JP2013249993A - Refrigerant heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent brazing material from flowing into a flow path hole, in a refrigerant heat exchanger in which longitudinal end parts of a multi-hole pipe with a plurality of flow path holes are brazed to headers.SOLUTION: A refrigerant heat exchanger (1) is configured by brazing longitudinal end parts (12 and 13) of a multi-hole pipe (10) with a plurality of flow path holes (11a-11i) to headers (20 and 30). In the multi-hole pipe (10), brazing material reservoir holes (14a an 14b) having an opening cross section smaller than those of the flow path holes (11a-11i) are formed at a portion on the outer peripheral side than the plurality of flow paths (11a-11i) when the longitudinal end parts (12 and 13) of the multi-hole pipe (10) are seen along the longitudinal direction of the multi-hole pipe (10).

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 multi-hole tube in which a plurality of flow passage holes are formed to a header.

  Conventionally, as shown in Patent Document 1 (Japanese Patent Application Laid-Open No. 2006-284133), the refrigerant heat formed by joining the end portions in the longitudinal direction of a multi-hole tube in which a plurality of channel holes are formed to a header. There is an exchanger.

  In the conventional refrigerant heat exchanger, the end of the multi-hole tube in the longitudinal direction is brazed to the header. Specifically, when the heat exchanger assembly in which the longitudinal ends of the multi-hole tube are assembled at predetermined positions of the header is heated in the brazing furnace, the brazing material is melted, and the molten brazing material The longitudinal end of the tube is joined to a predetermined position on the header.

  However, in such a brazing joint, since the flow of the molten brazing material cannot be controlled, the brazing material may flow into the channel hole of the multi-hole tube, and the channel hole may be clogged. There is.

  An object of the present invention is to provide a refrigerant heat exchanger configured by brazing and joining a longitudinal end portion of a multi-hole pipe in which a plurality of flow path holes are formed to a header. It is to suppress inflow.

  The refrigerant heat exchanger according to the first aspect is configured by brazing and joining a longitudinal end portion of a multi-hole tube having a plurality of flow path holes to a header. And when the multi-hole pipe is viewed along the longitudinal direction of the multi-hole pipe along the longitudinal direction of the multi-hole pipe, the opening of the flow-path hole is formed on the outer peripheral side of the plurality of flow-path holes. A brazing hole having an opening cross-sectional area smaller than the cross-sectional area is formed.

  In a refrigerant heat exchanger configured by brazing and joining a longitudinal end portion of a multi-hole pipe in which a plurality of flow path holes are formed to a header, the brazing material is a flow path hole of the multi-hole pipe at the time of brazing and joining. As a cause of inflow, the capillary force of the channel hole can be mentioned. That is, the brazing material melted at the time of brazing and joining is drawn into the channel hole from the outer peripheral portion of the multi-hole tube by the capillary force of the channel hole. In order to suppress the pulling-in of the brazing material into the channel hole due to such capillary force, it is preferable to provide a structure capable of pulling in the brazing material with a force larger than the capillary force of the channel hole.

  Therefore, here, in the multi-hole tube, when the longitudinal end portion of the multi-hole tube is viewed along the longitudinal direction of the multi-hole tube, the channel hole A brazing hole having an opening cross-sectional area smaller than the opening cross-sectional area is formed. For this reason, the brazing material melted at the time of brazing is preferentially drawn into the brazing hole having a capillary force larger than the capillary force of the flow path hole in the outer peripheral portion of the multi-hole pipe. It becomes like this.

  Thereby, inflow of the brazing material into the channel hole can be suppressed here, and the occurrence of clogging of the channel hole can be suppressed.

  A refrigerant heat exchanger according to a second aspect is the refrigerant heat exchanger according to the first aspect, wherein the multi-hole tube is a flat multi-hole tube having a flat cross-sectional shape, and a plurality of flow path holes are provided with a plurality of flow path holes. When the end portion in the longitudinal direction of the hole tube is viewed along the longitudinal direction of the multi-hole tube, they are arranged side by side in the long side direction of the flat cross-sectional shape. And the solder pool hole is formed in the edge part of the long side direction of the flat cross-sectional shape, when the edge part of the longitudinal direction of a multi-hole pipe is seen along the longitudinal direction of a multi-hole pipe.

  The cause of the brazing material flowing into the flow hole of the multi-hole pipe during brazing is that when the multi-hole pipe is a flat multi-hole pipe, not only the capillary force of the flow hole but also the brazing joint The influence of the posture of the multi-hole tube is also mentioned. That is, at the time of brazing joining, the multi-hole tube composed of a flat multi-hole tube is placed in the furnace with the long side of the flat cross-sectional shape facing the vertical direction, but in this case, it melted at the time of brazing joining The brazing material tends to accumulate at the lower end in the long side direction of the multi-hole tube. And the brazing | wax material collected at the lower end of the long side direction of a multi-hole pipe | tube tends to flow into the flow-path hole arrange | positioned near the lower end part of the long side direction of a multi-hole pipe | tube.

  Therefore, here, the length of the flat cross-sectional shape of the multi-hole tube made of a flat multi-hole tube when the longitudinal end of the multi-hole tube is viewed along the longitudinal direction of the multi-hole tube. It is formed at the end in the side direction. For this reason, the brazing hole is disposed near the end in the long side direction of the multi-hole tube at the time of brazing joining, and the brazing material accumulated at the lower end in the long side direction of the multi-hole tube It preferentially flows into the wax reservoir hole instead of the hole.

  Thereby, the influence of the attitude | position of the multi-hole pipe at the time of brazing joining is also considered here, and the inflow of the brazing material to a flow-path hole can be suppressed.

  The refrigerant heat exchanger according to the third aspect is the refrigerant heat exchanger according to the first or second aspect, wherein a guide groove extending along the longitudinal direction of the multi-hole tube is formed on the inner surface of the wax reservoir hole. ing.

  In order to enhance the pulling action of the brazing material into the brazing hole, it is preferable to sufficiently increase the capillary force of the brazing hole.

  Therefore, here, a guide groove extending along the longitudinal direction of the multi-hole tube is formed on the inner surface of the brazing hole.

  Thereby, here, the capillary force of the brazing hole can be further increased, and the brazing material melted at the time of brazing can be more preferentially drawn into the brazing hole.

  A refrigerant heat exchanger according to a fourth aspect is the refrigerant heat exchanger according to any one of the first to third aspects, wherein the multi-hole pipe has a low-temperature reservoir on a surface close to a portion where the low-temperature reservoir hole is opened. A guide surface having a larger surface roughness than a surface far from the portion where the hole is opened is formed.

  In order to enhance the pulling action of the brazing material into the brazing hole, it is preferable that the brazing material melted at the time of brazing is easily held on the surface close to the portion where the brazing hole is opened.

  Therefore, here, a guide surface having a larger surface roughness than a surface far from the portion where the solder reservoir hole is opened is formed on the surface near the portion where the solder reservoir hole is opened. For this reason, the brazing material melted at the time of brazing joining becomes easy to get wet on the surface near the portion where the brazing hole is opened, and hardly gets wet on the surface far from the portion where the brazing hole is opened.

  As a result, the brazing material melted at the time of brazing can be easily held on the surface near the portion where the brazing hole is opened, and the brazing material melted at the time of brazing is prioritized over the brazing hole. Can be pulled in.

  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 multi-hole tube is formed by extrusion molding of a metal material. And the solder pool hole is formed with the several flow-path hole at the time of extrusion molding of a multi-hole pipe | tube.

  Thereby, here, the brazing hole can be easily formed in the multi-hole tube.

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

  In the refrigerant heat exchanger according to the first aspect, the inflow of the brazing material into the flow path hole can be suppressed, and the occurrence of clogging of the flow path hole can be suppressed.

  In the refrigerant heat exchanger according to the second aspect, it is possible to suppress the inflow of the brazing material into the flow path hole in consideration of the influence of the attitude of the multi-hole tube at the time of brazing joining.

  In the refrigerant heat exchanger according to the third aspect, the capillary force of the brazing hole can be further increased, and the brazing material melted at the time of brazing can be more preferentially drawn into the brazing hole.

  In the refrigerant heat exchanger according to the fourth aspect, the brazing material melted at the time of brazing joining can be easily held on the surface close to the portion where the brazing hole is opened. It is possible to draw more preferentially into the wax pool hole.

  In the refrigerant heat exchanger according to the fifth aspect, the wax reservoir hole can be easily formed in the multi-hole tube.

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 header body. 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 left edge part vicinity) 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. 6 is an enlarged view of FIG. 5 illustrating the flow of the brazing material during brazing joining. It is a figure explaining the flow of the brazing material at the time of brazing joining in the case where the opening cross-sectional area of the brazing hole is larger than the opening cross-sectional area of the flow path hole. It is a figure which shows the multi-hole pipe concerning the modification 1, Comprising: The figure which looked at the edge part of the longitudinal direction of a multi-hole pipe along the longitudinal direction of a multi-hole pipe, and the enlarged view of a wax reservoir hole. It is a figure which shows the multi-hole pipe concerning the modification 2, Comprising: (a) The figure which looked at the edge part of the longitudinal direction of a multi-hole pipe along the longitudinal direction of a multi-hole pipe, and (b) It is the figure which looked at the edge part of the longitudinal direction along the short side direction of a multi-hole pipe. It is a figure which shows the refrigerant | coolant heat exchanger concerning the modification 3, Comprising: It is the longitudinal cross-sectional view which expanded the A section of the refrigerant | coolant heat exchanger of 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 configured by brazing and joining the longitudinal ends 12 and 13 of the multi-hole tube 10 formed with a plurality of flow passage holes 11a to 11i to the headers 20 and 30. It is.

  Specifically, the refrigerant heat exchanger 1 is a stacked heat exchanger mainly composed of a plurality of multi-hole tubes 10 and a plurality of heat transfer fins 40. The multi-hole tube 10 is 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). 12 and 13 are brazed to the headers 20 and 30. 1 and 2, the heat transfer fins 40 are arranged in a ventilation space sandwiched between vertically adjacent multi-hole tubes 10. The headers 20 and 30 are cylindrical members extending in the vertical direction in FIG. 1, the function of supporting the multi-hole pipe 10, the function of guiding the refrigerant to the flow-path holes 11 a to 11 i of the multi-hole pipe 10, and the flow path It has a function of collecting the refrigerant that has come out of the holes 11a to 11i.

(2) Multi-hole tube The multi-hole tube 10 here is a flat multi-hole tube having a flat cross-sectional shape as shown in FIG. 2, and a plurality of (here, nine) channel holes 11 a to 11 i. However, when the end portions 12 and 13 in the longitudinal direction of the multi-hole tube 10 are viewed along the longitudinal direction of the multi-hole tube 10, the long side direction of the flat cross-sectional shape (that is, the front and back of the paper surface in FIGS. 1 and 2) Are arranged side by side.

  The flow path holes 11a to 11i have a circular hole shape having an inner diameter of about 0.5 mm to 2 mm or a polygonal hole shape having an equivalent cross-sectional area. 13 is penetrated. The multi-hole 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 multi-hole tube 10 is formed with a structure for suppressing the inflow of the brazing material into the flow path holes 11a to 11i. This structure will be described later.

(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 multi-hole tube 10 and are brazed. 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 multi-hole pipe 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 channel holes 11a to 11b of the multi-hole 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 multi-hole 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 path holes 11a to 11b of the multi-hole pipe 10 disposed below. The refrigerant that has flowed into the header 30 is folded back and flows into the upper space of the header 20 through the channel holes 11a to 11b of the multi-hole tube 10 disposed above, and then the refrigerant heat exchanger 1 is connected to the multi-hole tube. 10 penetrates between the longitudinal ends 12 and 13. Get out. 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 multi-hole 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 header bodies 22 and 32 and connecting portions 25 and 35. The multi-hole tube 10 is brazed to the headers 20 and 30 via the connecting portions 22 and 32. 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 described, and for the configuration of the header 20, the 30th code of the header 30 is replaced with the 20th code.

<Header body>
Here, as shown in FIGS. 3 and 4, the header main body 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 header body 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 header body 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 described later.

  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 part 34, a plurality of 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 holes 34 a are arranged at the same arrangement interval as the multi-hole tube 10. When the header 30 and the multi-hole 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 the vicinity of the left end). 6 is a II-II cross-sectional view of the refrigerant heat exchanger 1 of FIG. 2 (only in the vicinity of the left end).

  The connecting portion 35 mainly includes a spacer 36, a tube fixing plate 37, and a joining member 38. The spacer 36 is disposed so as to contact a surface of the communication hole forming portion 34 on the end 13 side of the multi-hole tube 10 (that is, a surface far from the cylindrical portion 33). The tube fixing plate 37 is disposed so as to contact a surface of the spacer 36 on the end 13 side of the multi-hole tube 10 (that is, a surface far from the cylindrical portion 33). The joining member 38 is disposed so as to surround the communication hole forming portion 34, the spacer 36, and the tube fixing plate 37 from the side far from the cylindrical portion 33. That is, the spacer 36, the tube fixing plate 37, and the joining member 38 that constitute the connecting portion 35 are sequentially arranged from the header body 32 side.

  As shown in FIGS. 3 and 5 to 8, the spacer 36 is an elongated and substantially rectangular member extending 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 36 has a plurality of collecting holes 36a. The collective holes 36 a are formed side by side in the longitudinal direction of the spacers 36. The collective holes 36a are arranged at the same arrangement interval as the communication holes 34a and the multi-hole tube 10. The collective hole 36a is a substantially rectangular hole whose cross-sectional shape viewed from the direction along the longitudinal direction of the multi-hole tube 10 communicates with all of the communication hole 34a and the flow path holes 11a to 11i. That is, the collecting hole 36a of the spacer 36 is a flow path for distributing the refrigerant from the header main body 32 to the flow hole 11a to 11i of the multi-hole pipe 10 between the header main body 32 and the multi-hole pipe 10, or , A flow path for joining the refrigerant from the flow path holes 11a to 11i of the multi-hole tube 10 is formed. Further, the hole dimension in the long side direction of the collective hole 36a is smaller than the length dimension in the long side direction of the flat cross-sectional shape of the multi-hole tube 10. For this reason, the spacer 36 has both end portions 36b on the outer peripheral side in the long side direction of the collecting hole 36a when the end portion 13 in the longitudinal direction of the multi-hole tube 10 is viewed along the longitudinal direction of the multi-hole tube 10. It arrange | positions so that the edge part 13b of the long side direction of a flat cross-sectional shape may be contacted. Here, the hole size in the short side direction of the collecting hole 36a is larger than the length size in the short side direction of the flat cross-sectional shape of the multi-hole tube 10, but the flat cross-section of the multi-hole tube 10 It may be smaller than the length dimension in the short side direction of the shape. The spacer 36 is a clad material. Specifically, the spacer 36 is a member in which a metal material such as aluminum or aluminum alloy, which is the same as the header main body 31 and the multi-hole tube 10, is used as a core material, and a brazing material is bonded to the surface of the core material. The spacer 36 is brazed to the communication hole forming portion 34 of the header body 32 and the end portion 13 in the longitudinal direction of the multi-hole tube 10.

  As shown in FIGS. 3, 5, 6, and 9, the tube fixing plate 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 tube fixing plate 37 is formed with a plurality of insertion holes 37a. The insertion holes 37 a are formed side by side in the longitudinal direction of the tube fixing plate 37. The insertion holes 37a are arranged at the same arrangement intervals as the communication holes 34a, the collecting holes 36a, and the multi-hole tube 10. The insertion hole 37 a is a hole whose cross-sectional shape seen from the direction along the longitudinal direction of the multi-hole tube 10 can be inserted into the end 13 in the longitudinal direction of the multi-hole tube 10. For this reason, the tube fixing plate 37 supports the end portion 13 in the longitudinal direction of the multi-hole tube 10 inserted in the insertion hole 37a. The tube fixing plate 37 is made of the same metal material as the header main body 31 and the multi-hole tube 10 such as aluminum or aluminum alloy. The tube fixing plate 37 is brazed and joined to the spacer 36 and the longitudinal end portion 13 of the multi-hole tube 10 in a state where the longitudinal end portion 13 of the multi-hole tube 10 is supported.

  As shown in FIGS. 3 and 5 to 10, the joining member 38 is an elongated, substantially rectangular member that extends 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 joining member 38 has a substantially U shape when viewed along the longitudinal direction of the header 30. A plurality of insertion holes 38 a are formed in the joining member 38. The insertion hole 38 a is formed side by side in the longitudinal direction of the joining member 38. The insertion holes 38a are arranged at the same arrangement intervals as the communication holes 34a, the collecting holes 36a, the insertion holes 37a, and the multi-hole tube 10. The insertion hole 38a is a hole whose cross-sectional shape viewed from the direction along the longitudinal direction of the multi-hole tube 10 is such that the end 13 in the longitudinal direction of the multi-hole tube 10 can be inserted. Therefore, like the tube fixing plate 37, the joining member 38 supports the end portion 13 in the longitudinal direction of the multi-hole tube 10 in a state of being inserted into the insertion hole 38a. The joining member 38 holds the spacer 36, the tube fixing plate 37, and the multi-hole tube 10, and the tip end portion 38 b on the header body 32 side of the joining member 38 forms the communication hole of the header body 31 in this held state. The portion 34 is fixed by caulking. The joining member 38 is also a clad material similar to the spacer 36. The joining member 38 is brazed and joined to the tube fixing plate 37 and the end portion 13 in the longitudinal direction of the multi-hole tube 10.

(5) Flow of brazing material at the time of brazing joining Basic structure of the refrigerant heat exchanger 1 (that is, a structure for suppressing the inflow of brazing material into the channel holes 11a to 11i in the multi-hole tube 10 described later) In the configuration in which no brazing is formed, brazing is performed by the following procedure.

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

  Then, the brazing material bonded to the spacer 36 and the joining member 38 is melted, and the longitudinal end portions 12 and 13 of the multi-hole 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 communication hole forming portion 24 of the header body 21, the spacer 26, the tube fixing plate 27, and the joining member 28. In addition, the header 30 is configured by brazing and joining the communication hole forming portion 34 of the header body 31, the spacer 36, the tube fixing plate 37, and the joining member 38. The headers 20 and 30 are configured, and the end portions 12 and 13 in the longitudinal direction of the multi-hole tube 10 are brazed to the headers 20 and 30.

  However, in such brazing joining, since the flow of the molten brazing material cannot be controlled, the brazing material flows into the channel holes 11a to 11i of the multi-hole tube 10, and the channel holes 11a to 11i 11i may be clogged. Here, the cause of the brazing material flowing into the channel holes 11a to 11i of the multi-hole tube 10 at the time of brazing is the capillary force of the channel holes 11a to 11i. That is, the brazing material melted at the time of brazing and joining is drawn into the channel holes 11a to 11i from the portion on the outer peripheral side of the channel holes 11a to 11i of the multi-hole tube 10 by the capillary force of the channel holes 11a to 11i. That's what it means. For example, it is conceivable to be drawn into the channel hole 11a or the channel hole 11i from the end 13b in the long side direction of the flat cross-sectional shape. Further, the cause of the brazing material flowing into the flow hole 11a to 11i of the multi-hole tube 10 at the time of brazing and joining is the capillary of the flow hole 11a to 11i in the case of the multi-hole tube 10 made of a flat multi-hole tube. Not only the force but also the influence of the posture of the multi-hole tube 10 at the time of brazing joining can be mentioned. That is, at the time of brazing, when the multi-hole tube 10 is placed in the furnace with the flat cross-sectional long side facing up and down, the brazing material melted at the time of brazing is 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). Then, the brazing material accumulated at the lower end in the long side direction of the multi-hole tube 10 tends to flow into the flow path hole 11a or the flow path hole 11i disposed near the lower end portion in the long side direction of the multi-hole pipe 10.

  Thus, in the refrigerant heat exchanger 1, there is a technical problem of suppressing the inflow of the brazing material into the flow path holes 11a to 11i. On the other hand, in the refrigerant heat exchanger 1, as described later, A structure for suppressing the inflow of the brazing material into the flow path holes 11a to 11i is provided.

(6) Structure for suppressing inflow of brazing material into flow path hole In the refrigerant heat exchanger 1, in order to suppress the drawing of the brazing material into the flow path holes 11a to 11i due to the capillary force as described above, It is preferable to provide a structure that can draw the brazing material with a force larger than the capillary force of the passage holes 11a to 11i.

  Therefore, here, as shown in FIGS. 2, 5, and 8 to 10, solder reservoir holes 14 a and 14 b are formed in the multi-hole tube 10. The solder reservoir holes 14a and 14b are located on the outer peripheral side of the plurality of flow path holes 11a to 11i when the longitudinal ends 12 and 13 of the multi-hole tube 10 are viewed along the longitudinal direction of the multi-hole tube 10. It is formed in the part. Here, brazing hole 14a, 14b is formed in the both ends 12b, 13b of the long side direction of the flat cross-sectional shape among the part of the outer peripheral side rather than the some flow-path hole 11a-11i in the multi-hole pipe 10. Yes. The wax reservoir holes 14a and 14b have an opening cross-sectional area smaller than the opening cross-sectional areas of the flow path holes 11a to 11i. That is, when the solder pool holes 14a and 14b and the flow passage holes 11a to 11i are circular holes, the inner diameters of the solder pool holes 14a and 14b are the inner diameters (0.5 mm to 2 mm) of the flow passage holes 11a to 11i. Less than degree). For example, the inner diameters of the wax reservoir holes 14a and 14b are set to about 0.2 to 0.8 times the inner diameter of the flow path holes 11a to 11i (about 0.05 to 0.7 times in the opening cross-sectional area). . Moreover, the polygonal hole shape may be sufficient as the wax accumulation holes 14a and 14b, and also in this case, it is formed so that it may have an opening cross-sectional area smaller than the opening cross-sectional area of the flow-path holes 11a-11i. In addition, here, the solder pool holes 14a and 14b are formed together with the plurality of channel holes 11a to 11i when the multi-hole tube 10 is extruded, and similarly to the plurality of channel holes 11a to 11i, It penetrates between the longitudinal ends 12 and 13 of the tube 10. For this reason, in the refrigerant heat exchanger 1, the wax reservoir holes 14 a and 14 b can be easily formed in the multi-hole tube 10. The solder pool holes 14a and 14b are not limited to those formed together with the plurality of flow path holes 11a to 11i when the multi-hole tube 10 is extruded. For example, the solder pool holes 14a and 14b can be easily formed. However, it may be formed by drilling the multi-hole tube 10. Further, here, the solder reservoir holes 14a and 14b are formed when the longitudinal end portions 12 and 13 of the multi-hole tube 10 are viewed along the longitudinal direction of the multi-hole tube 10 as shown in FIGS. In addition, the spacer 36 is disposed so as to communicate with the collecting hole 36 a of the spacer 36.

  For this reason, as shown in FIG. 11, the brazing material melted at the time of brazing joining is a portion on the outer peripheral side of the flow hole 11a to 11i of the multi-hole tube 10 (here, in the long side direction of the multi-hole tube 10). At both end portions 12b and 13b), the flow passage holes 11a to 11i (here, the flow passage holes 11a and the flow passage holes 11i) are preferentially drawn into the wax reservoir holes 14a and 14b having a capillary force larger than the capillary force of the flow passage holes 11a to 11i. It becomes like this. Further, the brazing holes 14a and 14b are arranged near the end portions 12b and 13b in the long side direction of the multi-hole tube 10 at the time of brazing and joining, so that they accumulate at the lower end in the long side direction of the multi-hole tube 10. As shown in FIG. 11, the brazing material flows preferentially into the brazing hole 14b instead of the flow path hole 11i.

  For example, as shown in FIG. 12, assuming that the opening cross-sectional area of the wax collecting holes 14a and 14b is equal to or larger than the opening cross-sectional area of the flow path holes 11a to 11i, the capillary force of the wax collecting holes 14a and 14b is It will become below the capillary force of channel holes 11a-11i. Therefore, the brazing material melted at the time of brazing and joining is not preferentially drawn into the brazing hole 14a, 14b as shown in FIG. 12, but is drawn into the flow path hole 11a or the flow path hole 11i. The inflow of the brazing material into the flow path holes 11a to 11i cannot be suppressed.

  Thus, in the refrigerant heat exchanger 1, it becomes possible to suppress the inflow of the brazing material into the flow path holes 11a to 11i, and the occurrence of clogging of the flow path holes 11a to 11i can be suppressed. Moreover, in the refrigerant | coolant heat exchanger 1, the influence of the attitude | position of the multi-hole pipe 10 at the time of brazing joining is also considered, and the inflow of the brazing material to the flow-path holes 11a-11i can be suppressed. Further, the refrigerant wax reservoir hole can be easily formed in the multi-hole tube.

(7) Modification <Modification 1>
In order to enhance the pulling action of the brazing material into the brazing hole 14a, 14b, it is preferable to sufficiently increase the capillary force of the brazing hole 14a, 14b.

  Therefore, here, as shown in FIG. 13, guide grooves 15 a and 15 b extending along the longitudinal direction of the multi-hole tube 10 are formed on the inner surfaces of the wax reservoir holes 14 a and 14 b.

  Thereby, here, the capillary force of the brazing hole 14a, 14b can be further increased, and the brazing material melted at the time of brazing can be more preferentially drawn into the brazing hole 14a, 14b.

<Modification 2>
In order to enhance the pulling action of the brazing material into the brazing hole 14a, 14b, it is preferable that the brazing material melted at the time of brazing is easily held on the surface near the portion where the brazing hole 14a, 14b is opened. .

  Therefore, here, as shown in FIG. 14, a guide surface 16a having a larger surface roughness than a surface near the portion where the solder pool holes 14a and 14b are opened and a surface far from the portion where the solder pool holes 14a and 14b are opened. 16b are formed. Here, the guide surfaces 16a and 16b are the multi-hole tube 10 connected to the end surfaces on the longitudinal direction side of both end portions 12b and 13b in the long side direction of the multi-hole tube 10 and the end surfaces on the longitudinal direction side of both end portions 12b and 13b. It is formed on the outer peripheral surface. Further, portions 17a and 17b formed on the outer peripheral surface of the multi-hole tube 10 of the guide surfaces 16a and 16b are closer to the end in the longitudinal direction than the surface of the joining member 38 on the center side in the longitudinal direction of the multi-hole tube 10. Extends to position.

  For this reason, the brazing material melted at the time of brazing joining becomes easy to get wet on the surface close to the portion where the brazing hole 14a, 14b is opened, and hardly gets wet on the surface far from the portion where the brazing hole 14a is opened.

  As a result, the brazing material melted at the time of brazing can be easily held on the surface close to the portion where the brazing hole 14a, 14b is opened. 14a and 14b can be further preferentially drawn.

<Modification 3>
The heat transfer fins 40 are not limited to the corrugated fins shown in FIG. For example, as shown in FIG. 15, an insertion fin type stacked heat exchanger is formed using an insertion fin in which a notch 45 that substantially matches the outer shape of the flat cross-sectional shape of the multi-hole tube 10 is used. You may make it comprise. Even in this case, the brazing material holes 14a and 14b can suppress the inflow of the brazing material into the flow path holes 11a to 11i.

<Modification 4>
The headers 20 and 30 are composed of header bodies 22 and 32 and connecting portions 25 and 35 (spacers 26 and 36, pipe fixing plates 27 and 37, and a joining member 38) shown in FIGS. It is not limited. For example, although not shown here, a header structure in which the spacers 26 and 36 and the tube fixing plates 27 and 37 are omitted from the connecting portions 25 and 35 or a header structure without the connecting portions 25 and 36 may be used. Even in this case, the brazing material holes 14a and 14b can suppress the inflow of the brazing material into the flow path holes 11a to 11i.

  The present invention is widely applicable to a refrigerant heat exchanger configured by brazing and joining the end portions in the longitudinal direction of a multi-hole tube in which a plurality of flow path holes are formed to a header.

DESCRIPTION OF SYMBOLS 1 Refrigerant heat exchanger 10 Multi-hole pipe 11a-11i Flow path hole 12, 13 Longitudinal end part 12b, 13b Long side direction end part 20, 30 Header 14a, 14b Wax accumulation hole 15a, 15b Guide groove 16a, 16b Guide plane

JP 2006-284133 A

Claims (5)

Refrigerant heat configured by brazing and joining longitudinal ends (12, 13) of the multi-hole pipe (10) in which a plurality of flow path holes (11a to 11i) are formed to the header (20, 30). In the exchanger
In the multi-hole tube, when the end portion in the longitudinal direction of the multi-hole tube is viewed along the longitudinal direction of the multi-hole tube, the flow path is formed on the outer peripheral side of the plurality of flow path holes. A wax reservoir hole (14a, 14b) having an opening cross-sectional area smaller than the opening cross-sectional area of the hole is formed,
Refrigerant heat exchanger (1). The multi-hole tube (10) is a flat multi-hole tube having a flat cross-sectional shape,
The plurality of flow path holes (11a to 11i) have the flat cross-sectional shape when the longitudinal ends (12, 13) of the multi-hole tube are viewed along the longitudinal direction of the multi-hole tube. It is arranged side by side in the long side direction,
The brazing hole (14a, 14b) is a long side end of the flat cross-sectional shape when the longitudinal end of the multi-hole tube is viewed along the longitudinal direction of the multi-hole tube ( 12b, 13b),
The refrigerant heat exchanger (1) according to claim 1. Guide grooves (15a, 15b) extending along the longitudinal direction of the multi-hole tube (10) are formed on the inner surfaces of the wax reservoir holes (14a, 14b).
The refrigerant heat exchanger (1) according to claim 1 or 2. The multi-hole pipe (10) has a guide surface (16a) having a surface roughness larger than a surface near the portion where the solder reservoir holes (14a, 14b) are opened and a surface far from the portion where the solder reservoir holes are opened. 16b) is formed,
The refrigerant | coolant heat exchanger (1) of any one of Claims 1-3. The multi-hole tube (10) is formed by extrusion molding of a metal material,
The wax reservoir holes (14a, 14b) are formed together with a plurality of flow path holes (11a to 11i) when the multi-hole tube is extruded.
The refrigerant | coolant heat exchanger (1) of any one of Claims 1-4.

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