here, as the headers 20 and 30, a laminated structure including the holding members 28 and 38, the gap securing members 27 and 37, the spacer members 26 and 36, and the foundation members 22 and 32 is employed.

  And in the refrigerant | coolant heat exchanger 1 which has such a header 20 and 30, although the structure for ensuring sufficient proof pressure strength is suppressed, suppressing clogging of the flow-path holes 11a-11i by a brazing material, This structure will be described later.

(5) Brazing joining in a case where there is no structure for suppressing clogging of the flow path holes by the brazing material (ie, clogging of the flow path holes 11a to 11i by the brazing material described later) In a configuration in which a structure for ensuring sufficient pressure strength while suppressing is not formed), brazing is performed in the following procedure.

  The brazing of the refrigerant heat exchanger 1 is performed by assembling the end portions 12 and 13 of the flat tube 10 at predetermined positions of the headers 20 and 30 and the heat transfer assembly before brazing and joining the heat transfer fins 40 between the flat tubes 10. Is placed in a brazing furnace and heated. At this time, the heat exchanger assembly is arranged in the furnace in a posture in which the long side of the flat cross-sectional shape of the flat tube 10 faces the vertical direction (see FIG. 2).

Then, the brazing material bonded to the spacer member 36 and the holding member 38 is melted, and the longitudinal ends 12 and 13 of the flat tube 10 are joined to predetermined positions of the headers 20 and 30 by the melted brazing material. Here, the header 20 is configured by brazing and joining the communicating hole forming portion 24 of the base member 22, the spacer member 26, the gap ensuring member 27, and the holding member 28. In addition, the header 30 is configured by brazing and joining the communication hole forming portion 34, the spacer member 36, the gap securing member 37, and the holding member 38 of the base member 32. The headers 20 and 30 are configured, and the longitudinal ends 12 and 13 of the refrigerant pipe 10 are brazed to the headers 20 and 30.

  However, in such brazing joining, surplus brazing material is generated, and this surplus brazing material flows into the channel holes 11a to 11i of the flat tube 10, and the channel holes 11a to 11i due to the brazing material. There is a risk of clogging. Here, as a cause of the brazing material flowing into the flow passage holes 11a to 11i of the flat tube 10 at the time of brazing joining, the capillary force of the flow passage holes 11a to 11i and the like can be cited. That is, surplus brazing material generated during brazing joining flows from the outer peripheral portion of the flat tube 10 to the channel holes 11a to 11i due to the capillary force of the channel holes 11a to 11i. It is to be drawn. Moreover, the influence of the attitude | position of the flat tube 10 at the time of brazing joining is mentioned as a cause in which the brazing material flows into the flow-path holes 11a-11i of the flat tube 10 at the time of brazing joining. That is, at the time of brazing joining, if the long side of the flat cross-sectional shape of the flat tube 10 is disposed in the furnace in a posture in which the flat tube 10 is directed in the vertical direction, surplus brazing material generated at the time of brazing joining It tends to accumulate at the lower end in the long side direction (for example, the end 13b in the long side direction having a flat cross-sectional shape). The surplus brazing material collected at the lower end in the long side direction of the flat tube 10 is likely to flow into a flow path hole (for example, the flow path hole 11i) disposed near the lower end portion in the long side direction of the flat tube 10. .

  As described above, the refrigerant heat exchanger 1 has a technical problem of clogging the flow path holes 11a to 11i due to the brazing material. On the other hand, the refrigerant heat exchanger 1 uses the brazing material as will be described later. A structure for suppressing clogging of the flow path holes 11a to 11i is provided.

(6) Structure for suppressing clogging of flow path hole by brazing material In the refrigerant heat exchanger 1, in order to suppress clogging of the flow path hole by the brazing materials 11a to 11i as described above, first, the flat tube 10 It is preferable to employ a structure in which a gap is secured between the outer peripheral edge and the insertion holes 27a and 37a ( gap securing side flat tube insertion holes) of the gap securing members 27 and 37.

Therefore, here, as shown in FIGS. 5, 6, 9, and 11, when the insertion hole 37 a is viewed along the longitudinal direction of the flat tube 10 in the header 30, An insertion hole 37a is formed in the gap securing member 37 so that a gap is secured at any part between the gaps . Here, FIG. 11 is an enlarged view of FIG. Specifically, the dimension Lf in the long side direction of the insertion hole 37a is made larger than the dimension Lt in the long side direction of the flat tube 10, and the dimension Wf in the short side direction of the insertion hole 37a is set to the short side of the flat tube 10. It is made larger than the direction dimension Wt. Here, a space formed in the gap securing member 37 by securing a gap between the outer peripheral edge of the flat tube 10 and the insertion hole 37 a is defined as a cavity region Sf in the gap securing member 37. Although not shown here, in the header 20 as well as in the header 30, the insertion hole 27a is formed in the gap securing member 27 so that a gap is secured at any part between the outer peripheral edge of the flat tube 10. However, the cavity region Sf is formed by securing this gap.

And if a clearance gap is ensured between the outer periphery of such a flat tube 10, and insertion hole 27a, 37a, since the cavity area | region Sf in the clearance ensuring members 27 and 37 will become large, the excess brazing which generate | occur | produced at the time of brazing joining will be carried out. Capillary force or the like of the channel holes 11a to 11i is less likely to act on the material. As a result, surplus brazing material generated at the time of brazing is less likely to be drawn into the channel holes 11a to 11i from the outer peripheral side portions of the flat tube 10 than the channel holes 11a to 11i. The clogging of 11a to 11i can be suppressed.

In addition, here, not only the gap is secured between the outer peripheral edge of the flat tube 10 and the insertion holes 27a and 37a, but also the brazing material 37 is attached to the gap securing member 37 in the header 30 as shown in FIGS. A wax reservoir portion 37b made of a space capable of accumulating water is provided. Here, the wax reservoir portion 37b is formed at one end portion in the long side direction of the insertion hole 37a (here, the end portion close to the flow path hole 11i). Specifically, when the insertion hole 37a is viewed along the longitudinal direction of the flat tube 10, the outer peripheral edge of the flat tube 10 and the end portion on one side in the long side direction of the insertion hole 37a (here, the flow channel hole The gap between the outer peripheral edge of the flat tube 10 and the other end in the long side direction of the insertion hole 37a (here, the end near the flow path hole 11a) is larger. As a result, a solder pool portion 37 b is formed in the clearance securing member 37. That is, here, one end portion in the long side direction of the insertion hole 37a (here, the end portion near the flow path hole 11i) functions as the wax reservoir portion 37b. Although not shown here, also in the header 20, as with the header 30, a solder pool portion 27 b is formed in the gap securing member 27.

When such brazing reservoir portions 27b and 37b are formed, the cavity region Sf in the gap securing members 27 and 37 is further increased, so that excess brazing material generated during brazing and joining is accumulated in the brazing reservoir portions 27b and 37b. Will be able to. Thereby, the excess brazing material collected at the lower end in the long side direction of the flat tube 10 flows into the flow path hole (here, the flow path hole 11 i) arranged near the lower end portion in the long side direction of the flat tube 10. Therefore, clogging of the flow path holes 11a to 11i due to the brazing material can be suppressed.

However, by ensuring the clearance between the outer peripheral edge of the flat tube 10 and the insertion holes 27a and 37a of the clearance securing members 27 and 37 as described above, and by forming the wax accumulation portions 27b and 37b on the clearance securing members 27 and 37, respectively. When the cavity region Sf in the gap securing members 27 and 37 is increased, the stress due to the refrigerant pressure in the headers 20 and 30 tends to concentrate on the holding members 28 and 38 and the gap securing members 27 and 37 side. If it does so, there exists a possibility that sufficient withstand pressure strength cannot be secured.

  Thus, in the refrigerant heat exchanger 1, a technical problem of a decrease in pressure resistance due to the adoption of a structure for solving the technical problem of clogging of the flow passage holes 11a to 11i due to the brazing material as described above. On the other hand, the refrigerant heat exchanger 1 is provided with a structure for ensuring sufficient pressure resistance as will be described later.

(7) Structure for ensuring sufficient pressure strength In the refrigerant heat exchanger 1, in order to suppress a decrease in pressure strength due to the adoption of a structure that suppresses clogging of the flow path hole due to the brazing material as described above, It is preferable to provide a structure that suppresses stress concentration toward the holding members 28 and 38 and the gap securing members 27 and 37.

Therefore, here, as shown in FIGS. 8, 9, and 11, in the header 30, the dimension Ws in the short side direction of the opposed hole 36 a (spacer side flat tube opposed hole) of the spacer member 36 is set to the gap securing member 37. The insertion hole 37a ( gap securing side flat tube insertion hole) is made larger than the dimension Wf in the short side direction. Here, a space formed in the spacer member 36 by the facing hole 36 a is defined as a cavity region Ss in the spacer member 36. Although not shown here, in the header 20 as well as the header 30, the dimension Ws in the short side direction of the opposed hole 26a of the spacer member 26 is set to the dimension Wf in the short side direction of the insertion hole 27a of the clearance securing member 27. Try to make it bigger.

When the relationship between the dimension Ws in the short side direction of the opposing holes 26a and 36a and the dimension Wf in the short side direction of the insertion holes 27a and 37a is adopted, the cavity region Ss in the spacer members 26 and 36 is increased. For this reason, the stress due to the pressure of the refrigerant in the headers 20 and 30 is distributed also to the spacer members 26 and 36 and the base members 22 and 32 (here, the communication hole forming portions 24 and 34), and the holding members 28 and 38 And the stress concentration to the gap ensuring members 27 and 37 side is suppressed. In particular, where a row reservoir 27b, 37b despite being formed in the gap securing member 27, 37, stress concentration to the holding member 28, 38 and the gap secured member 27, 37 side is suppressed . Thereby, here, when adopting the headers 20 and 30 of the laminated structure having the holding members 28 and 38, the gap securing members 27 and 37, the spacer members 26 and 36, and the base members 22 and 32, the flow passage holes made of the brazing material are used. It is possible to ensure a sufficient pressure strength while suppressing clogging of 11a to 11i.

In addition, here, the thickness tb in the longitudinal direction of the flat tube 10 in the communication hole forming portions 24 and 34 (thick portions) facing the facing holes 26a and 36a among the base members 22 and 32 is set as the holding members 28 and 38. Among these, it is larger than the thickness ta in the longitudinal direction of the flat tube 10 at the portion (thin wall portion) facing the insertion holes 27a, 37a. For this reason, it is preferable to receive the stress by the pressure of the refrigerant | coolant in the headers 20 and 30 by the spacer members 26 and 36 and the base members 22 and 32 side which have a thick part (namely, communication hole formation parts 24 and 34). For this reason, as described above, by making the dimension Ws in the short side direction of the opposing holes 26a, 36a larger than the dimension Wf in the short side direction of the insertion holes 27a, 37a, the stress is reduced to the holding member 28 having the thin wall part, The stress can be concentrated on the spacer members 26 and 36 and the base members 22 and 32 having thick portions without concentrating them on the side 38 and the gap securing members 27 and 37.

  Thereby, the stress by the pressure of the refrigerant | coolant in the headers 20 and 30 is mainly received in the spacer members 26 and 36 and the base members 22 and 32 side with a thick part here, and the pressure-resistant strength can be improved. .

(8) Modification 1
In the above embodiment, as shown in FIG. 9, the insertion holes 27a and 37a ( gap securing side flat tube insertion holes) formed in the clearance securing members 27 and 37 are substantially elliptical holes, and their long sides Both end portions in the direction have a semicircular shape, but the present invention is not limited to this.

  For example, as shown in FIG. 12, in the header 30, the long side and the short side of one end in the long side direction of the insertion hole 37 a (here, close to the flow path hole 11 i) are interposed via the R portion 37 c. It may be a connected shape. Moreover, as shown in FIG. 13, in the header 30, you may make the both ends of the long side direction of the insertion hole 37a into the shape where the long side and the short side were connected via the R part 37c. Although not shown here, the header 20 also has an end portion or both end portions on one side of the insertion hole 37a in the long side direction (here, close to the flow path hole 11i), and the long side and the short side are the R portion 27c. You may make it the shape connected via.

  Also in this modification, the same effect as said embodiment can be acquired. Moreover, in this modification, the gap between the end of one side of the insertion holes 27a and 37a in the long side direction (here, close to the flow path hole 11i) and the outer peripheral edge of the flat tube 10 can be increased. it can. For this reason, the brazing material reservoirs 27b and 37b can be enlarged. Thereby, here, clogging of the channel holes 11a to 11i due to the brazing material can be further suppressed.

(9) Modification 2
In the above embodiment and the first modification, as shown in FIGS. 1 to 13, a so-called single header in which the end portions 12, 13 in the longitudinal direction of the flat tube 10 are inserted in each stage of the headers 20, 30. Although the present invention is applied to the configuration, the present invention is not limited to this.

For example, as shown in FIGS. 14 and 15, the present invention is applied to a so-called return header configuration in which two end portions 13 in the longitudinal direction of the flat tube 10 are inserted in each stage of the header 30. Good. In the header 30 of this modification, two insertion holes 38 a (holding side flat tube insertion holes) are formed in each stage of the holding member 38. Further, two insertion holes 37 a ( gap securing side flat tube insertion holes) are formed in each step of the clearance securing member 37. A wax reservoir 37b is formed in one of the two insertion holes 37a. Each step of the spacer member 36 is formed with a counter hole 36 a (spacer side flat tube counter hole) communicating with both of the two flat tubes 10. Thereby, the two flat tubes 10 are connected in series. The base member 32 is a substantially rectangular member. In such a header 30 as well, the structure in which a gap is secured between the outer peripheral edge of the flat tube 10 and the insertion hole 37a of the gap securing member 37, as in the above embodiment and the first modification, and the gap A structure in which the securing member 37 is provided with a wax reservoir portion 37b is employed. Further, a structure is adopted in which the dimension Ws in the short side direction of the opposed hole 36a of the spacer member 36 is larger than the dimension Wf in the short side direction of the insertion hole 27a of the gap ensuring member 27. Further, the thickness tb in the longitudinal direction of the flat tube 10 in the portion (thick portion) facing the facing hole 36a in the base member 32 is used as the flat tube in the portion (thin portion) facing the insertion hole 37a in the holding member 38. A structure having a wall thickness ta larger than 10 in the longitudinal direction is employed. Although not shown here, when the configuration of the return header is adopted for the header 20, it can be configured similarly to the header 30.

  Also in this modification, the same effect as said embodiment and the modification 1 can be acquired.

  The present invention is widely applicable to a refrigerant heat exchanger configured by brazing and joining a longitudinal end portion of a flat tube in which a flow path hole is formed to a header.

DESCRIPTION OF SYMBOLS 1 Refrigerant heat exchanger 10 Flat tube 11a-11i Flow path hole 12, 13 End part 20, 30 Header 22, 32 Base member 26, 36 Spacer member 26a, 36a Opposite hole (spacer side flat tube counter hole)
27, 37 clearance securing member 27a, 37a insertion hole ( gap securing side flat tube insertion hole)
27b, 37b Wax reservoir portion 27c, 37c R portion 28, 38 Holding member 28a, 38a Insertion hole (holding side flat tube insertion hole)

JP 2012-93075 A

Claims (5)

In the refrigerant heat exchanger configured by brazing and joining the longitudinal ends (12, 13) of the flat tube (10) in which the flow path holes (11a to 11i) are formed to the headers (20, 30). ,
The header was inserted into the holding member (28, 38) formed with flat holding-side flat tube insertion holes (28a, 38a) into which the end portion of the flat tube in the longitudinal direction was inserted. A gap securing member (27, 37) formed with a flat gap securing side flat tube insertion hole (27a, 37a) for inserting an end portion in the longitudinal direction of the flat tube in a state, and a longitudinal direction of the flat tube The gap between the holding member and a spacer member (26, 36) in which a flat spacer-side flat tube facing hole (26a, 36a) facing the end portion and the gap securing side flat tube insertion hole is formed. And a base member (22, 32) provided so as to sandwich the securing member and the spacer member,
When the gap securing side flat tube insertion hole is viewed along the longitudinal direction of the flat tube, the gap securing side flattening is ensured so that a gap is secured in any part between the outer peripheral edge of the flat tube. A tube insertion hole is formed in the gap ensuring member;
The dimension (Wf) in the short side direction of the gap securing side flat tube insertion hole does not have a portion that is equal to or larger than the dimension (Ws) in the short side direction of the spacer side flat tube opposing hole.
Refrigerant heat exchanger (1). The gap securing member (27, 37) has a brazing pool consisting of a space in which brazing material can be accumulated at one end in the long side direction of the gap securing side flat tube insertion hole (27a, 37a). Parts (27b, 37b) are formed,
The refrigerant heat exchanger (1) according to claim 1. When the gap securing side flat tube insertion hole (27a, 37a) is viewed along the longitudinal direction of the flat tube (10), the outer peripheral edge of the flat tube and the long side direction of the gap securing side flat tube insertion hole The gap ensuring member is made larger by making a gap between one end of the flat tube and an outer peripheral edge of the flat tube and an end on the other side in the long side direction of the gap securing flat tube insertion hole. (27, 37) is formed with the wax reservoir (27b, 37b),
The refrigerant heat exchanger (1) according to claim 2. One end portion in the long side direction of the gap securing side flat tube insertion hole (27a, 37a) has a shape in which the long side and the short side are connected via the R portion (27c, 37c). ,
The refrigerant heat exchanger (1) according to claim 3. The thickness (tb) in the longitudinal direction of the flat tube (10) in the thick wall portion facing the spacer-side flat tube facing hole (26a, 36a) of the foundation member (22, 32) is the holding member ( 28, 38) larger than the thickness (ta) in the longitudinal direction of the flat tube in the thin portion facing the gap securing side flat tube insertion hole (27a, 37a),
The refrigerant | coolant heat exchanger (1) of any one of Claims 1-4.

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