JP6520563B2 - Refrigerant evaporator - Google Patents

Description

  The present invention relates to a refrigerant evaporator that has a first evaporator and a second evaporator arranged to face each other in the flow direction of the fluid to be cooled, and performs heat exchange between the fluid to be cooled and the refrigerant. .

  The refrigerant evaporator takes heat from the fluid to be cooled flowing outside by the latent heat of evaporation when the liquid phase refrigerant flowing inside evaporates, thereby cooling the fluid to be cooled.

  For example, Patent Document 1 below shows a refrigerant evaporator having a core portion formed by laminating a plurality of tubes in which liquid-phase refrigerant and gas-phase refrigerant (hereinafter both are also simply referred to as "refrigerant") flow. Have been described. The core portion has a wide shape in which the dimension in the stacking direction is larger than the dimension in the direction in which the air as the fluid to be cooled flows.

  The refrigerant evaporator disclosed in Patent Document 1 is configured to allow the refrigerant to flow into the core portion from a first header tank disposed above the core portion. That is, the first header tank distributes the refrigerant flowing therein and flows into the plurality of tubes in one row constituting the core portion. The refrigerant flows downward in each tube and flows out from the lower end of each tube. When the refrigerant is folded back in the second header tank disposed below the core portion, it then flows into the other row of tubes constituting the core portion. The refrigerant flows upward in each tube.

  By the way, the first header tank is provided with an inlet for introducing the refrigerant from the outside, but the refrigerant flowing into the first header tank from the inlet has a flow rate of the refrigerant, particularly when the flow rate of the refrigerant is small. It tends to flow easily into the tube located near the inlet. For this reason, in the wide core portion, the flow rate of the refrigerant flowing into the tube may differ between the portion near the inflow port and the portion far away from the inflow port, and the distribution of the refrigerant may become uneven. There is. As described above, when the distribution of the refrigerant becomes uneven in the core portion, a region where heat exchange between the fluid to be cooled and the refrigerant is not effectively performed is generated in the core portion, and the cooling performance of the refrigerant evaporator decreases. Occur. In addition, since the air that has flowed in the region where heat exchange is not effectively performed is not sufficiently cooled, it also causes a problem of impairing comfort.

  Also, even when the refrigerant is made to flow uniformly into the tubes from the first header tank, the refrigerant flows from the second header tank into the plurality of tubes in the other row because of the evaporation of the refrigerant in the tubes. The distribution of the refrigerant may be uneven. More specifically, in the case of flowing the refrigerant of the same mass flow rate, the resistance that the gas phase refrigerant receives from the wall of the tube is greater than the resistance that the liquid phase refrigerant receives from the wall of the tube. Further, on the downstream side of the tubes, a large amount of liquid phase refrigerant evaporates to become a gas phase refrigerant, but the ease of evaporation may also differ between the tubes. For this reason, if the inside of the second header tank is a single space, the refrigerant in the second header tank is directed to a tube in which the liquid-phase refrigerant is less likely to evaporate compared to the other tubes. Become. As a result, the distribution of the refrigerant flowing from the second header tank into the plurality of tubes in the other row becomes uneven.

  On the other hand, in the refrigerant evaporator described in Patent Document 1 below, the inside of the header tank is divided into a plurality of compartments by arranging a plurality of partition walls in the second header tank. The partition walls are formed so as not to cause the movement of the refrigerant in the adjacent compartments. As a result, even when the evaporation easiness of the refrigerant is different between the tubes, it is possible to suppress the nonuniformity of the distribution of the refrigerant and to improve the cooling performance of the refrigerant evaporator.

JP 2014-518370 gazette

  However, the refrigerant evaporator described in Patent Document 1 has a problem that the refrigerant distribution can not be sufficiently suppressed from being uneven when the flow rate of the supplied refrigerant is relatively small. That is, in the refrigerant evaporator described in Patent Document 1, when the flow rate of the supplied refrigerant is relatively small, the refrigerant tends to be directed to the tube located in the vicinity of the inlet of the first header tank. As described above, when the distribution of the refrigerant becomes uneven at the time of flowing into the tube, the inside of the second header tank is partitioned by the dividing wall, so that the unevenness is not eliminated in the second header tank. It affects further downstream. As a result, air that is not cooled even when flowing through the refrigerant evaporator is generated, and there is a problem in that the comfort of a vehicle compartment or the like to which the air is supplied is reduced.

  The present invention has been made in view of such problems, and an object thereof is to suppress uneven distribution of the refrigerant regardless of the flow rate of the supplied refrigerant and to uniformly cool the flowing air. It is to provide a refrigerant evaporator.

In order to solve the above-mentioned subject, the refrigerant evaporator concerning the present invention is the 1st evaporation part (20, 20C) and the 2nd evaporation part (10, 10C) which were arranged so as to mutually oppose in the direction to which a to-be-cooled fluid flows. A refrigerant evaporator (1, 1A, 1B, 1C) for exchanging heat between the fluid to be cooled and the refrigerant, wherein the first evaporation section is configured to flow the refrigerant downward. The first core portion (22, 22C) configured by laminating the first tubes (22a, 22Ca) in the first direction, and the first core portion are disposed above, and the refrigerant flows along the first direction. And a first distribution portion (21, 21C) for distributing the refrigerant to flow from the upper end portions of the plurality of first tubes, and a lower portion of the plurality of first tubes disposed below the first core portion A first collecting portion (23, 23B, 23C) for collecting the refrigerant which has flowed out A. The second evaporation unit is configured by laminating a plurality of second tubes (12a, 12Ca) for flowing the refrigerant upward in the first direction, and a second core unit. And a second distribution unit (13, 13C) for receiving the supply of the refrigerant from the first collecting portion and distributing the refrigerant from the lower end portions of the plurality of second tubes, and the second core And a second collecting portion (11, 11C) for collecting the refrigerant flowing out from the upper ends of the plurality of second tubes. The first collective portion is partitioned by a plurality of first partitions (231, 231A, 231B, 231C) arranged at predetermined intervals so as to line up in the first direction, and the plurality of first partitions. And a plurality of first compartments (232, 232B, 232C). The second distribution unit is defined by a plurality of second partitions (131, 131C) arranged at predetermined intervals so as to line up in the first direction, and the plurality of second partitions , and is independent of each other And a plurality of second compartments (132, 132C) formed as a separated space . The first partition is a water draining portion for moving the refrigerant to another first compartment adjacent to the first compartment when the water level of the refrigerant in the first compartment exceeds a predetermined water level ((1) 234, 234A, 234B, 234C).

  According to this configuration, when the flow rate of the refrigerant reaching each of the first compartments of the first collecting portion is relatively large, the refrigerant is supplied to the second distribution unit without staying in each of the first compartments. For this reason, the movement of the refrigerant between the adjacent first compartments is hindered by the first partition wall.

  On the other hand, when the flow rate of the refrigerant reaching each first compartment of the first collecting portion is relatively small, the refrigerant stagnates in each first compartment and its water level rises. When the water level of the refrigerant in one first compartment exceeds the predetermined water level, the refrigerant moves to another first compartment adjacent to the first compartment. That is, the refrigerant is moved from the first compartment where the water level of the refrigerant is high to the first compartment where the water level of the refrigerant is low, and the water level of the refrigerant staying in each first compartment of the first collecting portion is equalized. it can. Since the refrigerant whose water level has been equalized is supplied to the second distribution unit, the distribution of the refrigerant in the second evaporation unit can be equalized.

  Therefore, according to this configuration, it is possible to suppress uneven distribution of the refrigerant in the first core portion and the second core portion regardless of the flow rate of the supplied refrigerant.

  ADVANTAGE OF THE INVENTION According to this invention, it can suppress that distribution of a refrigerant | coolant becomes non-uniform | heterogenous regardless of the flow volume of the refrigerant | coolant supplied, and can provide the refrigerant | coolant evaporator which can cool flowing air uniformly.

It is a perspective view which shows the refrigerant evaporator concerning a 1st embodiment typically. It is a disassembled perspective view which shows typically the flow of the refrigerant | coolant in the refrigerant evaporator of FIG. It is sectional drawing which shows the III-III cross section of the refrigerant evaporator of FIG. 1 in case the flow volume of the refrigerant | coolant supplied is comparatively large. It is sectional drawing which shows the III-III cross section of the refrigerant evaporator of FIG. 1 in case the flow volume of the refrigerant | coolant supplied is comparatively small. It is sectional drawing which shows the VV cross section of the refrigerant evaporator of FIG. 2 in case the flow volume of the refrigerant | coolant supplied is comparatively small. It is sectional drawing which shows the refrigerant evaporator which concerns on a 1st modification. It is sectional drawing which shows the refrigerant evaporator which concerns on a 1st modification. It is a perspective view which shows the refrigerant evaporator concerning a 2nd embodiment typically. It is sectional drawing which shows the IX-IX cross section of the refrigerant evaporator of FIG.

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

  The configuration of the refrigerant evaporator 1 according to the first embodiment will be described with reference to FIGS. 1 and 2. FIG. 2 illustrates the inside of the upwind collective tank 11, the upwind distribution tank 13, the downwind distribution tank 21, and the downwind collective tank 23 described later by broken lines.

  The refrigerant evaporator 1 is mounted on a vehicle air conditioner that adjusts the temperature in a vehicle compartment, and is used for a refrigeration cycle. Specifically, the refrigerant evaporator 1 is a cooling heat exchanger that cools air by taking heat from the air blown into the vehicle compartment and giving the heat to a liquid phase refrigerant to evaporate it. As well known, in addition to the refrigerant evaporator 1, the refrigeration cycle is composed of a compressor, a radiator, an expansion valve, and the like (not shown).

  The refrigerant evaporator 1 includes two evaporators 10 and 20. The evaporation units 10 and 20 are disposed on the upstream side and the downstream side so as to face each other in the air flow direction indicated by the arrow X1. Hereinafter, the evaporation unit 10 disposed on the upstream side in the direction of the arrow X1 will be referred to as "wind-side evaporation unit 10" (second evaporation unit). Moreover, the evaporation part 20 arrange | positioned downstream in the arrow X1 direction is called "the downwind side evaporation part 20" (1st evaporation part).

  In addition, in order to facilitate understanding, a rectangular coordinate in which the direction (horizontal direction) in which the air to be cooled flows is taken as the X direction, the horizontal direction orthogonal to the X direction as the Y direction, and the upper direction as the Z direction. It demonstrates using. The orthogonal coordinates used correspond to each other in FIG.

  The upwind evaporation unit 10 includes an upwind collective tank 11 (second aggregation unit), an upwind core unit 12 (second core unit), and an upwind distribution tank 13 (second distribution unit). . The upwind collecting tank 11, the upwind core portion 12 and the upwind distribution tank 13 are arranged in this order in the -Z direction.

  The windward core portion 12 has a flat rectangular parallelepiped shape whose thickness direction is the X direction as a whole. A windward distribution tank 13 is connected to the lower end 12 d of the windward core portion 12. The windward collecting tank 11 is connected to the upper end 12 e of the windward core portion 12. The upwind core portion 12 has a structure in which a plurality of upwind tubes 12a (second tubes) and a plurality of upwind fins 12b are alternately stacked in the Y direction.

  The upwind side tube 12a has a flat cross section and is arranged to extend in the Z direction. A flow path through which the refrigerant flows is formed in the upwind side tube 12a.

  The windward fins 12b are so-called corrugated fins formed by bending a thin metal plate. The windward fins 12b are disposed between the windward tubes 12a and 12a adjacent in the Y direction, and are connected to the outer surface of the windward tube 12a.

  Further, the windward core portion 12 has plate-shaped side plates 12c at both ends in the Y direction of the windward tube 12a and the windward fins 12b, which are stacked. The side plate 12 c is a member for reinforcing the windward core portion 12.

  The upwind distribution tank 13 is formed of a tubular member having a flow path of refrigerant inside. Both ends in the axial direction (Y direction) of the upwind distribution tank 13 are closed. As shown in FIG. 2, the upwind distribution tank 13 has five upwind partitions 131 (second partitions) inside thereof. The upwind partitions 131 have a plate shape having a plane substantially perpendicular to the Y direction, and are arranged in the upwind distribution tank 13 at intervals along the Y direction. Thereby, in the windward distribution tank 13, six windward side compartments 132 (second compartments) arranged along the Y direction are defined.

  Further, on the outer side surface of the upper portion of the windward distribution tank 13, a plurality of through holes (not shown) into which the lower end portion 12a1 of the windward tube 12a is inserted are formed. By inserting the lower end portion 12a1 (see FIG. 2) of the upwind tube 12a into the through hole, each upwind compartment 132 communicates with the upwind tubes 12a. That is, each upwind compartment 132 is a space that allows the refrigerant to flow in from the lower ends 12a1 of the plurality of upwind tubes 12a in communication, and distributes the refrigerant to each upwind tube 12a.

  As shown in FIG. 2, six inlets 133 communicating with the upwind side compartments 132 are formed on the outer side surface of the upwind side distribution tank 13. The inlet 133 is an opening for introducing the refrigerant into the upwind compartments 132 and is formed on the side of each upwind compartment 132.

  As shown in FIG. 1 and FIG. 2, the windward collecting tank 11 is formed of a tubular member having a flow path of refrigerant inside. The Y-direction end of the windward collecting tank 11 is closed. A discharge port 11 a is formed at an end of the windward collecting tank 11 on the −Y direction side. The discharge port 11a is connected to the suction side of a compressor (not shown).

  Further, a plurality of through holes (not shown) into which the upper end portion 12a2 (see FIG. 2) of the windward tube 12a is inserted are formed on the outer side surface of the lower portion of the windward collecting tank 11. When the upper end 12a1 of the upwind tube 12a is inserted into the through hole, the internal flow path of the upwind collective tank 11 communicates with the upwind tube 12a. That is, the refrigerant flowing through the upwind tubes 12 a and flowing out of the upper end 12 a 1 is collected in the upwind collecting tank 11. The refrigerant collected in the upwind collecting tank 11 is led to the compressor via the outlet 11a.

  The downwind side evaporation unit 20 has a downwind side distribution tank 21 (first distribution portion), a downwind side core portion 22 (first core portion), and a downwind side collective tank 23 (first aggregation portion). . The downwind distribution tank 21, the downwind core portion 22, and the downwind collective tank 23 are arranged in this order in the -Z direction.

  The downwind side core portion 22 has substantially the same structure as the upwind side core portion 12. That is, the leeward core portion 22 has a flat rectangular parallelepiped shape whose thickness direction is the X direction as a whole. Further, as shown in FIG. 2, the leeward core portion 22 has a structure in which a plurality of leeward tubes 22 a (first tubes) and a plurality of leeward fins 22 b are alternately stacked in the Y direction, Plate-shaped side plates 22c are provided at both ends in the Y direction of the downwind side tubes 22a and the downwind side fins 22b that are stacked. A leeward distribution tank 21 is connected to the upper end 22 e of the leeward core portion 22. A leeward collecting tank 23 is connected to the lower end 22 d of the leeward core portion 22.

  The downwind side distribution tank 21 consists of a cylindrical member which has a flow path of a refrigerant inside. The Y-direction end of the downwind distribution tank 21 is closed. An inflow port 21 a is formed at an end of the downwind side distribution tank 21 in the −Y direction. A low pressure refrigerant whose pressure is reduced by an expansion valve (not shown) flows into the inlet 21a.

  Further, a plurality of through holes (not shown) into which the upper end 22a2 (see FIG. 2) of the downwind side tube 22a is inserted are formed on the outer side surface of the lower side of the downwind side distribution tank 21. When the upper end 22a2 of the leeward tube 22a is inserted into the through hole, the internal flow passage of the leeward distribution tank 21 communicates with the leeward tube 22a. That is, the refrigerant flowing into the downwind side distribution tank 21 from the inflow port 21 a is distributed to the downwind side tubes 22 a.

  The downwind side collection tank 23 consists of a cylindrical member which has a flow path of a refrigerant inside. The downwind side accumulation tank 23 has the same volume as the upwind distribution tank 13, and the height position (Z direction position) of the bottom surface 232 a is substantially the same as the bottom surface 132 a of the upwind distribution tank 13. Both ends in the Y direction of the downwind side collective tank 23 are closed. As shown in FIG. 2, the downwind side collective tank 23 has two downwind side partitions 231 (first partition). The downwind side partition 231 has a plate shape having a flat surface substantially perpendicular to the Y direction, and is disposed in the upwind distribution tank 13 at intervals along the Y direction. Thus, three leeward side compartments 232 (first compartments) are formed in the leeward side collecting tank 23 along the Y direction.

  Each leeward partition wall 231 is disposed at a position corresponding to the windward partition wall 131 in the Y direction. That is, when the leeward-side partitions 231 are viewed along the X direction, the leeward-side partitions 231 are disposed at positions overlapping with the upwind-side partition 131.

  The downwind side partition wall 231 has a through hole 234 (water drain portion) formed in a part thereof. The through hole 234 has a circular cross section, and penetrates the downwind side partition wall 231 in the Y direction. Thereby, the leeward side partitions 231 and 231 adjacent to each other communicate with each other in the through hole 234.

  Further, a plurality of through holes (not shown) into which the lower end portion 22a1 (see FIG. 2) of the downwind side tube 22a is inserted are formed on the outer side surface of the upper portion of the downwind side collective tank 23. When the lower end portion 22a1 of the leeward tube 22a is inserted into the through hole, the internal flow passage of the leeward collecting tank 23 communicates with the leeward tube 22a. That is, the refrigerant flowing through the downwind side tubes 22 a and flowing out of the lower end portion 22 a 1 is collected in the downwind side compartments 232 of the downwind side collective tank 23.

  As shown in FIG. 2, six outlet ports 233 communicating with the downwind side compartments 232 are formed on the outer side surface of the downwind side collective tank 23. The discharge port 233 is an opening for discharging the refrigerant of each leeward side compartment 232 to the outside, and is formed two by two on the side face of each leeward side compartment 232. In the state of the refrigerant evaporator 1 shown in FIG. 1, one outlet 233 of the downwind side collective tank 23 and one inlet 133 of the upwind distribution tank 13 are in communication as a pair.

  Subsequently, the flow of the refrigerant supplied to the refrigerant evaporator 1 and the method of cooling the air will be described. The refrigerant reduced in pressure by the expansion valve (not shown) is supplied from the inlet 21 a into the downwind side distribution tank 21 as shown by arrow A in FIG. 2. The refrigerant is distributed in the downwind distribution tank 21 and flows into the downwind tubes 22a of the downwind core portion 22 as indicated by arrows B, C, and D.

  The refrigerant that has flowed into the downwind side tubes 22a flows in the inside in the -Z direction. At this time, the refrigerant flowing in each leeward tube 22a exchanges heat with the air flowing in the direction of the arrow X1 outside the leeward tube 22a via the wall surface of each leeward tube 22a. As a result, a part of the refrigerant evaporates to take heat from the air, thereby cooling the air.

  The refrigerant flowing in each leeward tube 22a of the leeward core portion 22 and flowing out from the lower end 22a1 of each leeward tube 22a is, as indicated by arrows E, F, and G, each leeward of the leeward collective tank 23. It flows into the side compartment 232. The refrigerant in the downwind side compartments 232 is discharged to the outside through the discharge port 233. The refrigerant in each downwind compartment 232 is split into two upwind compartments 132 as it is discharged through each outlet 233 as indicated by arrows H-M.

  The refrigerant discharged from the downwind side compartments 232 flows into the upwind side compartments 132 through the inlets 133 of the upwind distribution tank 13. Since each upwind compartment 132 is in communication with one inlet port 133, the refrigerant discharged from one downwind compartment 232 is distributed to the two upwind compartments 132.

  The refrigerant that has flowed into each upwind compartment 132 flows in the upwind compartment 132 in the Z direction, and is discharged from the upper through hole. The refrigerant | coolant discharged | emitted from the through-hole of each upwind compartment 132 is supplied to the upwind core part 12 as arrow N-S shows. The refrigerant flows in from the lower end portion 12a1 of each upwind side tube 12a, and flows in each upwind side tube 12a in the Z direction.

  The refrigerant flowing in the upwind tubes 12a and flowing out of the upper end 12a2 is collected in the upwind collecting tank 11 as shown by arrows T, U and V. The refrigerant collected in the upwind collecting tank 11 is supplied from the outlet 11a of the upwind collecting tank 11 to the suction side of the compressor (not shown) as shown by the arrow W.

  Subsequently, the flow of the refrigerant in the upwind distribution tank 13 and the downwind collective tank 23 will be described with reference to FIGS. 3 to 5.

  FIG. 3 shows the flow of the refrigerant when the flow rate of the refrigerant supplied to the refrigerant evaporator 1 is relatively large. As described above, when the flow rate of the refrigerant is relatively large, the shape and the like of the downwind side distribution tank 21 are set such that the flow rate of the refrigerant distributed from the downwind side distribution tank 21 and flowing in each downwind side tube 22a becomes substantially uniform. It is done.

  As shown in FIG. 3, the refrigerant that has flowed out from the lower end 22 a 1 of the downwind side tube 22 a flows into the downwind side compartment 232 of the downwind side collective tank 23. Because the flow rate is relatively large, the refrigerant collides with the bottom surface 232 a of the downwind side compartment 232 from above with a large water pressure. The interior of the downwind side compartment 232 is filled with a refrigerant.

  The cooling water that has collided with the bottom surface 232a flows along the bottom surface 232a so as to swirl around the through hole 234 and is led to the outlet 233 disposed above the bottom surface 232a. In the lower end 22a1 of the downwind side tube 22a, the refrigerant that has flowed out from a portion near the outlet 233 and flowed into the downwind side compartment 232 is drawn into the flow of the swirling refrigerant and is led to the outlet 233 .

  The refrigerant guided to the discharge port 233 is discharged from the leeward collecting tank 23. The refrigerant discharged from the downwind side collective tank 23 flows into the upwind side compartment 132 of the upwind distribution tank 13 via the inlet port 133.

  The refrigerant flowing into the upwind side compartment 132 flows upward and flows into the lower end portion 12a1 of the upwind side tube 12a. The refrigerant flows upward in the upwind tube 12a and is collected in the upwind collective tank 11 as described above.

  As described above, when the flow rate of the refrigerant supplied to the refrigerant evaporator 1 is relatively large, the refrigerant flowing into the downwind side compartment 232 is smoothly led to the discharge port 233. Therefore, most of the refrigerant in the downwind side compartment 232 is guided to the discharge port 233 and discharged from the downwind side collective tank 23 without passing through the through holes 234 of the downwind side partition 231. That is, when the flow rate of the supplied refrigerant is relatively large, the movement of the refrigerant between the adjacent downwind side compartments 232, 232 is relatively small.

  4 and 5 show the flow of the refrigerant when the flow rate of the refrigerant supplied to the refrigerant evaporator 1 is relatively small. Thus, when the flow rate of the refrigerant is relatively small, the flow rate of the refrigerant distributed from the downwind side distribution tank 21 to the downwind side tubes 22a tends to be uneven. More specifically, when the flow rate of the refrigerant flowing into the leeward distribution tank 21 from the inlet 21 a is relatively small, the refrigerant is difficult to be supplied to the back side in the leeward distribution tank 21. As a result, of the plurality of downwind tubes 22a of the downwind core portion 22, compared to the flow rate of the refrigerant flowing into the downwind tube 22a near the inflow port 21a, it flows into the downwind tube 22a far from the inflow port 21a. Flow rate of the refrigerant to be

  In this case, the flow rate of the refrigerant flowing out of the lower end portion 22a1 of the downwind side tube 22a and flowing into the downwind side compartments 232 of the downwind side collective tank 23 also becomes relatively small. Therefore, the refrigerant stagnates in the downwind side compartment 232 without being discharged smoothly from the downwind side collective tank 23.

  The water level of the refrigerant stagnating in this manner differs among the downwind side compartments 232. That is, as shown in FIG. 5, the level of the refrigerant is higher toward the downwind side compartment 232 where the refrigerant flows in from the downwind side tube 22a in the vicinity of the inflow port 21a (see FIGS. 1 and 2), The water level of the refrigerant decreases as the leeward-side compartment 232 flows into the refrigerant from the leeward tube 22a.

  When the water level of the refrigerant is different between the adjacent downwind side compartments 232 and 232 and the water level of the refrigerant exceeds the lower end 235 of the through hole 234 of the downwind side partition 231, the movement of the refrigerant through the through hole 234 It occurs. That is, as shown in FIG. 5, the refrigerant moves from the downwind side compartment 232 where the water level of the refrigerant is high to the downwind side compartment 232 where the water level of the refrigerant is low. As a result, the water level of the refrigerant remaining in the downwind side compartments 232 of the downwind side collective tank 23 is equalized.

  The refrigerant in the downwind side collective tank 23 flows into the upwind side compartments 132 of the upwind distribution tank 13 via the outlet 233 and the inlet 133. Since the refrigerant water level is uniformed in the leeward collecting tank 23, the amount of refrigerant flowing into each upwind compartment 132 is also equalized, and furthermore, the refrigerant in each upwind compartment 132 is each It is distributed to the upwind tube 12a. That is, the distribution of the refrigerant flowing through the upwind side tubes 12a is substantially uniform.

  As described above, according to the configuration of the refrigerant evaporator 1, when the flow rate of the refrigerant reaching the leeward side compartments 232 of the leeward side collective tank 23 is relatively large, the refrigerant is the leeward side compartments 232. The windward distribution tank 13 is supplied without stagnating therein. For this reason, the movement of the refrigerant between the leeward side compartments 232 and 232 adjacent to each other is hindered by the leeward side partition wall 231, and nonuniform distribution of the refrigerant can be suppressed.

  On the other hand, when the flow rate of the refrigerant reaching the downwind side compartments 232 of the downwind side collective tank 23 is relatively small, the refrigerant stays in the downwind side compartments 232 and the water level rises. When the water level of the refrigerant in one downwind side compartment 232 exceeds the lower end 235 of the through hole 234, the refrigerant moves into the other downwind side compartment 232 adjacent to the one downwind side compartment 232, and the refrigerant Are evenly distributed.

  Therefore, according to this configuration, it is possible to suppress uneven distribution of the refrigerant in the upwind core portion 12 regardless of the flow rate of the supplied refrigerant.

  Further, in the refrigerant evaporator 1, the downwind side partition wall 231 is formed with a through hole 234 penetrating in the Y direction.

  According to this configuration, when the flow rate of the supplied refrigerant is relatively large, the refrigerant flowing from the lower end portion 22a1 of each leeward tube 22a into one leeward side compartment 232 is swirled around the through hole 234 It can flow as. Thus, the refrigerant in one downwind side compartment 232 can be discharged toward the upwind distribution tank 13 while suppressing the movement to the other downwind side compartment 232 adjacent thereto.

  On the other hand, when the flow rate of the supplied refrigerant is relatively small, the refrigerant staying in one leeward side compartment 232 is moved to the other leeward side compartment 232 through the through hole 234, and each leeward side The water level of the refrigerant staying in the compartment 232 can be further equalized. That is, according to this configuration, it is possible to more reliably suppress the non-uniform distribution of the refrigerant in the upwind core portion 12.

  Further, in the refrigerant evaporator 1, the downwind side partition 231 and the upwind side partition 131 are disposed at corresponding positions in the Y direction.

  According to this configuration, when the refrigerant is supplied from the downwind side partitions 232 formed by the downwind side partition 231 to the upwind side partitions 132 formed by the upwind partition 131, the Y direction of the refrigerant It is possible to flow the refrigerant without largely changing the flow velocity component of Therefore, in each downwind side compartment 232, it is suppressed that the refrigerant flows in the Y direction and unnecessarily moves between upwind compartments 132 and 132, and the distribution of the refrigerant becomes even more uneven. It can be suppressed reliably.

  Further, in the refrigerant evaporator 1, the number of upwind compartments 132 (6) is larger than the number of downwind compartments 232 (3), and one downwind compartment 232 is plural (2) The refrigerant is supplied to the upwind side compartment 132 of

  According to this configuration, for example, the number of upwind tubes 12a communicating with one upwind compartment 132 is smaller than in the case where the number of upwind compartments 132 is three, the same as the number of downwind compartments 232. Become. Therefore, when the refrigerant is distributed from the upwind side compartment 132 to the plurality of upwind side tubes 12a, it is possible to more reliably suppress the uneven distribution of the refrigerant.

  Subsequently, a refrigerant evaporator 1A according to a first modified example will be described with reference to FIG. 6 shows a cross section of the refrigerant evaporator 1A, and shows a cross section corresponding to the III-III cross section of FIG. 1 in the refrigerant evaporator 1A. As in the first embodiment, the refrigerant evaporator 1A is mounted on a vehicle air conditioner that adjusts the temperature in a vehicle compartment, and is used for a refrigeration cycle. About the structure same as refrigerant | coolant evaporator 1 among refrigerant | coolant evaporator 1A, the same code | symbol is suitably attached and description is abbreviate | omitted.

  First, the refrigerant evaporator 1A differs from the refrigerant evaporator 1 in terms of its arrangement. That is, the refrigerant evaporator 1A is disposed in a state where the refrigerant evaporator 1 (not shown in FIG. 6) is rotated about the Y axis by a predetermined angle and inclined. Due to such an inclined arrangement, the discharge port 233 is located closer to the upper end of the leeward collecting tank 23.

  Further, the configuration of the refrigerant evaporator 1A is different from that of the refrigerant evaporator 1 in the point of the through holes 234A of the upwind side partition 231A. That is, the through hole 234A is not completely circular in cross section, but has a shape in which the lower part of the circle is lost. Thus, the lower end 235A of the through hole 234A is substantially horizontal and linear.

  As described above, in the refrigerant evaporator 1A, the downwind side evaporation unit 20 and the upwind side evaporation unit 10 rotate a predetermined angle around the Y axis such that the discharge port 233 is positioned closer to the upper end of the downwind side collective tank 23. Are arranged in an inclined manner. Thereby, the refrigerant which flowed out from lower end part 22a1 of leeward tube 22a can be preferentially collected to leeward side collection tank 23. As a result, when the flow rate of the supplied refrigerant is relatively small, the refrigerant is moved by the through holes 234A of the leeward partition 231A, and the water level of the refrigerant staying in each leeward side compartment 232 in the leeward collecting tank 23 is determined. It is possible to further equalize.

  Further, the lower end 235A of the through hole 234A is formed substantially horizontally. Thereby, when the water level of the refrigerant staying in each leeward side compartment 232 in the leeward side collective tank 23 exceeds the lower end 235A, the movement of the refrigerant between the adjacent leeward side compartments 232, 232 is rapidly performed. It becomes possible.

  Subsequently, a refrigerant evaporator 1B according to a second modification will be described with reference to FIG. FIG. 7 shows a cross section of the refrigerant evaporator 1B, and shows a cross section corresponding to the III-III cross section of FIG. 1 in the refrigerant evaporator 1B. The refrigerant evaporator 1B is mounted on a vehicle air conditioner that adjusts the temperature in the vehicle compartment, as in the above-described embodiment, and is used for a refrigeration cycle. About the structure same as the refrigerant evaporator 1 among the refrigerant evaporators 1B, the same code | symbol is suitably attached | subjected and description is abbreviate | omitted.

  First, the configuration of the refrigerant evaporator 1B differs from that of the refrigerant evaporator 1 in terms of the leeward collecting tank 23B. That is, in the refrigerant evaporator 1 (not shown in FIG. 6), the volume in the downwind side collective tank 23 is about the same as the volume in the upwind side distribution tank 13, while the refrigerant evaporator 1B is on the downwind side. The volume in the collecting tank 23 B is configured to be larger than the volume in the windward distribution tank 13. Specifically, the bottom surface 232Ba of the downwind side collective tank 23B is disposed in the −Z direction relative to the bottom face 132a of the upwind distribution tank 13, whereby the volume in the downwind side collective tank 23B is increased.

  According to such a refrigerant evaporator 1B, the refrigerant flowing out of the lower end 22a1 of the downwind side tube 22a can be preferentially collected in the downwind side collective tank 23B. As a result, the flow rate of the refrigerant supplied is relatively small, and the water level of the refrigerant is different between the adjacent downwind side compartments 232B and 232B, and the water level of the refrigerant is lower end 235B of the through hole 234B of the downwind side partition 231B. The refrigerant can be moved through the through hole 234B. As a result, it is possible to further equalize the water level of the refrigerant remaining in each leeward-side compartment 232B of the leeward-side collective tank 23B.

  Subsequently, a refrigerant evaporator 1C according to a second embodiment will be described with reference to FIGS. 8 and 9. The refrigerant evaporator 1 </ b> C is mounted on a vehicle air conditioner that adjusts the temperature in the vehicle compartment, as in the above-described embodiment, and is used for a refrigeration cycle. About the structure corresponding to the refrigerant evaporator 1 among 1 C of refrigerant evaporators, description is abbreviate | omitted suitably.

  The refrigerant evaporator 1C is a heat exchanger having a so-called Drone cup structure, and is configured by alternately stacking a plurality of plates 60 and a plurality of fins 70 in the Y direction. The refrigerant evaporator 1C is provided with an upwind side evaporation portion 10C and a downwind side evaporation portion 20C opposed in the air flow direction indicated by the arrow X2.

  As shown in FIG. 8, each plate 60 is configured by polymerizing one first plate 61 and one second plate 62 in the Y direction. Each of the first plate 61 and the second plate 62 is a metal plate on which an unevenness is formed. The shape of the first plate 61 is symmetrical to the shape of the second plate 62 in the Y direction. Therefore, in the following, the shape of the second plate 62 will be described, and the description of the shape of the first plate 61 will be omitted.

  As shown in FIG. 9, the second plate 62 has a windward tube 12Ca and a windward tube 22Ca. Both the upwind side tube 12Ca and the downwind side tube 22Ca are formed by projecting one metal plate in the Y direction. Further, although the upwind side tube 12Ca and the downwind side tube 22Ca are mostly separated from each other in the X direction by the separation wall 63, they communicate with each other through the discharge port 233C and the introduction port 133C in the vicinity of the lower end. ing.

  Further, communication holes 11Cb and 21Cb are formed in the upper part of the second plate 62. Each of the communication holes 11Cb and 21Cb is a hole that penetrates the metal plate in the Y direction, and is opposed to each other in the X direction with the separation wall 63 interposed therebetween. The communication hole 11Cb communicates with the windward tube 12Ca, and the communication hole 21Ca communicates with the windward tube 22Ca.

  Further, in the lower part of the second plate 62, a through hole 234C (water drainage part) is formed. The through hole 234C is a hole that penetrates the metal plate in the Y direction, and is formed at a portion closer to the bottom surface 232Ca in the downwind side tube 22Ca.

  The second plate 62 formed as described above and the first plate symmetrically formed with the second plate 62 are polymerized in the Y direction, so that the refrigerant is applied in the Z direction in each plate 60. An upwind side tube 12Ca and a downwind side tube 22Ca are formed as a flow path. The windward tube 12Ca constitutes the windward core portion 12C by laminating the plurality of plates 60 in the Y direction with the fins 70 interposed therebetween. Further, the downwind side tube 22Ca constitutes the downwind side core portion 22C by laminating the plurality of plates 60 in the Y direction with the fins 70 interposed therebetween.

  Further, by the plates 60 being stacked in the Y direction and adjacent to each other, the communication holes 11Cb and 11Cb communicate with each other to form the windward collecting portion 11C, and the communication holes 21Cb and 21Cb communicate with each other so as to leeward. The side distribution unit 21C is formed. As shown in FIG. 8, an exhaust port 11Ca in which an exhaust port 11Ca is formed at the end on the -Y direction side of the windward gathering portion 11C is connected to the suction side of a compressor not shown. Moreover, inflow port 21Ca is formed in the edge part at the side of-Y direction of downwind side distribution part 21C. A low pressure refrigerant whose pressure is reduced by an expansion valve (not shown) flows into the inflow port 21Ca.

  Further, by the plates 60 being stacked in the Y direction and adjacent to each other, a plurality of upwind side compartments 132C defined by the upwind side partition 131C are formed in the lower part thereof. The upwind-side partition 131C is a part of a projectingly formed metal plate. The windward distribution portion 13C is formed by arranging the plurality of windward compartments 132C along the Y direction.

  In addition, when the plates 60 are stacked in the Y direction and adjacent to each other, the through holes 234C and 234C communicate with each other. As a result, a plurality of downwind side compartments 232C which are separated by the downwind side partition 231C and communicate with each other in the through holes 234C are formed in the lower part of the plate 60. The downwind side partition wall 231C is a part of the metal plate formed to be protruded. Such a plurality of downwind side compartments 232C are arranged along the Y direction, whereby a downwind side collective portion 23C is formed.

  The upwind side evaporation section 10C described above is configured of an upwind side collecting section 11C, an upwind side core section 12C, and an upwind side distribution section 13C. The downwind side evaporation unit 20C is configured by the downwind side distribution unit 21C, the downwind side core unit 22C, and the downwind side distribution unit 23C.

  Subsequently, the flow of the refrigerant in the refrigerant evaporator 1C and the method of cooling the air will be described. The refrigerant decompressed by the expansion valve (not shown) is supplied from the inlet 21Ca into the downwind distribution unit 21C as shown by an arrow AC in FIG. The refrigerant is distributed in the downwind distribution unit 21C, and flows into the downwind tube 22Ca of the downwind core portion 22C of each plate 60.

  The refrigerant that has flowed into the downwind side tubes 22Ca flows in the inside in the -Z direction. At this time, the refrigerant flowing in the downwind side tubes 22Ca exchanges heat with the air flowing in the direction of the arrow X2 outside the downwind side tubes 22Ca via the wall surface of the plate 60. As a result, a part of the refrigerant evaporates to take heat from the air, thereby cooling the air.

  The refrigerant that has flowed through each leeward tube 22Ca of the leeward core portion 22C flows into each leeward side compartment 232C of the leeward collecting portion 23C. The refrigerant in the downwind side compartments 232C is discharged to the outside through the discharge port 233C.

  The refrigerant | coolant discharged | emitted from each discharge port 233C flows in in each windward side compartment 132C via each inlet port 133C of windward distribution part 13C. Since each upwind compartment 132C is in communication with one inlet port 133C, the refrigerant discharged from one downwind compartment 232C is supplied to one upwind compartment 132C.

  The refrigerant that has flowed into each upwind compartment 132C flows in the upwind compartment 132 in the Z direction, and is supplied to the upwind core portion 12C. The refrigerant flows through the upwind tubes 12Ca of the upwind core portion 12C in the Z direction.

  The refrigerant having flowed in the upwind tubes 12Ca is collected in the upwind collecting portion 11C. The refrigerant collected in the windward collecting portion 11C is discharged from the discharge port 11a via the communication hole 11Cb, and is supplied to the suction side of the compressor (not shown).

  In the refrigerant evaporator 1C configured as described above, when the flow rate of the supplied refrigerant is relatively small, the refrigerant stagnates in the downwind side compartment 232C. The water level of the refrigerant stagnating in this way is different for each leeward side compartment 232C of the leeward side collective portion 23C, and the leeward side compartment 232C where the refrigerant flows in from the leeward tube 22Ca near the inflow port 21Ca. The water level of the refrigerant becomes lower as the water level is higher and the refrigerant flows from the downwind side tube 22Ca far from the inflow port 21Ca to the downwind side compartment 232C.

  When the water level of the refrigerant is different between the adjacent downwind side compartments 232C and 232C and the water level of the refrigerant exceeds the lower end 235C of the through hole 234C of the downwind partition 231C, the movement of the refrigerant through the through hole 234C It occurs. That is, the refrigerant moves from the downwind side compartment 232C where the water level of the refrigerant is high to the downwind side compartment 232C where the water level of the refrigerant is low. As a result, the water level of the refrigerant remaining in the downwind side compartments 232C of the downwind side collecting portion 23C is equalized. As a result, non-uniform distribution of the refrigerant can be suppressed in the downwind side core portion 22C and the upwind side core portion 12C.

  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. That is, those to which those skilled in the art appropriately modify the design of these specific examples are also included in the scope of the present invention as long as they have the features of the present invention. The elements included in each of the specific examples described above and their arrangements, materials, conditions, shapes, sizes, and the like are not limited to those illustrated, and can be changed as appropriate.

  In the refrigerant evaporator 1B according to the second modification described above, in order to make the volume in the leeward collecting tank 23B larger than the volume in the leeward distributing tank 13, the bottom surface 232Ba of the leeward collecting tank 23B is upwind Although it arrange | positions to the-Z direction rather than the bottom face 132a of the distribution tank 13, this invention is not limited to this. For example, by separately connecting a tank communicating with the leeward collecting tank 23 to the leeward collecting tank 23 of the refrigerant evaporator 1 according to the first embodiment, the capacity in the leeward collecting tank 23 is substantially increased. It is also possible.

1, 1A, 1B, 1C: Refrigerant evaporator 10, 10C: Upwind evaporator (second evaporator)
11: Upwind collecting tank (second collecting part)
11C: Upwind collecting part (second collecting part)
12, 12C: Upwind core (second core)
12a, 12Ca: Upwind tube (second tube)
13: Upwind distribution tank (second distribution unit)
13C: Upwind distribution unit (second distribution unit)
131, 131 C: Upwind bulkhead (second bulkhead)
132, 132C: Upwind compartment (second compartment)
20, 20C: downwind side evaporation section (first evaporation section)
21: Downwind side distribution tank (first distribution unit)
21C: downwind distribution unit (first distribution unit)
22, 22C: downwind side core (first core)
22a, 22Ca: Downwind side tube (first tube)
23, 23 B: downwind side collecting tank (first collecting part)
23C: downwind side assembly (first assembly)
231, 231A, 231B, 231C: downwind side partition wall (first partition wall)
232, 232B, 232C: downwind compartment (first compartment)
234, 234A, 234B, 234C: through holes (water drainage part)

Claims (8)

It has the 1st evaporation part (20, 20C) and the 2nd evaporation part (10, 10C) which were arranged so that it might face each other in the flow direction of a to-be-cooled fluid, and heat exchange between to-be-cooled fluid and a refrigerant Refrigerant evaporators (1, 1A, 1B, 1C) that
The first evaporation unit is
A first core portion (22, 22C) configured by laminating in a first direction a plurality of first tubes (22a, 22Ca) for flowing the refrigerant downward;
A first distribution unit (21, 21C) disposed above the first core portion to flow the refrigerant along the first direction and distribute the refrigerant to flow from the upper end portions of the plurality of first tubes )When,
And a first collecting portion (23, 23B, 23C) disposed below the first core portion and collecting the refrigerant flowing out from lower ends of the plurality of first tubes,
The second evaporation unit is
A second core portion (12, 12C) configured by laminating a plurality of second tubes (12a, 12Ca) for flowing the refrigerant upward in the first direction;
A second distribution unit (13, disposed below the second core unit and receiving the supply of the refrigerant from the first collecting unit and distributing the refrigerant from the lower end portions of the plurality of second tubes. 13C),
And a second collecting portion (11, 11C) disposed above the second core portion and collecting the refrigerant flowing out from the upper end portions of the plurality of second tubes,
The first collective portion is divided by a plurality of first partitions (231, 231A, 231B, 231C) arranged at predetermined intervals so as to be arranged along the first direction, and the plurality of first partitions. And a plurality of first compartments (232, 232B, 232C) formed;
The second distribution unit is sectioned by a plurality of second partitions (131, 131C) arranged at predetermined intervals so as to be aligned along the first direction, and the plurality of second partitions , and And a plurality of second compartments (132, 132C) formed as mutually independent spaces ,
The first partition moves the refrigerant to the other first compartment adjacent to the one first compartment when the water level of the one first compartment exceeds the predetermined water level. What is claimed is: 1. A refrigerant evaporator comprising a water draining portion (234, 234A, 234B, 234C).   The refrigerant evaporator according to claim 1, wherein the first partition has a through hole (234, 234A, 234B, 234C) penetrating in the first direction.   The refrigerant evaporator according to claim 1, wherein the first partition and the second partition are disposed at corresponding positions in the first direction. The number of second compartments is greater than the number of first compartments,
The refrigerant evaporator according to claim 1, wherein one of the first compartments supplies a refrigerant to the plurality of second compartments. The first collecting portion has an outlet (233) for discharging the refrigerant,
The first evaporation portion and the second evaporation portion are disposed to be inclined at a predetermined angle around an axis extending in the first direction such that the discharge port is positioned closer to the upper end portion of the first collecting portion. The refrigerant evaporator according to claim 1, characterized in that: The first barrier rib 231A is formed with a through hole 234A penetrating in the first direction.
The refrigerant evaporator according to claim 2, wherein the lower end (235A) of the through hole is formed substantially horizontally.   The refrigerant evaporator according to claim 1, wherein a volume of the first collecting portion (23B) is larger than a volume of the second distributing portion (13).   The refrigerant evaporator according to claim 7, wherein the bottom surface (232a, 232Ba) of the first collecting portion is disposed lower than the bottom surface of the second distribution portion (132a).

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