JP6477314B2 - Refrigerant evaporator - Google Patents

Description

  The present invention relates to a refrigerant evaporator that performs heat exchange between a fluid to be cooled and a refrigerant.

  The refrigerant evaporator cools the cooled fluid by removing heat from the cooled fluid flowing outside and applying the heat to the liquid-phase refrigerant flowing inside to evaporate.

  As this type of refrigerant evaporator, one described in Patent Document 1 below is known. The refrigerant evaporator performs heat exchange between air, which is a fluid to be cooled, and the refrigerant, and includes a first heat exchange unit and a second heat exchange unit. The first heat exchange unit and the second heat exchange unit are arranged to face each other in the direction in which air flows.

  The first heat exchange part is partitioned into a first core part and a second core part in a direction orthogonal to the direction in which air flows. The second heat exchange part is also divided into a first core part and a second core part in a direction orthogonal to the air flow direction. The 1st core part of the 1st heat exchange part has countered the 1st core part of the 2nd heat exchange part in the direction through which air flows. The 2nd core part of the 1st heat exchange part has countered the 2nd core part of the 2nd heat exchange part in the direction where air flows.

  In addition, the refrigerant evaporator described in Patent Document 1 below includes a pair of tanks connected to both ends of the first heat exchange unit in the vertical direction, and a pair of tanks connected to both ends of the second heat exchange unit in the vertical direction. It has. Moreover, the refrigerant evaporator described in Patent Document 1 below includes a replacement tank between a tank connected to the lower part of the first heat exchange unit and a tank connected to the lower part of the second heat exchange unit.

  In the refrigerant evaporator described in Patent Document 1 below, the refrigerant flows from the tank connected to the upper part of the second heat exchange unit to the first core unit and the second core unit of the second heat exchange unit. The refrigerant that has flowed into the first core part of the second heat exchanging part passes through the tank connected to the lower part of the second heat exchanging part, the replacement tank, and the tank connected to the lower part of the first heat exchanging part. It flows to the second core part of the exchange part. On the other hand, the refrigerant flowing into the second core part of the second heat exchanging part passes through the tank connected to the lower part of the second heat exchanging part, the replacement tank, and the tank connected to the lower part of the first heat exchanging part. It flows to the 1st core part of 1 heat exchange part. The refrigerant that has flowed into the first core part of the first heat exchange part and the refrigerant that has flowed into the second core part of the first heat exchange part are discharged through a tank connected to the upper part of the second heat exchange part.

  Moreover, the vehicle air conditioner of the following patent document 2 is known as an air conditioner which mounts a refrigerant evaporator. In the vehicle air conditioner, a packing material is provided on the outer surface of the lower part of the refrigerant evaporator (evaporator). The packing material contacts the case by disposing the refrigerant evaporator in the case of the vehicle air conditioner, and exhibits a function of sealing between the refrigerant evaporator and the case. Thereby, it is possible to suppress the inflow of air between the refrigerant evaporator and the case, and to efficiently exchange heat between the air and the refrigerant.

JP 2013-185723 A JP 2008-18905 A

  By the way, in the refrigerant evaporator described in Patent Document 1, when the temperature of the air is reduced by heat exchange with the refrigerant, condensed water is generated on the outer surfaces of the first heat exchange unit and the second heat exchange unit. The said condensed water flows below along the outer surface of a 1st heat exchange part or a 2nd heat exchange part. When a gap is formed between the tank connected to the lower part of the first heat exchange part, the tank connected to the lower part of the second heat exchange part, and the replacement tank, the condensed water flows into the gap and stays there. Sometimes. This condensed water may be splashed and mixed in the air, or may hinder the flow of air and cause a decrease in performance.

  The inventors of the present application have studied to form a drainage channel in the refrigerant evaporator and discharge the condensed water to the outside from the gap through the drainage channel as a solution to the problem caused by such condensed water. However, when such a refrigerant evaporator is sealed at its lower part with a packing material like the refrigerant evaporator described in Patent Document 2, the drainage channel is covered with the packing material, and the condensed water cannot be discharged to the outside. I faced a new challenge.

  This invention is made | formed in view of such a situation, The objective is to provide the refrigerant | coolant evaporator which can discharge | emit condensed water outside while sealing with a sealing member.

In order to solve the above problems, a refrigerant evaporator according to the present invention is a refrigerant evaporator (1) that exchanges heat between a fluid to be cooled and a refrigerant, and the refrigerant flows inside and the outside that flows outside. A first heat exchanging section (12) for exchanging heat between the cooling fluid and the refrigerant; and a first heat exchanging section disposed so as to oppose the first heat exchanging section. A second heat exchanging part (22) for exchanging heat between the cooled fluid flowing outside and passing through the refrigerant, and connected to the lower part of the first heat exchanging part, to the first heat exchanging part A first tank (13) for supplying refrigerant, a second tank (23) connected to a lower part of the second heat exchange unit and collecting refrigerant flowing out of the second heat exchange unit, the first tank and the A third tank (3 is connected to the second tank and guides the refrigerant collected in the second tank to the first tank. Comprising a) a seal member provided on the outer surface (60), the. A gap (CL) is formed between the first tank, the second tank, and the third tank. Water is discharged from the gap to at least one of the connection part (133, 304) between the first tank and the third tank and the connection part (233, 305) between the second tank and the third tank. A drainage channel (40) is formed. In the sealing member, a drainage portion (61) for discharging water discharged from the discharge port (42) which is a downstream end portion of the drainage channel to the outside is formed at a portion corresponding to the discharge port . The seal member has an interval seal portion (62) disposed at an interval of the drainage channel. The drainage part is disposed below the discharge port, extends outward from the discharge port side, and has a groove (63) having a width shorter than the diameter of the discharge port, and the discharge port And an inclined surface portion (64) having an inclined surface extending from the side of the groove portion toward both sides of the groove portion and connecting the groove portion and the upper end of the seal member.

  In the present invention, when condensed water generated on the outer surface of the first heat exchange part or the second heat exchange part flows into the gap between the first to third tanks, the condensed water is discharged from the gap via the drainage channel. Discharged. Moreover, also when sealing by making a sealing member contact | abut on the case of an air conditioner, the condensed water which flowed out from the outflow port of a drainage channel is discharged | emitted outside by the drainage part of a sealing member. Therefore, it is possible to discharge condensed water to the outside while sealing with the seal member.

  According to the present invention, it is possible to provide a refrigerant evaporator that can discharge condensed water to the outside while sealing with a seal member.

It is a perspective view which shows the refrigerant | coolant evaporator which concerns on 1st Embodiment, and the vehicle air conditioner which mounts the said refrigerant | coolant evaporator. It is a disassembled perspective view which shows the vehicle air conditioner of FIG. It is a disassembled perspective view which shows the leeward side distribution tank of FIG. 1, the leeward side collection tank, and the replacement | exchange tank. It is a disassembled perspective view which shows typically the flow of the refrigerant | coolant in the refrigerant evaporator of FIG. It is a perspective view which shows the case where the refrigerant evaporator of FIG. 1 is seen in the arrow V direction. It is a side view which shows the structure of the drainage channel of FIG. It is a perspective view which shows the refrigerant evaporator which concerns on 2nd Embodiment. It is a perspective view which shows the refrigerant evaporator which concerns on 3rd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted.

  First, the refrigerant evaporator 1 according to the first embodiment will be described with reference to FIGS. 1 to 6. The refrigerant evaporator 1 of the present embodiment shown in FIG. 1 is mounted on a vehicle air conditioner AC that adjusts the temperature in the passenger compartment, and is used in a refrigeration cycle. Specifically, the refrigerant evaporator 1 is a cooling heat exchanger that cools air by removing heat from the air blown into the passenger compartment and giving the heat to a liquid-phase refrigerant to evaporate it. As is well known, the refrigeration cycle includes, in addition to the refrigerant evaporator 1, a compressor, a radiator, an expansion valve, and the like (not shown).

  The refrigerant evaporator 1 is assembled to the case 90 of the vehicle air conditioner AC. The case 90 is a member that forms a flow path that guides air taken from outside the vehicle (not shown) into the vehicle interior. 1 and 2, a part of the case 90 that supports the refrigerant evaporator 1 and forms the drain 93 is shown in cross-sectional view. The refrigerant evaporator 1 includes two evaporators 10 and 20, a replacement tank 30 (third tank), and an upwind packing 60.

  The evaporators 10 and 20 are arranged on the upstream side and the downstream side so as to face each other in the air flow direction indicated by the arrow X. In this embodiment, the arrow X direction is a direction orthogonal to the arrow Y1 direction that is above the vertical direction and the arrow Y2 direction that is below the vertical direction. Hereinafter, the evaporator 10 arranged on the upstream side in the direction of the arrow X is referred to as “windward evaporator 10”. In addition, the evaporation unit 20 disposed on the downstream side in the arrow X direction is referred to as a “leeward side evaporation unit 20”.

  The windward side evaporation unit 10 includes a windward side collective tank 11, a windward side heat exchange unit 12 (first heat exchange unit), and a windward side distribution tank 13 (first tank). The windward collecting tank 11, the windward heat exchanger 12 and the windward distribution tank 13 are arranged in this order in the direction of the arrow Y1.

  The windward heat exchange unit 12 has a substantially rectangular parallelepiped shape as a whole. The windward heat exchange unit 12 is arranged so that the arrow X direction is the thickness direction. An upwind distribution tank 13 is connected to an end surface 12d of the upwind heat exchange unit 12 in the arrow Y1 direction. The windward collective tank 11 is connected to the end surface 12e on the arrow Y2 side of the windward heat exchange unit 12. The windward heat exchange unit 12 has a structure in which a plurality of tubes 12a and a plurality of fins 12b are alternately stacked in the horizontal direction. In addition, illustration of the tube 12a and the fin 12b is abbreviate | omitted in FIG.

  The tube 12a is arranged so that the cross section is flat and extends in the directions of the arrows Y1 and Y2. A flow path through which the refrigerant flows is formed inside the tube 12a.

  The fins 12b are so-called corrugated fins formed by bending a thin metal plate. The fin 12b is arrange | positioned between the tubes 12a and 12a adjacent to the horizontal direction, and is connected to the outer surface of the tube 12a.

  As shown in FIG. 2, the windward heat exchange unit 12 is partitioned into a first windward core portion 121 and a second windward core portion 122 in the stacking direction of the tubes 12 a and the fins 12 b. Further, as shown in FIG. 1, the windward heat exchange unit 12 includes side plates 12c at both ends in the stacking direction of the tubes 12a and the fins 12b. The side plate 12 c is a member for reinforcing the windward heat exchange unit 12.

  The upwind distribution tank 13 is formed of a cylindrical member having a refrigerant flow path therein. Both ends in the axial direction of the upwind distribution tank 13 are closed. As shown in FIG. 2, the upwind distribution tank 13 has a partition plate 13 a at the center in the axial direction. The partition plate 13 a partitions the internal flow path of the windward distribution tank 13 into a first distribution unit 131 and a second distribution unit 132.

  A plurality of through holes (not shown) into which the end of the tube 12a on the arrow Y1 side is inserted are formed on the outer surface of the upwind distribution tank 13. Through this through hole, the internal flow path of the first distribution part 131 communicates with the tube 12a of the first upwind core part 121, and the internal flow path of the second distribution part 132 communicates with the tube 12a of the second upwind core part 122. doing. That is, the first distribution unit 131 distributes the refrigerant to the tube 12 a of the first upwind core unit 121. The second distribution unit 132 distributes the refrigerant to the tube 12 a of the second upwind core unit 122.

  As shown in FIG. 3, a planar connection portion 133 is formed on the outer surface of the windward distribution tank 13 so as to extend in the axial direction. The connection part 133 is a part to which the replacement tank 30 is connected. A through hole 134 that penetrates the internal flow path of the first distribution part 131 is formed in the connection part 133. The through hole 134 serves as an inlet for guiding the refrigerant in the replacement tank 30 to the first distribution unit 131. In addition, a through hole 135 that penetrates the internal flow path of the second distribution unit 132 is formed in the connection unit 133. The through hole 135 serves as an inlet for guiding the refrigerant in the replacement tank 30 to the second distribution unit 132.

  As shown in FIGS. 1 and 2, the windward collecting tank 11 is formed of a cylindrical member having a refrigerant flow path therein. One end in the axial direction of the windward collecting tank 11 is closed. A refrigerant discharge port 11 a is formed at the other axial end of the windward collecting tank 11. The refrigerant discharge port 11a is connected to the suction side of a compressor (not shown).

  In addition, a plurality of through holes (not shown) into which the ends of the tubes 12a on the arrow Y2 direction side are inserted are formed on the outer surface of the windward collecting tank 11. Through this through hole, the internal flow path of the windward collective tank 11 communicates with the tube 12a of the first windward core part 121 and the tube 12a of the second windward core part 122, respectively. That is, the refrigerant flowing through the tube 12 a of the first upwind core portion 121 and the refrigerant flowing through the tube 12 a of the second upwind core portion 122 are collected in the upwind collecting tank 11. The refrigerant collected in the windward collecting tank 11 is guided to the compressor through the refrigerant discharge port 11a.

  The leeward side evaporation unit 20 includes a leeward side distribution tank 21, a leeward side heat exchange unit 22 (second heat exchange unit), and a leeward side collecting tank 23 (second tank). The leeward distribution tank 21, the leeward heat exchange unit 22, and the leeward collective tank 23 are arranged in this order in the direction of the arrow Y1.

  The leeward heat exchange unit 22 has substantially the same structure as the leeward heat exchange unit 12. That is, the leeward side heat exchanging portion 22 has a substantially rectangular parallelepiped shape as a whole, and is arranged so that the arrow X direction is the thickness direction. The leeward side heat exchanging section 22 has a structure in which a plurality of tubes 22a and a plurality of fins 22b are alternately stacked in the horizontal direction, and has side plates 22c at both ends in the stacking direction of the tubes 22a and the fins 22b. doing. A leeward side collective tank 23 is connected to an end surface 22d of the leeward side heat exchange unit 22 in the arrow Y1 direction. A leeward side distribution tank 21 is connected to an end surface 22e of the leeward side heat exchange unit 22 on the arrow Y2 direction side. Further, as shown in FIG. 2, the leeward side heat exchanging part 22 faces the first leeward side core part 221 and the second leeward side core part 122 facing the first windward side core part 121 in the arrow X direction. The second leeward core portion 222 is partitioned.

  The leeward side distribution tank 21 is formed of a cylindrical member having a refrigerant flow path therein. One end of the leeward side distribution tank 21 in the axial direction is closed. A refrigerant inlet 21 a is formed at the other axial end of the leeward distribution tank 21. Low-pressure refrigerant decompressed by an expansion valve (not shown) flows into the refrigerant inlet 21a.

  In addition, a plurality of through holes (not shown) into which the ends of the tubes 22a on the arrow Y2 direction side are inserted are formed on the outer surface of the leeward distribution tank 21. Through this through hole, the internal flow path of the leeward side distribution tank 21 communicates with the tube 22a of the first leeward side core portion 221 and the tube 22a of the second leeward side core portion 222, respectively. That is, the refrigerant flowing into the leeward distribution tank 21 from the refrigerant inlet 21 a is distributed to the tube 22 a of the first leeward core portion 221 and the tube 22 a of the second leeward core portion 222.

  The leeward side collecting tank 23 is made of a cylindrical member having a refrigerant flow path therein. Both axial ends of the leeward collecting tank 23 are closed. The leeward side collective tank 23 has a partition plate 23a at the center in the axial direction. As shown in FIG. 2, the partition plate 23 a partitions the internal flow path of the leeward collecting tank 23 into a first collecting portion 231 and a second collecting portion 232.

  In addition, a plurality of through holes (not shown) into which the end portions of the tubes 22a in the arrow Y1 direction are inserted are formed on the outer surface of the leeward side collecting tank 23. Through this through hole, the internal flow path of the first collecting portion 231 communicates with the tube 22 a of the first leeward core portion 221, and the internal flow passage of the second collective portion 232 communicates with the tube 22 a of the second leeward core portion 222. doing. That is, the refrigerant flowing through the tube 22 a of the first leeward core portion 221 is collected in the first collecting portion 231. In addition, the refrigerant flowing through the tube 22 a of the second leeward core portion 222 is collected in the second collecting portion 232.

  As shown in FIG. 3, a planar connection portion 233 is formed on the outer surface of the leeward collecting tank 23 so as to extend in the axial direction. The connection part 233 is a part to which the replacement tank 30 is connected. A through hole 234 that penetrates the internal flow path of the first collecting portion 231 is formed in the connection portion 233. The through hole 234 serves as a flow path for guiding the refrigerant in the first collecting portion 231 to the replacement tank 30. In addition, a through hole 235 that penetrates the internal flow path of the second collecting portion 232 is formed in the connection portion 233. The through hole 235 serves as a flow path for guiding the refrigerant in the second collecting portion 232 to the replacement tank 30.

  The replacement tank 30 is provided between the leeward distribution tank 13 and the leeward collective tank 23. The replacement tank 30 is formed of a cylindrical member having a refrigerant flow path therein. A partition member 301 is provided inside the replacement tank 30. The partition member 301 partitions the internal space of the replacement tank 30 into a first refrigerant channel 302 and a second refrigerant channel 303.

  As shown in FIG. 3, a planar connection portion 304 to which the connection portion 133 of the upwind distribution tank 13 is connected and a connection portion 233 of the leeward side collective tank 23 are connected to the outer surface of the replacement tank 30. And a planar connecting portion 305 is formed.

  A through hole 306 that penetrates the first refrigerant flow path 302 is formed in the connection portion 304. The through hole 306 is arranged so as to be connected to the through hole 134 of the upwind distribution tank 13. A through hole 307 that penetrates the first refrigerant flow path 302 is formed in the connection portion 305. The through hole 307 is arranged so as to be connected to the through hole 235 of the leeward collecting tank 23. That is, the refrigerant collected in the second collecting portion 232 of the leeward side collecting tank 23 flows into the first refrigerant flow path 302 through the through hole 235 of the leeward side collecting tank 23 and the through hole 307 of the replacement tank 30. The refrigerant flowing into the first refrigerant flow path 302 is guided to the first distribution part 131 of the upwind distribution tank 13 through the through hole 306 of the replacement tank 30 and the through hole 134 of the upwind distribution tank 13.

  In addition, a through hole 308 that penetrates the second refrigerant flow path 303 is formed in the connection portion 304. The through hole 308 is arranged so as to be connected to the through hole 135 of the upwind distribution tank 13. The connection part 305 is formed with a through hole 309 that penetrates the second refrigerant flow path 303. The through hole 309 is arranged so as to be connected to the through hole 234 of the leeward collecting tank 23. That is, the refrigerant collected in the first collecting portion 231 of the leeward collecting tank 23 flows into the second refrigerant flow path 303 through the through hole 234 of the leeward collecting tank 23 and the through hole 309 of the replacement tank 30. The refrigerant flowing into the second refrigerant flow path 303 is guided to the second distribution part 132 of the upwind distribution tank 13 through the through hole 308 of the replacement tank 30 and the through hole 135 of the upwind distribution tank 13.

  In this way, the replacement tank 30 functions as a portion that guides the refrigerant collected in the leeward side collecting tank 23 to the leeward side distribution tank 13. In addition, the replacement tank 30 functions as a portion that exchanges the refrigerant flow in the leeward heat exchange unit 22 and the refrigerant flow in the leeward heat exchange unit 12 in the stacking direction of the tubes 12a and 22a.

  The windward packing 60 (seal member) is a flat plate member formed so as to extend along the axial direction of the windward distribution tank 13 and the replacement tank 30 as shown in FIG. The windward side packing 60 is formed of a rubber material having great elasticity. Further, as shown in FIG. 1, the windward side packing 60 is pasted so as to straddle the windward side distribution tank 13 and the replacement tank 30 so as to follow the shape of the outer side surfaces of both. Yes.

  When the refrigerant evaporator 1 is assembled to the case 90, the support protrusions 91 a and 91 b formed on the windward side support wall 91 of the case 90 come into contact with the windward side packing 60. Thereby, the seal | sticker between the refrigerant evaporator 1 and the windward support wall 91 is comprised. The windward packing 60 suppresses the inflow of air between the refrigerant evaporator 1 and the windward support wall 91.

  Further, the refrigerant evaporator 1 abuts the outer surface of the leeward side collective tank 23 with the leeward side packing 70 attached near the upper end of the leeward side support wall 92 of the case 90. As a result, the refrigerant evaporator 1 is sandwiched between the windward side packing 60 and the leeward side packing 70 in the direction of the arrow X and supported above the drain 93 of the case 90.

  Next, the refrigerant flow and the air cooling method in the refrigerant evaporator 1 will be described. The refrigerant decompressed by an expansion valve (not shown) is introduced into the leeward distribution tank 21 from the refrigerant inlet 21a as indicated by an arrow A in FIG. This refrigerant is distributed inside the leeward side distribution tank 21 and flows into the first leeward side core part 221 and the second leeward side core part 222 of the leeward side heat exchange part 22 as indicated by arrows B and C. .

  The refrigerant flowing into the first leeward core portion 221 and the second leeward core portion 222 flows in the direction of the arrow Y1 through the inside of each tube 22a. At this time, the refrigerant flowing inside the tube 22a exchanges heat with the air flowing in the X direction outside the tube 22a through the wall surface of the tube 22a. As a result, part of the refrigerant evaporates and takes heat from the air, thereby cooling the air.

  The refrigerant flowing through the tube 22 a of the first leeward core portion 221 is collected in the first collecting portion 231 of the leeward collecting tank 23 as indicated by an arrow D. The refrigerant collected in the first collecting portion 231 flows into the second distribution portion 132 of the upwind distribution tank 13 through the second refrigerant flow path 303 of the replacement tank 30 as indicated by an arrow F. The refrigerant flowing into the second distribution unit 132 flows into the second upwind core unit 122 as indicated by an arrow H.

  On the other hand, the refrigerant flowing through the tube 22 a of the second leeward core 222 is collected in the second collecting portion 232 of the leeward collecting tank 23 as indicated by an arrow E. The refrigerant collected in the second collecting portion 232 flows into the first distribution portion 131 of the upwind distribution tank 13 through the first refrigerant flow path 302 of the replacement tank 30 as indicated by an arrow G. The refrigerant that has flowed into the first distribution unit 131 flows into the first upwind core unit 121 as indicated by the arrow I.

  The refrigerant that has flowed into the first windward core portion 121 and the second windward core portion 122 flows in the direction of the arrow Y2 through the inside of each tube 12a. At this time, the refrigerant flowing inside the tube 12a exchanges heat with the air flowing outside the tube 12a in the direction of the arrow X and the wall surface of the tube 12a. As a result, part of the refrigerant evaporates and takes heat from the air, thereby cooling the air.

  The refrigerant flowing through the first windward core portion 121 and the second windward core portion 122 is collected in the windward collecting tank 11 as indicated by arrows K and J. As indicated by an arrow L, the refrigerant collected in the windward collecting tank 11 is supplied from the refrigerant discharge port 11a of the windward collecting tank 11 to the suction side of a compressor (not shown).

  Next, discharge of condensed water generated in the refrigerant evaporator 1 will be described with reference to FIGS. FIG. 5 is a perspective view showing the refrigerant evaporator 1 as viewed in the direction of arrow V in FIG. 1, and the illustration of the case 90 is omitted.

  When the temperature of the air decreases due to heat exchange with the refrigerant, condensed water (hereinafter also simply referred to as “water”) due to condensation is generated on the outer surfaces of the windward side heat exchange unit 12 and the leeward side heat exchange unit 22. This water flows in the direction of the arrow Y1 along the outer surfaces of the windward side heat exchange unit 12 and the leeward side heat exchange unit 22.

  As shown in FIG. 6, this water may flow into the gap CL between the leeward distribution tank 13, the leeward collecting tank 23, and the replacement tank 30 and may stay there. This condensed water may be splashed and mixed in the air, or may hinder the flow of air and cause a decrease in performance. Therefore, the refrigerant evaporator 1 of the present embodiment is provided with a drainage structure for discharging water from the gap CL.

  As shown in FIG. 3, a plurality of drain grooves 310 are formed in the connection portion 304 of the replacement tank 30 along the slope of the connection portion 304. Further, a drainage groove 136 is formed in the connection part 133 of the upwind distribution tank 13 at a position corresponding to the drainage groove 310 of the connection part 304 of the replacement tank 30.

  As shown in FIG. 6, the replacement tank 30 and the windward distribution tank 13 are connected, so that the drainage groove 310 of the connection portion 304 of the replacement tank 30 and the drainage groove of the connection portion 133 of the windward distribution tank 13 are connected. Two drainage channels 40 surrounded by 136 are formed. The drainage channels 40, 40 are both cylindrical spaces and are formed at intervals.

  An inlet 41 that opens to the gap CL is formed at one end of each drainage channel 40. Further, a discharge port 42 is formed at the other end of each drainage channel 40 and opens into the space on the arrow Y1 direction side of the upwind distribution tank 13. Each discharge port 42 is arranged on the arrow Y1 direction side from the gap CL.

  As shown in FIG. 3, a plurality of drain grooves 311 are formed in the connection portion 305 of the replacement tank 30 along the slope of the connection portion 305. Further, a drainage groove 236 is formed in the connection portion 233 of the leeward side collecting tank 23 at a position corresponding to the drainage groove 311 of the connection portion 305 of the replacement tank 30.

  As shown in FIG. 6, by connecting the replacement tank 30 and the leeward side collective tank 23, the drainage groove 311 of the connection portion 305 of the replacement tank 30 and the drainage groove of the connection portion 233 of the leeward side collective tank 23. Four drainage channels 50 surrounded by 236 are formed. Each drainage channel 50 is a cylindrical space, and is formed with a space therebetween.

  At one end of each drainage channel 50, an inflow port 51 that opens to the gap CL is formed. Further, at the other end of each drainage channel 50, a discharge port 52 that opens into a space on the arrow Y1 direction side of the leeward side collecting tank 23 is formed. Each discharge port 52 is arranged on the arrow Y1 direction side from the gap CL.

  2 and 4, the drainage grooves 310 and 311 of the replacement tank 30, the drainage groove 136 of the upwind distribution tank 13, and the drainage groove 236 of the leeward side collecting tank 23 are not shown.

  Further, as shown in FIG. 5, drainage portions 61, 61 are formed in a portion of the upwind packing 60 corresponding to the discharge port 42. Each drainage portion 61 is formed in a notch shape in which a part of the upper end portion of the windward side packing 60 is notched in a triangular shape and has a groove portion 63 and inclined surface portions 64 and 64. ing. The part between the drainage parts 61 and 61 in the upwind packing 60 is a gap seal part 62 arranged at the gap between the discharge ports 42 and 42.

  The groove 63 is a surface that is disposed below the discharge port 42 and extends outward from the discharge port 42 side. The groove 63 extends so as to incline downward from the discharge port 42 side toward the outside. Moreover, the groove part 63 is exhibiting the triangular shape which makes the discharge port 42 side a base, and it is formed so that the width | variety may decrease gradually toward the outward from the discharge port 42 side.

  The inclined surface portions 64 and 64 are surfaces disposed on the side of the discharge port 42, and are connected to the groove portion 63 at the lower end thereof. The inclined surface portions 64 and 64 are opposed to each other with the discharge port 42 interposed therebetween, and are inclined so as to be inclined downward toward the groove portion 63 so that the distance between the two decreases from the discharge port 42 side to the groove portion 63 side. ing.

  Water generated on the outer surfaces of the windward side heat exchange unit 12 and the leeward side heat exchange unit 22 and flowing into the gap CL is discharged from the gap CL via the drainage channel 40 or the drainage channel 50. Of these, the water discharged from the gap CL through the drainage channel 50 flows in the direction of the arrow Y1 along the inner side surface of the leeward side support wall 92 of the case 90 as shown by the arrow W3 in FIG. It is led to a drain 93 for discharging water from the inside.

  On the other hand, the water discharged from the gap CL through the drainage channel 40 flows into a space formed between the outer surface of the upwind distribution tank 13 and the replacement tank 30 and the upwind packing 60. This water is further discharged to the outside through drainage portions 61 and 61 formed in the upwind packing 60.

  As indicated by an arrow W <b> 1 in FIG. 5, this water is discharged outside along the groove 63 of the drainage part 61. As described above, since the groove portion 63 is inclined downward from the discharge port 42 side toward the outside, the water is smoothly discharged using its own weight. The water discharged to the outside through the drainage part 61 flows in the direction of the arrow Y1 along the inner side surface of the windward support wall 91 of the case 90 as shown by the arrow W2 in FIG. Led to.

  As described above, according to the refrigerant evaporator 1, the condensed water generated on the outer surface of the windward side heat exchange unit 12 or the leeward side heat exchange unit 22 becomes the windward side distribution tank 13, the leeward side collecting tank 23, and the replacement tank 30. When the water flows into the gap CL, the condensed water is discharged from the gap CL through the drainage channel 40. Even when sealing is performed by bringing the windward packing 60 into contact with the case 90 of the vehicle air conditioner AC, the condensed water flowing out from the discharge port 42 of the drainage channel 40 is discharged from the drainage portion of the windward packing 60. 61 is discharged to the outside. Therefore, it is possible to discharge condensed water to the outside while sealing with the upwind packing 60.

  Further, in the refrigerant evaporator 1, the drainage part 61 is formed in a portion corresponding to the discharge port 42 in the upwind packing 60. Accordingly, the condensed water discharged from the discharge port 42 can be smoothly discharged to the outside of the windward side packing 60.

  Further, in the refrigerant evaporator 1, the drainage channels 40, 40 are formed with a space therebetween, and the upwind packing 60 has a space seal portion 62 disposed at this space. Therefore, it is possible to further improve the sealing performance of the upwind packing 60 while discharging the condensed water by the drainage part 61.

  Further, in the refrigerant evaporator 1, the drainage part 61 is disposed below the discharge port 42 and extends outward from the discharge port 42 side, and is disposed on the side of the discharge port 42 toward the groove part 63. And an inclined surface portion 64 inclined downward. Thereby, the condensed water discharged from the discharge port 42 is collected in the lower groove portion 63 along the inclination of the inclined surface portion 64. Therefore, even when the condensed water is in the form of water droplets in the groove 63, the water droplets are relatively large. As a result, the water droplet-shaped condensed water can be smoothly discharged from the drainage portion 61 by its own weight without remaining in the groove portion 63.

  Moreover, the groove part 63 is formed so that the width | variety may reduce gradually toward the outward from the discharge port 42 side. Thereby, the condensed water which flows through the groove part 63 is gradually collected as it goes outside from the discharge port 42 side. Therefore, even when the condensed water is in the form of water droplets in the groove 63, the water droplets are relatively large. As a result, the water droplet-shaped condensed water can be smoothly discharged from the drainage portion 61 by its own weight without remaining in the groove portion 63.

  Next, the refrigerant evaporator 1A according to the second embodiment will be described with reference to FIG. The refrigerant evaporator 1A according to the second embodiment is used for the refrigeration cycle of the vehicle air conditioner AC, similarly to the refrigerant evaporator 1 according to the first embodiment. FIG. 7 is a perspective view showing a case where the refrigerant evaporator 1A is viewed in the same direction as FIG. 5 (the direction of arrow V in FIG. 1). The same components as those in the first embodiment are denoted by the same reference numerals as appropriate, and the description thereof is omitted.

  The windward packing 60A according to the second embodiment is provided with drainage portions 61A and 61A. Each drainage portion 61A is formed in a cutout shape in which a part of the upper end portion of the windward side packing 60A is cut out in a rectangular shape facing downward, and has a groove portion 63A and vertical surface portions 65 and 65. ing. The water discharged from the discharge port 42 is discharged to the outside along the groove portion 63A of the drainage portion 61 as indicated by an arrow W4.

  In this 2nd Embodiment, since each drainage part 61A is exhibiting the rectangular shape, it becomes possible to form by comparatively simple processing. Accordingly, it is possible to reduce the manufacturing cost and discharge condensed water to the outside while sealing with the upwind packing 60A.

  Next, the refrigerant evaporator 1B according to the third embodiment will be described with reference to FIG. The refrigerant evaporator 1B according to the third embodiment is used for the refrigeration cycle of the vehicle air conditioner AC, similarly to the refrigerant evaporators 1 and 1A according to the above-described embodiments. FIG. 8 is a perspective view showing a case where the refrigerant evaporator 1B is viewed in the same direction as FIG. 5 (the direction of arrow V in FIG. 1). The same configurations as those of the above-described embodiment are appropriately denoted by the same reference numerals, and description thereof is omitted.

  Drainage portions 61B and 61B are formed in the upwind packing 60B according to the third embodiment. Each drainage part 61B has a groove part 63B and vertical surface parts 65 and 65. Moreover, each drainage part 61B has the upper seal part 66 which covers the upper direction of the discharge port 42. As shown in FIG. Thereby, each drainage part 61B is formed in the through-hole shape which penetrates a part of upper part of upwind packing 60B in thickness direction. The water discharged from the discharge port 42 is discharged to the outside along the groove portion 63B of the drainage portion 61B as indicated by the arrow W5.

  In the third embodiment, since each drainage part 61B has the upper seal part 66 that covers the upper side of the discharge port 42, the inflow of air to the discharge port 42 can be suppressed. Therefore, the condensed water can be discharged smoothly from the discharge port 42.

  The embodiments of the present invention have been described above with reference to specific examples. However, the present invention is not limited to these specific examples. In other words, those specific examples that have been appropriately modified by those skilled in the art are also included in the scope of the present invention as long as they have the characteristics of the present invention. Each element included in each of the specific examples described above and their arrangement, material, condition, shape, size, and the like are not limited to those illustrated, and can be appropriately changed.

1, 1A, 1B: Refrigerant evaporator 12: Upwind heat exchange section (first heat exchange section)
13: Upwind distribution tank (first tank)
22: Downward heat exchange section (second heat exchange section)
23: Downward side collecting tank (second tank)
30: Replacement tank (third tank)
40, 50: Drainage channel 42, 52: Discharge port 60, 60A, 60B: Upwind packing (seal member)
61, 61A, 61B: Drainage part 62: Spacing seal part 63, 63A, 63B: Groove part 64: Inclined surface part 66: Upper seal part

Claims (2)

A refrigerant evaporator (1) for exchanging heat between a fluid to be cooled and a refrigerant,
A first heat exchanging section (12) for exchanging heat between the refrigerant to be cooled flowing inside and the fluid to be cooled flowing outside; and the refrigerant;
The second heat exchanger is disposed so as to face the first heat exchange unit, and the refrigerant flows through the inside, and exchanges heat between the refrigerant to be cooled and the refrigerant flowing outside through the first heat exchange unit. A heat exchange section (22);
A first tank (13) connected to a lower part of the first heat exchange unit and supplying a refrigerant to the first heat exchange unit;
A second tank (23) connected to a lower portion of the second heat exchange unit and collecting refrigerant flowing out of the second heat exchange unit;
A third tank (30) connected to the first tank and the second tank and guiding the refrigerant collected in the second tank to the first tank;
A seal member (60) provided on the outer surface,
A gap (CL) is formed between the first tank, the second tank, and the third tank,
Water is discharged from the gap to at least one of the connection part (133, 304) between the first tank and the third tank and the connection part (233, 305) between the second tank and the third tank. A plurality of drainage channels (40) are formed at intervals ,
The seal member is formed with a drainage portion (61) for discharging water discharged from the discharge port (42), which is the downstream end portion of the drainage channel, to a portion corresponding to the discharge port. ,
The seal member has an interval seal portion (62) disposed at an interval of the drainage channel,
The drainage part is disposed below the discharge port, extends outward from the discharge port side, and has a groove (63) having a width shorter than the diameter of the discharge port, and the discharge port A refrigerant evaporator, comprising: an inclined surface portion (64) extending from the side of the groove portion toward both sides of the groove portion and having an inclined surface connecting the groove portion and the upper end of the seal member. 2. The refrigerant evaporator according to claim 1, wherein the groove portion is formed so that a width thereof gradually decreases outward from the discharge port side.

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