JP2014219176A - Refrigerant evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant evaporator capable of suppressing degradation in refrigerant distributivity.SOLUTION: A refrigerant evaporator 1 is configured so that a first refrigerant assembly unit 23a formed within a second leeward tank unit 23 is coupled to a second refrigerant distribution unit 13b formed within a second windward tank unit 13, a second refrigerant assembly unit 23b formed within the second leeward tank unit 23 is coupled to a first refrigerant distribution unit 13a formed within the second windward tank unit 13, and a flow direction of a refrigerant is switched depending on a core width direction of each of heat exchanger core parts 11 and 21. The number of first refrigerant outlet ports 24b for flowing out the refrigerant within the second refrigerant assembly unit 23b to the first refrigerant distribution unit 13a differs from the number of first refrigerant inlet ports 14a for flowing the refrigerant from the second refrigerant assembly unit 23b into the first refrigerant distribution unit 13a.

Description

  The present invention relates to a refrigerant evaporator that cools a fluid to be cooled by absorbing heat from the fluid to be cooled and evaporating the refrigerant.

  The refrigerant evaporator functions as a cooling heat exchanger that cools the fluid to be cooled by absorbing heat from the fluid to be cooled (for example, air) flowing outside and evaporating the refrigerant (liquid phase refrigerant) flowing inside. .

  As this type of refrigerant evaporator, the first and second evaporation parts including a heat exchange core part formed by laminating a plurality of tubes and a pair of tank parts connected to both ends of the plurality of tubes are covered. A configuration is known in which the tanks are arranged in series in the flow direction of the cooling fluid, and one tank unit in each evaporation unit is connected via a pair of communication units (see, for example, Patent Document 1).

  In the refrigerant evaporator of Patent Document 1, the refrigerant that has flowed through the heat exchange core portion of the first evaporation portion is secondly passed through one tank portion of each evaporation portion and a pair of communication portions that connect the tank portions. When flowing through the heat exchange core part of the evaporation part, the refrigerant flow is changed in the width direction (left-right direction) of the heat exchange core part. That is, in the refrigerant evaporator, the refrigerant flowing on one side in the width direction of the heat exchange core portion of the first evaporation portion is caused to flow in the width direction of the heat exchange core portion of the second evaporation portion by one of the pair of communication portions. The refrigerant is caused to flow to the other side, and the refrigerant flowing on the other side in the width direction of the heat exchange core part of the first evaporation part is caused to flow to one side in the width direction of the heat exchange core part of the second evaporation part. Yes.

Japanese Patent No. 4124136

  Here, the refrigerant evaporator described in Patent Document 1 is a communication in which the refrigerant flowing on one side in the width direction of the heat exchange core part of the first evaporation part flows to the other side in the width direction of the heat exchange core part of the second evaporation part. And a communication portion that allows the refrigerant flowing on the other side in the width direction of the heat exchange core portion of the first evaporation portion to flow to one side in the width direction of the heat exchange core portion of the second evaporation portion, respectively. .

  For this reason, the pressure loss of the refrigerant increases in proportion to the length of the distance between the refrigerant inlet and the tube end portion, which is the connection portion of the tank portion with the communication portion, and the amount of refrigerant flowing into the tube decreases. As a result, the liquid-phase refrigerant is unevenly distributed in the heat exchange core part, and there is a possibility that a temperature distribution is generated in the blown air passing through the refrigerant evaporator.

  An object of this invention is to provide the refrigerant | coolant evaporator which can suppress the deterioration of the distribution of a refrigerant | coolant in view of the said point.

  In order to achieve the above object, in the refrigerant evaporator for exchanging heat between the cooled fluid flowing outside and the refrigerant, the first evaporator (20) arranged in series with respect to the flow direction of the cooled fluid, and A heat exchange core unit including a second evaporation unit (10), and each of the first evaporation unit (20) and the second evaporation unit (10) is configured by stacking a plurality of tubes (111, 211) through which a refrigerant flows. (11, 21) and a pair of tank parts (12, 13, 22, and 2) connected to both ends of the plurality of tubes (111, 211) and collecting or distributing refrigerant flowing through the plurality of tubes (111, 211). 23), and the heat exchange core part (21) in the first evaporation part (20) is a first core part (21a) constituted by a part of the tube group among the plurality of tubes (211). And the remaining tube group The heat exchange core part (11) in the second evaporation part (10) is a first core part (11) in the flow direction of the fluid to be cooled among the plurality of tubes (111). 21a) and a third core part (11a) constituted by a tube group opposed to at least a part of the tube, and a tube group opposed to at least a part of the second core part (21b) in the flow direction of the fluid to be cooled. Among the pair of tank parts (22, 23) in the first evaporation part (20), one tank part (23) is from the first core part (21a). A first refrigerant collecting part (23a) for collecting refrigerant and a second refrigerant collecting part (23b) for collecting refrigerant from the second core part (21b) are included, and a pair of second evaporator parts (10) Of the tank parts (12, 13) The first tank part (13) distributes the refrigerant to the third core part (11a), and the second refrigerant distribution part (13b) distributes the refrigerant to the fourth core part (11b). The first evaporation section (20) and the second evaporation section (10) are configured to include a first communication section (31a) that guides the refrigerant of the first refrigerant assembly section (23a) to the second refrigerant distribution section (13b). , 32b, 33a) and the refrigerant replacement part (30) having the second communication part (31b, 32a, 33b) for guiding the refrigerant of the second refrigerant assembly part (23b) to the first refrigerant distribution part (13a). The first refrigerant distribution section (13a) is connected to the second communication section (31b, 32a, 33b), and the refrigerant from the second refrigerant assembly section (23b) is distributed to the first refrigerant distribution section (13a). The refrigerant inlet (14a) is provided to flow into the section (13a). Thus, the second refrigerant collecting portion (23b) is connected to the second communication portion (31b, 32a, 33b), and the refrigerant in the second refrigerant collecting portion (23b) is transferred to the first refrigerant distributing portion (13a). ), And the number of the refrigerant outlet (24b) is different from that of the refrigerant inlet (14a).

  According to this, the refrigerant outlet (24b) that causes the refrigerant in the second refrigerant assembly (23b) to flow out to the first refrigerant distributor (13a) and the refrigerant from the second refrigerant assembly (23b) are the first. Since the number of refrigerant inlets (14a) that flow into the refrigerant distributor (13a) is different, the refrigerant flow path that flows out of the second refrigerant assembly (23b) and flows into the first refrigerant distributor 13a is halfway It will branch at. For this reason, since the pressure loss of the refrigerant | coolant which distribute | circulates the said refrigerant | coolant flow path can be reduced, it becomes possible to suppress that a liquid phase refrigerant is distributed unevenly in the 3rd core part (11a). Therefore, it is possible to suppress a decrease in the cooling performance of the fluid to be cooled in the refrigerant evaporator.

  In the invention according to claim 2, in the refrigerant evaporator that performs heat exchange between the fluid to be cooled flowing outside and the refrigerant, the first evaporator disposed in series with respect to the flow direction of the fluid to be cooled (20) and the second evaporation section (10), each of the first evaporation section (20) and the second evaporation section (10) is configured by laminating a plurality of tubes (111, 211) through which refrigerant flows. A heat exchange core (11, 21) and a pair of tanks (12, 12) connected to both ends of the plurality of tubes (111, 211) and collecting or distributing refrigerant flowing through the tubes (111, 211) 13, 22, 23), and the heat exchange core section (21) in the first evaporation section (20) is a first core configured by a part of the tube group among the plurality of tubes (211). Part (21a) and the remaining tube The heat exchange core part (11) in the second evaporation part (10) is a first core in the flow direction of the fluid to be cooled among the plurality of tubes (111). A third core portion (11a) composed of a tube group facing at least a portion of the core portion (21a), and a tube group facing at least a portion of the second core portion (21b) in the flow direction of the fluid to be cooled. Among the pair of tank parts (22, 23) in the first evaporation part (20), one tank part (23) has the first core part (21a). ) Including a first refrigerant collecting portion (23a) for collecting refrigerant from the second core portion (21b) and a second refrigerant collecting portion (23b) for collecting refrigerant from the second core portion (21b). A pair of tank parts (12, 13) in Among these, one tank part (13) is a 1st refrigerant | coolant distribution part (13a) which distributes a refrigerant | coolant to a 3rd core part (11a), and a 2nd refrigerant | coolant distribution part (the refrigerant | coolant is distributed to a 4th core part (11b)). 13b), and the first evaporation section (20) and the second evaporation section (10) are the first communication section that guides the refrigerant of the first refrigerant assembly section (23a) to the second refrigerant distribution section (13b). (31a, 32b, 33a) and a refrigerant replacement part (30) having a second communication part (31b, 32a, 33b) for guiding the refrigerant of the second refrigerant assembly part (23b) to the first refrigerant distribution part (13a). The first refrigerant distribution part (13a) is connected to the second communication part (31b, 32a, 33b), and the refrigerant from the second refrigerant assembly part (23b) is supplied to the first refrigerant distribution part (13a). Plural refrigerant inlets (14a) to be introduced into the refrigerant distributor (13a) It is provided.

  According to this, the first refrigerant distribution part (13a) is provided with a plurality of refrigerant inlets (14a) through which the refrigerant from the second core part (21b) flows into the first refrigerant distribution part (13a). Therefore, compared with the case where one refrigerant inlet (14a) is provided, the distance from the end of the tube (111) farthest from the refrigerant inlet (14a) to the refrigerant inlet (14a) Can be shortened.

  Here, the shorter the distance between the refrigerant inlet (14a) and the end of the tube (111), the smaller the pressure loss of the refrigerant and the greater the amount of refrigerant flowing into the tube (111). For this reason, compared with the case where one refrigerant inlet (14a) is provided, the distance from the end of the tube (111) farthest from the refrigerant inlet (14a) to the refrigerant inlet (14a) By shortening, the amount of refrigerant flowing into the tube (111) increases. Thereby, since the deviation of the refrigerant amount flowing into each tube (111) can be reduced, it is possible to suppress the uneven distribution of the liquid-phase refrigerant in the third core portion (11a). Therefore, it is possible to suppress a decrease in the cooling performance of the fluid to be cooled in the refrigerant evaporator.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a typical perspective view of the refrigerant evaporator concerning a 1st embodiment. It is a disassembled perspective view of the refrigerant evaporator shown in FIG. It is explanatory drawing for demonstrating the positional relationship of the some tube which comprises each core part of the windward heat exchange core part which concerns on 1st Embodiment, and each refrigerant | coolant inflow port. It is a typical perspective view of the intermediate tank part in a 1st embodiment. It is a disassembled perspective view of the intermediate tank part shown in FIG. It is explanatory drawing for demonstrating the flow of the refrigerant | coolant in the refrigerant evaporator which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the positional relationship of the some tube which comprises each core part of the windward heat exchange core part which concerns on 2nd Embodiment, and each refrigerant | coolant inflow port. It is explanatory drawing for demonstrating the positional relationship of the some tube which comprises each core part of the windward heat exchange core part which concerns on 3rd Embodiment, and each refrigerant | coolant inflow port.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. The refrigerant evaporator 1 according to the present embodiment is applied to a vapor compression refrigeration cycle of a vehicle air conditioner that adjusts the temperature in the passenger compartment, and absorbs heat from the blown air that is blown into the passenger compartment to form a refrigerant (liquid phase refrigerant). It is a heat exchanger for cooling which cools blowing air by evaporating. In the present embodiment, the blown air corresponds to the “cooled fluid flowing outside” in the claims.

  As is well known, the refrigeration cycle includes a compressor, a radiator (condenser), an expansion valve, and the like (not shown) in addition to the refrigerant evaporator 1, and in this embodiment, liquid is received between the radiator and the expansion valve. It is configured as a receiver cycle in which a device is arranged. The refrigerant of the refrigeration cycle is mixed with refrigeration oil for lubricating the compressor, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.

  Here, in FIG. 2, illustration of the tubes 111 and 211 and the fins 112 and 212 in each heat exchange core part 11 and 21 mentioned later is abbreviate | omitted.

  As shown in FIGS. 1 and 2, the refrigerant evaporator 1 according to the present embodiment includes two evaporators 10 and 20 arranged in series with respect to the flow direction (flow direction of the fluid to be cooled) X of the blown air. It is prepared for. Here, in this embodiment, the evaporation part arrange | positioned among the two evaporation parts 10 and 20 on the windward side (upstream side) of the air flow direction of blowing air is called the windward evaporation part 10, and the flow of blowing air The evaporator disposed on the leeward side (downstream side) in the direction is referred to as a leeward evaporator 20. The upwind evaporator 10 in the present embodiment constitutes the “second evaporator” in the claims, and the downwind evaporator 20 constitutes the “first evaporator” in the claims. Yes.

  The basic configurations of the windward side evaporator 10 and the leeward side evaporator 20 are the same, and the heat exchange core parts 11 and 21 and a pair of tank parts 12 disposed on the upper and lower sides of the heat exchange core parts 11 and 21, respectively. 13, 22, and 23.

  In the present embodiment, the heat exchange core part in the windward evaporator 10 is referred to as the windward heat exchange core part 11, and the heat exchange core part in the leeward evaporator 20 is referred to as the leeward heat exchange core part 21. Of the pair of tank portions 12 and 13 in the windward side evaporation unit 10, the tank portion disposed on the upper side is referred to as a first windward tank portion 12, and the tank portion disposed on the lower side is referred to as the second windward side. This is referred to as a tank portion 13. Similarly, of the pair of tank parts 22 and 23 in the leeward side evaporation part 20, the tank part arranged on the upper side is referred to as the first leeward side tank part 22, and the tank part arranged on the lower side is referred to as the second leeward side. This is referred to as a side tank portion 23.

  Each of the windward side heat exchange core part 11 and the leeward side heat exchange core part 21 of the present embodiment includes a plurality of tubes 111 and 211 extending in the vertical direction and fins 112 and 212 joined between the adjacent tubes 111 and 211. And a laminate in which layers are alternately arranged. Hereinafter, the stacking direction in the stacked body of the plurality of tubes 111 and 211 and the plurality of fins 112 and 212 is referred to as a tube stacking direction.

  Here, the windward side heat exchange core part 11 is the 2nd wind comprised by the 1st windward heat exchange core part 11a comprised by some tube groups among the some tubes 111, and the remaining tube group. It has the upper side heat exchange core part 11b. In addition, the 1st windward heat exchange core part 11a in this embodiment comprises the "3rd core part" in a claim, and the 2nd windward heat exchange core part 11b is the "first" in a claim. 4 core part "is comprised.

  In the present embodiment, when the windward heat exchange core part 11 is viewed from the flow direction of the blown air, the first windward heat exchange core part 11a is configured by a tube group existing on the right side of the tube lamination direction, and the tube lamination direction The second upwind heat exchange core portion 11b is configured by a tube group existing on the left side of the above.

  Moreover, the leeward side heat exchange core part 21 is the 2nd leeward side comprised by the 1st leeward side heat exchange core part 21a comprised by some tube groups among the some tubes 211, and the remaining tube group. It has a heat exchange core portion 21b. In addition, the 1st leeward side heat exchange core part 21a in this embodiment comprises the "1st core part" in a claim, and the 2nd leeward side heat exchange core part 21b is the "first" in a claim. 2 core part "is comprised.

  In this embodiment, when the leeward heat exchange core portion 21 is viewed from the flow direction of the blown air, the first leeward heat exchange core portion 21a is configured by a tube group existing on the right side of the tube lamination direction, and the tube lamination direction The second leeward heat exchange core portion 21b is configured by a tube group existing on the left side of the leeward side. In the present embodiment, the first windward side heat exchange core portion 11a and the first leeward side heat exchange core portion 21a are arranged so as to overlap (opposite) when viewed from the flow direction of the blown air. The second leeward side heat exchange core part 11b and the second leeward side heat exchange core part 21b are arranged so as to overlap (oppose) each other.

  Each of the tubes 111 and 211 includes a flat tube in which a refrigerant passage through which a refrigerant flows is formed and a cross-sectional shape thereof is a flat shape extending along the flow direction of the blown air.

  The tube 111 of the windward side heat exchange core part 11 has one end side (upper end side) in the longitudinal direction connected to the first windward tank part 12, and the other end side (lower end side) in the longitudinal direction is the second windward side. It is connected to the tank unit 13. The tube 211 of the leeward heat exchange core portion 21 has one end side (upper end side) in the longitudinal direction connected to the first leeward tank portion 22 and the other end side (lower end side) in the longitudinal direction is second. The leeward tank unit 23 is connected.

  Each of the fins 112 and 212 is a corrugated fin formed by bending a thin plate material into a wave, joined to the flat outer surface side of the tubes 111 and 211, and heat for expanding the heat transfer area between the blown air and the refrigerant. It constitutes an exchange promoting means.

  In the laminated body of the tubes 111 and 211 and the fins 112 and 212, side plates 113 and 213 that reinforce the heat exchange core parts 11 and 12 are arranged at both ends in the tube lamination direction. The side plates 113 and 213 are joined to the fins 112 and 212 arranged on the outermost side in the tube stacking direction.

  The first upwind tank unit 12 is closed at one end (the left end when viewed from the flow direction of the blown air) and at the other end (the right end when viewed from the flow direction of the blown air). Further, it is constituted by a cylindrical member in which a refrigerant derivation part 12a for deriving the refrigerant from the inside of the tank to the suction side of a compressor (not shown) is formed. The first upwind tank unit 12 has a through hole (not shown) in which one end side (upper end side) of each tube 111 is inserted and joined at the bottom. That is, the first upwind tank unit 12 is configured such that the internal space thereof communicates with each tube 111 of the upwind heat exchange core unit 11, and the core units 11 a and 11 b of the upwind heat exchange core unit 11. It functions as a refrigerant collecting part that collects the refrigerant from.

  The first leeward tank unit 22 is closed at one end, and has a cylinder formed with a refrigerant introduction unit 22a for introducing low-pressure refrigerant decompressed by an expansion valve (not shown) into the tank at the other end. It is comprised by the shape-shaped member. The first leeward tank portion 22 has a through hole (not shown) in which one end side (upper end side) of each tube 211 is inserted and joined at the bottom. That is, the 1st leeward side tank part 22 is comprised so that the internal space may connect with each tube 211 of the leeward side heat exchange core part 21, and each core part 21a, 21b of the leeward side heat exchange core part 21 is comprised. It functions as a refrigerant distribution unit that distributes the refrigerant.

  The 2nd windward side tank part 13 is comprised with the cylindrical member by which the both end sides were obstruct | occluded. The second upwind tank portion 13 has a through hole (not shown) in which the other end side (lower end side) of each tube 111 is inserted and joined to the ceiling portion. That is, the second upwind tank unit 13 is configured such that its internal space communicates with each tube 111.

  In addition, a partition member 131 is disposed at the center in the longitudinal direction inside the second upwind tank unit 13, and the tank internal space forms the first upwind heat exchange core unit 11a by the partition member 131. Are divided into a space where the tubes 111 communicate with each other and a space where the tubes 111 constituting the second upwind heat exchange core portion 11b communicate with each other.

  Here, in the inside of the second upwind tank unit 13, the space communicating with each tube 111 constituting the first upwind heat exchange core unit 11a distributes the refrigerant to the first upwind heat exchange core unit 11a. A second refrigerant distributor that constitutes the first refrigerant distributor 13a and that communicates with the tubes 111 constituting the second windward heat exchange core 11b distributes the refrigerant to the second windward heat exchange core 11b. 13b is constituted.

  The 2nd leeward side tank part 23 is comprised with the cylindrical member by which the both end sides were obstruct | occluded. The second leeward tank portion 23 has a through hole (not shown) in which the other end side (lower end side) of each tube 211 is inserted and joined to the ceiling portion. That is, the second leeward tank unit 23 is configured such that the internal space thereof communicates with each tube 211.

  Inside the second leeward tank part 23, a partition member 231 is arranged at a central position in the longitudinal direction. By this partition member 231, the tank internal space constitutes the first leeward heat exchange core part 21a. It is partitioned into a space in which the tubes 211 communicate with each other and a space in which the tubes 211 constituting the second leeward heat exchange core portion 21b communicate with each other.

  Here, in the inside of the second leeward side tank part 23, the space communicating with each tube 211 constituting the first leeward side heat exchange core part 21a collects the refrigerant from the first leeward side heat exchange core part 21a. The second refrigerant that constitutes the first refrigerant collecting portion 23a to be communicated and in which the space where the tubes 211 constituting the second leeward heat exchange core portion 21b communicate with each other collects refrigerant from the second leeward heat exchange core portion 21b. The aggregation unit 23b is configured.

  Each of the second leeward tank unit 13 and the second leeward tank unit 23 is connected via a refrigerant replacement unit 30. The refrigerant replacement unit 30 guides the refrigerant in the first refrigerant collecting unit 23 a in the second leeward tank unit 23 to the second refrigerant distribution unit 13 b in the second leeward tank unit 13 and also the second leeward tank unit 23. The refrigerant in the second refrigerant collecting portion 23b is guided to the first refrigerant distributing portion 13a in the second upwind tank portion 13. That is, the refrigerant replacement unit 30 is configured to replace the refrigerant flow in the core width direction in each of the heat exchange core units 11 and 21.

  Specifically, the refrigerant replacement part 30 includes a pair of collecting part connecting members 31a and 31b connected to the first and second refrigerant collecting parts 23a and 23b in the second leeward tank part 23, and a second windward tank. Are connected to two pairs of distributor connecting members 32a and 32b connected to the respective refrigerant distributors 13a and 13b in the portion 13, a pair of aggregate connecting members 31a and 31b, and two pairs of distributor connecting members 32a and 32b. And an intermediate tank portion 33.

  Each of the pair of collecting portion connecting members 31a and 31b is configured by a cylindrical member in which a refrigerant flow passage through which a refrigerant flows is formed, and one end side thereof is connected to the second leeward tank portion 23. The other end side is connected to the intermediate tank portion 33.

  The first collecting portion connecting member 31a constituting one of the pair of collecting portion connecting members 31a and 31b is connected to the second leeward tank portion 23 so that one end side thereof communicates with the first refrigerant collecting portion 23a. The other end side is connected to the intermediate tank portion 33 so as to communicate with a first refrigerant flow passage 33a in the intermediate tank portion 33 described later.

  Further, the second collecting portion connecting member 31b constituting the other is connected to the second leeward tank portion 23 so that one end side thereof communicates with the second refrigerant collecting portion 23b, and the other end side is an intermediate tank portion 33 described later. It is connected to the intermediate tank portion 33 so as to communicate with the second refrigerant flow passage 33b.

  In the present embodiment, one end side of the first collecting portion connecting member 31a is connected to a position near the partition member 231 in the first refrigerant collecting portion 23a, and one end side of the second collecting portion connecting member 31b is the second refrigerant set. The part 23b is connected to a position close to the closed end of the second leeward tank part 23.

  Each of the two pairs of distributor connecting members 32a and 32b is formed of a cylindrical member in which a refrigerant flow passage through which a refrigerant flows is formed, and one end side thereof is connected to the second upwind tank unit 13. At the same time, the other end side is connected to the intermediate tank portion 33.

  Of the two pairs of distribution part connection members 32a and 32b, the two first distribution part connection members 32a constituting one of the second windward side tank parts 13 each have one end communicating with the first refrigerant distribution part 13a. The other end side is connected to the intermediate tank part 33 so as to communicate with a second refrigerant flow passage 33b in the intermediate tank part 33 described later. In other words, the two first distribution part connecting members 32a communicate with the above-described second collecting part connecting member 31b via the second refrigerant flow passage 33b of the intermediate tank part 33, respectively.

  In addition, each of the two second distributor connecting members 32b constituting the other is connected to the second windward tank 13 so that one end thereof communicates with the second refrigerant distributor 13b, and the other end will be described later. The intermediate tank 33 is connected to the intermediate tank 33 so as to communicate with the first refrigerant flow passage 33 a in the intermediate tank 33. In other words, the two second distribution part connecting members 32 b communicate with the above-described first collecting part connecting member 31 a via the first refrigerant flow passage 33 a of the intermediate tank part 33.

  Of the two first distributor connecting members 32a, one end of one first distributor connecting member 32a is connected to the end of the first refrigerant distributor 13a on the side close to the refrigerant outlet 12a in the tube stacking direction. Has been. Further, one end side of the other first distribution portion connecting member 32a is connected to an end portion of the first refrigerant distribution portion 13a that is far from the refrigerant outlet portion 12a in the tube stacking direction.

  Of the two second distribution portion connecting members 32b, one end side of one second distribution portion connecting member 32b is connected to the end portion of the second refrigerant distribution portion 13b on the side close to the refrigerant outlet portion 12a in the tube stacking direction. Has been. In addition, one end side of the other second distribution portion connecting member 32b is connected to an end portion of the second refrigerant distribution portion 13b that is far from the refrigerant outlet portion 12a in the tube stacking direction.

  A first refrigerant outlet 24a is connected to the second leeward tank unit 23, and the refrigerant from the first refrigerant assembly part 23a flows out to the first aggregate connection member 31a while being connected to the first ensemble connection member 31a. And the 2nd refrigerant | coolant outlet 24b which flows out a refrigerant | coolant from the 2nd refrigerant | coolant aggregate part 23b to the 2nd aggregate part connection member 31b while the 2nd aggregate part connection member 31b is connected is formed.

  As shown in FIGS. 2 and 3, the first windward tank unit 13 is connected to the first distribution unit coupling member 32a and the refrigerant from the first distribution unit coupling member 32a is supplied to the first refrigerant distribution unit 13a. The two first refrigerant inflow ports 14a and the second distribution part connecting member 32b are connected to each other, and the two refrigerants from the second distribution part connecting member 32b are supplied to the second refrigerant distribution part 13b. Two refrigerant inlets 14b are formed.

  Of the two first refrigerant inlets 14a, one first refrigerant inlet 14a is provided at the end of the first refrigerant distributor 13a on the side close to the refrigerant outlet 12a in the tube stacking direction. The other first refrigerant inlet 14a is provided at the end of the first refrigerant distributor 13a that is far from the refrigerant outlet 12a in the tube stacking direction.

  Of the two second refrigerant inlets 14b, one second refrigerant inlet 14b is provided at an end of the second refrigerant distribution part 13b on the side close to the refrigerant outlet 12a in the tube stacking direction. The other second refrigerant inlet 14b is provided at the end of the second refrigerant distributor 13b far from the refrigerant outlet 12a in the tube stacking direction.

  Returning to FIG. 2, the intermediate tank portion 33 is composed of a cylindrical member whose both ends are closed. The intermediate tank portion 33 is disposed between the second leeward tank portion 13 and the second leeward tank portion 23. Specifically, when viewed from the flow direction X of the blown air, the intermediate tank portion 33 of the present embodiment has a part (upper side portion) of the second windward side tank portion 13 and the second leeward side. It arrange | positions so that it may superimpose with the tank part 23 and the other part (lower site | part) may not superimpose with the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23. FIG.

  Thus, if it is set as the structure arrange | positioned so that a part of intermediate | middle tank part 33 may not superimpose with the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23, in the flow direction X of blowing air, the 1st Since the evaporator 10 and the second evaporator 20 can be arranged close to each other, an increase in the size of the refrigerant evaporator 1 due to the provision of the intermediate tank 33 can be suppressed.

  As shown in FIGS. 4 and 5, a partition member 331 is disposed inside the intermediate tank portion 33 at a position located on the upper side, and the partition member 331 allows the space inside the tank to flow through the first refrigerant. It is partitioned into a passage 33a and a second refrigerant flow passage 33b.

  The 1st refrigerant | coolant flow path 33a comprises the refrigerant | coolant flow path which guide | induces the refrigerant | coolant from the 1st gathering part connection member 31a to the 2nd distribution part connection member 32b. On the other hand, the second refrigerant flow passage 33b constitutes a refrigerant flow passage that guides the refrigerant from the second collecting portion connecting member 31b to the first distribution portion connecting member 32a.

  Here, in this embodiment, the 1st refrigerant | coolant flow path 33a in the 1st gathering part connection member 31a, the 2nd distribution part connection member 32b, and the intermediate tank part 33 is "the 1st communication part" as described in a claim. Is configured. Moreover, the 2nd refrigerant | coolant flow path 33b in the 2nd gathering part connection member 31b, the 1st distribution part connection member 32a, and the intermediate | middle tank part 33 comprises the "2nd communication part" as described in a claim.

  Next, the flow of the refrigerant in the refrigerant evaporator 1 according to this embodiment will be described with reference to FIG.

  As shown in FIG. 6, the low-pressure refrigerant decompressed by an expansion valve (not shown) is introduced into the tank from a refrigerant introduction part 22a formed on one end side of the first leeward tank part 22 as indicated by an arrow A. The The refrigerant introduced into the first leeward tank unit 22 descends the first leeward heat exchange core portion 21a of the leeward heat exchange core portion 21 as indicated by an arrow B, and at the same time leeward heat exchange as indicated by an arrow C. The second leeward heat exchange core portion 21b of the core portion 21 is lowered.

  The refrigerant descending the first leeward heat exchange core portion 21a flows into the first refrigerant collecting portion 23a of the second leeward tank portion 23 as indicated by an arrow D. On the other hand, the refrigerant descending the second leeward heat exchange core portion 21b flows into the second refrigerant collecting portion 23b of the second leeward tank portion 23 as indicated by an arrow E.

  The refrigerant flowing into the first refrigerant collecting portion 23a flows into the first refrigerant flow passage 33a of the intermediate tank portion 33 through the first collecting portion connecting member 31a as indicated by the arrow F. Further, the refrigerant flowing into the second refrigerant collecting portion 23b flows into the second refrigerant flow passage 33b of the intermediate tank portion 33 through the second collecting portion connecting member 31b as indicated by an arrow G.

  The refrigerant that has flowed into the first refrigerant flow passage 33a flows into the second refrigerant distribution portion 13b of the second upwind tank portion 13 through the two second distribution portion connecting members 32b as indicated by arrows H1 and H2. The refrigerant flowing into the second refrigerant flow passage 33b flows into the first refrigerant distribution portion 13a of the second upwind tank portion 13 through the two first distribution portion connecting members 32a as indicated by arrows I1 and I2.

  The refrigerant that has flowed into the second refrigerant distribution unit 13b of the second upwind tank unit 13 moves up the second upwind heat exchange core unit 11b of the upwind heat exchange core unit 11 as indicated by an arrow J. On the other hand, the refrigerant that has flowed into the first refrigerant distribution portion 13a rises in the first windward heat exchange core portion 11a of the windward heat exchange core portion 11 as indicated by an arrow K.

  The refrigerant that has risen up the second upwind heat exchange core portion 11b and the refrigerant that has risen up the first upwind heat exchange core portion 11a flow into the tank of the first upwind tank portion 12 as indicated by arrows L and M, respectively. As indicated by an arrow N, the refrigerant is led out to the compressor (not shown) suction side from a refrigerant lead-out portion 12a formed on one end side of the first upwind tank portion 12.

  In the refrigerant evaporator 1 according to the present embodiment described above, the first refrigerant inflow port through which the refrigerant from the second leeward heat exchange core portion 21b flows into the first refrigerant distribution portion 13a into the first refrigerant distribution portion 13a. A plurality of 14a are provided. For this reason, compared with the case where one first refrigerant inlet 14a is provided, the distance from the end of the tube 111 farthest from the first refrigerant inlet 14a to the first refrigerant inlet 14a is shortened. can do.

  As described above, the shorter the distance between the first refrigerant inlet 14a and the end of the tube 111, the smaller the refrigerant pressure loss and the greater the amount of refrigerant flowing into the tube 111. For this reason, the refrigerant evaporator 1 according to the present embodiment is the tube 111 farthest from the first refrigerant inflow port 14a compared to the refrigerant evaporator 1 in which one first refrigerant inflow port 14a is provided. Since the distance from the end to the first refrigerant inlet 14a is shortened, the amount of refrigerant flowing into the tube 111 increases.

  Thereby, since the deviation of the refrigerant amount flowing into each tube 111 constituting the first upwind heat exchange core portion 11a can be reduced, the liquid refrigerant is distributed unevenly in the first upwind heat exchange core portion 11a. Can be suppressed. Therefore, it is possible to suppress a decrease in the cooling performance of the fluid to be cooled in the refrigerant evaporator 1.

  Specifically, in the present embodiment, as shown in FIG. 3, the two first refrigerant inlets 14 a are provided on one side and the other side of the center line C in the tube 111 stacking direction in the first refrigerant distributor 13 a. One by one. In the present embodiment, the two first refrigerant inlets 14a are arranged symmetrically with respect to the center line C in the tube 111 stacking direction in the first refrigerant distributor 13a.

  More specifically, the two first refrigerant inflow ports 14a include an end portion of the first refrigerant distributor 13a in the tube stacking direction that is closer to the refrigerant outlet 12a and a refrigerant in the tube stack direction of the first refrigerant distributor 13a. It is provided at each end on the side far from the lead-out part 12a.

  In other words, in the plurality of tubes 111 constituting the first upwind heat exchange core part 11a, the distance from the refrigerant inlet 14a arranged closest to the two first refrigerant inlets 14a is defined as the refrigerant inlet. The distance between the refrigerant inlets in the tube 111a where the distance between the refrigerant inlets is the maximum with respect to one first refrigerant inlet 14a (left side of the paper) of the two first refrigerant inlets 14a, The refrigerant inlet distance lb in the tube 111b having the maximum distance between the refrigerant inlets is substantially equal to the other first refrigerant inlet 14a (right side in the drawing).

  According to this, since the bias of the refrigerant amount flowing into each tube 111 constituting the first upwind heat exchange core portion 11a can be further reduced, the liquid phase refrigerant is unevenly distributed in the first upwind heat exchange core portion 11a. It is possible to more reliably suppress the occurrence.

  Moreover, in this embodiment, the 1st distribution part connection member 32a and the 2nd distribution part connection member 32b are provided 2 each. According to this, compared with the refrigerant evaporator 1 in which each connection member 32a, 32b is provided one by one, the mass flow rate of the refrigerant per unit area is reduced in each of the distribution unit connection members 32a, 32b. can do. For this reason, since the pressure loss of the refrigerant | coolant of each distribution part connection member 32a, 32b becomes small, it becomes possible to improve the cooling performance of a to-be-cooled fluid.

  By the way, in the refrigerant evaporator 1 provided with one 1st refrigerant | coolant inflow port 14a, the flow velocity of the refrigerant | coolant which flowed in from the 1st refrigerant | coolant inflow port 14a rises, and it becomes easy to receive to the influence of the inertial force of a flow. For this reason, the larger the refrigerant flow rate, the larger the refrigerant flow rate flowing to the side farther from the first refrigerant inflow port 14a, and the more uneven the distribution of the liquid phase refrigerant.

  On the other hand, in this embodiment, as shown in FIG. 2, the number (specifically, two) of the first refrigerant inlets 14a with respect to the number (specifically one) of the second refrigerant outlets 24b. Is increasing. According to this, since the flow velocity of the refrigerant flowing into the first refrigerant distribution unit 13a can be reduced, it is possible to suppress the deterioration of refrigerant distribution due to the inertial force of the flow.

  Here, in the plurality of tubes 111 constituting the first upwind heat exchange core portion 11a, a tube disposed at a position farthest from the refrigerant deriving portion 12a is referred to as a deriving portion farthest tube 111f. At this time, in the present embodiment, as shown in FIG. 3, the refrigerant inlet distance lf in the derivation section furthest tube 111f is the maximum of the derivation section among the plurality of tubes 111 constituting the first upwind heat exchange core section 11a. The distance between the refrigerant inlets in the tubes 111 other than the far tube 111f is shorter.

  According to this, since the bias of the refrigerant pressure loss in each refrigerant flow path from the first refrigerant inflow port 14a through each tube 111 to the refrigerant outlet 12a can be suppressed, deterioration of refrigerant distribution is suppressed. It becomes possible.

  In the present embodiment, the two second refrigerant inlets 14b are also arranged in the same manner as the first refrigerant inlet 14a, that is, the end closer to the refrigerant outlet 12a in the tube stacking direction of the first refrigerant distributor 13a. And the end of the first refrigerant distributor 13a that is far from the refrigerant outlet 12a in the tube stacking direction. For this reason, also in the 2nd upwind heat exchange core part 11b, it becomes possible to suppress that a liquid phase refrigerant is distributed unevenly similarly to the 1st upwind heat exchange core part 11a.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The second embodiment differs from the first embodiment in the arrangement of the first refrigerant inlet 14a and the second refrigerant inlet 14b.

  As shown in FIG. 7, the first refrigerant outlet 14 a of this embodiment has two first refrigerant outlets 14 a with a gap in the inner portion of the first refrigerant distribution portion 13 a of the second upwind tank portion 13 from both ends in the tube stacking direction. Is provided.

  Here, among the plurality of tubes 111 constituting the first upwind heat exchange core portion 11a, the tube 111 having the longest distance from the first refrigerant inlet 14a is referred to as the farthest tube 111g, and the first refrigerant inlet is concerned. The tube with the shortest distance from 14a is recently referred to as tube 111h. Moreover, the tube arrange | positioned in the site | part nearest from the refrigerant | coolant derivation | leading-out part 12a among the several tubes 111 which comprise the 1st windward heat exchange core part 11a is called the derivation | leading-out part nearest tube 111e.

  In the present embodiment, the two first inlets 14a are arranged so that the distances between the first refrigerant inlets 14a are substantially equal in all the tubes 111 constituting the first upwind heat exchange core portion 11a. Has been. Specifically, the distance from the latest tube 111h to the first refrigerant inlet 14a is La, the distance from the farthest tube 111g to the first refrigerant inlet 14a is Lb, and the first refrigerant distribution in the latest tube 111h is Lb. When the length of the portion located inside the portion 13a is Ld, the two first inflow ports 14a are arranged at positions satisfying the relationship La ≦ Lb ≦ La + Ld.

  According to this, since the maximum value of the distance between the refrigerant inlets of the tubes 111 constituting the first upwind heat exchange core portion 11a can be reduced, the bias of the pressure loss of the refrigerant flowing into each tube 111 can be reduced. . For this reason, it becomes possible to suppress that liquid phase refrigerant is distributed unevenly in the 1st upwind heat exchange core part 11a.

  Moreover, in this embodiment, the refrigerant | coolant inlet distance le in the derivation | leading-out part nearest tube 111e is the refrigerant | coolant inlet_port | entrance in tubes 111 other than the derivation part nearest tube 111e among the several tubes 111 which comprise the 1st upwind heat exchange core part 11a. It is longer than the distance.

  According to this, since the bias of the pressure loss of the refrigerant in each refrigerant flow path from the first refrigerant inlet 14a through each tube 111 to the refrigerant outlet 12a can be suppressed, it is possible to suppress the deterioration of the refrigerant distribution property. It becomes possible.

  In the present embodiment, the two second refrigerant inlets 14b are arranged in the same manner as the first refrigerant inlet 14a, that is, in all the tubes 111 constituting the second upwind heat exchange core portion 11b, the second It arrange | positions so that the distance between the refrigerant | coolant inflow ports 14b may become substantially equal. For this reason, also in the 2nd windward heat exchange core part 11b, it can suppress that a liquid phase refrigerant is distributed unevenly similarly to the 1st windward heat exchange core part 11a.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. The third embodiment differs from the first embodiment in the arrangement of the first refrigerant inlet 14a and the second refrigerant inlet 14b.

  As shown in FIG. 8, the two first refrigerant inlets 14a are arranged on one side (right side of the drawing) of the center line C in the stacking direction of the tubes 111 in the first refrigerant distributor 13a. In addition, a throttle plate 15 is provided on the other side (paper surface) of the center line C in the first refrigerant distribution portion 13a as a flow rate adjusting means for adjusting the flow rate of the refrigerant flowing in the first refrigerant distribution portion 13a.

  According to the present embodiment, in the first refrigerant distributor 13a, the refrigerant flowing from the two first refrigerant inlets 14a diffuses when passing through the throttle plate 15, so that the refrigerant is distributed in the first refrigerant distributor 13a. Can be improved. Therefore, it is possible to suppress the liquid phase refrigerant from being unevenly distributed in the first upwind heat exchange core portion 11a.

  In the present embodiment, the two second refrigerant inlets 14b are also arranged in the same manner as the first refrigerant inlet 14a, that is, one side of the center line C in the stacking direction of the tubes 111 in the second refrigerant distributor 13b ( On the right side of the page). Further, the diaphragm plate 15 is also arranged on the other side (paper surface) of the center line C in the second refrigerant distribution portion 13b. For this reason, also in the 2nd windward heat exchange core part 11b, it can suppress that a liquid phase refrigerant is distributed unevenly similarly to the 1st windward heat exchange core part 11a.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, an example in which two first refrigerant inlets 14a are provided for one second refrigerant outlet 24b has been described. However, the number of the first refrigerant inlets 14a is not limited thereto. As long as the number is larger than the number of the second refrigerant outlets 24b, any number may be provided.

  (2) In the above-described embodiment, the example in which the second refrigerant inlet 14b is arranged in the same manner as the first refrigerant inlet 14a has been described. However, the present invention is not limited to this, and one second refrigerant inlet 14b may be provided. Good. In addition, a plurality of second refrigerant inlets 14b may be provided, and one first refrigerant inlet 14a may be provided.

  (3) In the above-described embodiment, as the refrigerant evaporator 1, the first windward side heat exchange core portion 11 a and the first leeward side heat exchange core portion 21 a are superposed when viewed from the flow direction of the blown air. Although the example arrange | positioned so that it may arrange | position and the 2nd leeward side heat exchange core part 11b and the 2nd leeward side heat exchange core part 21b superpose | polymerize was demonstrated, it is not restricted to this. The refrigerant evaporator 1 is arranged so that at least a part of the first windward heat exchange core portion 11a and the first leeward heat exchange core portion 21a are polymerized when viewed from the flow direction of the blown air, You may arrange | position so that at least one part of the 2nd leeward side heat exchange core part 11b and the 2nd leeward side heat exchange core part 21b may superpose | polymerize.

  (4) Although it is desirable to arrange the windward evaporator 10 in the refrigerant evaporator 1 on the upstream side in the flow direction X of the blown air as compared with the above-described embodiment, the present invention is not limited thereto. You may make it arrange | position the windward evaporation part 10 in the downstream in the flow direction X of blowing air rather than the leeward evaporation part 20. FIG.

  (5) In the above-described embodiment, the example in which each heat exchange core portion 11 and 21 is configured by the plurality of tubes 111 and 211 and the fins 112 and 212 has been described. The heat exchange core parts 11 and 21 may be configured as described above. Moreover, when each heat exchange core part 11 and 21 is comprised with the some tubes 111 and 211 and the fins 112 and 212, the fins 112 and 212 may employ | adopt a plate fin not only a corrugated fin.

  (6) In the above-described embodiment, the example in which the refrigerant evaporator 1 is applied to the refrigeration cycle of the vehicle air conditioner has been described. However, the present invention is not limited thereto, and the present invention may be applied to, for example, a refrigeration cycle used in a water heater. Good.

10 Upwind evaporator (second evaporator)
11 Upwind heat exchange core (heat exchange core)
11a 1st upwind heat exchange core part (3rd core part)
11b 2nd windward heat exchange core part (4th core part)
13a 1st refrigerant | coolant distribution part 14a 1st refrigerant | coolant inflow port 20 The leeward side evaporation part (1st evaporation part)
21 Downward heat exchange core (heat exchange core)
21a 1st leeward side heat exchange core part (1st core part)
21b 2nd leeward side heat exchange core part (2nd core part)

Claims (7)

A refrigerant evaporator that exchanges heat between a cooled fluid flowing outside and a refrigerant,
A first evaporator (20) and a second evaporator (10) arranged in series with respect to the flow direction of the fluid to be cooled;
Each of the first evaporator (20) and the second evaporator (10)
A heat exchange core (11, 21) configured by laminating a plurality of tubes (111, 211) through which refrigerant flows;
A pair of tank parts (12, 13, 22, 23) connected to both ends of the plurality of tubes (111, 211) and collecting or distributing refrigerant flowing through the plurality of tubes (111, 211); Have
The heat exchange core part (21) in the first evaporation part (20) includes a first core part (21a) constituted by a part of a tube group among the plurality of tubes (211), and a remaining tube. Having a second core portion (21b) composed of a group;
The heat exchange core part (11) in the second evaporation part (10) includes at least a part of the first core part (21a) in the flow direction of the fluid to be cooled among the plurality of tubes (111). A third core portion (11a) composed of opposing tube groups, and a fourth core portion composed of a tube group facing at least part of the second core portion (21b) in the flow direction of the fluid to be cooled (11b)
Of the pair of tank parts (22, 23) in the first evaporation part (20), one tank part (23) is a first refrigerant collecting part that collects refrigerant from the first core part (21a). (23a) includes a second refrigerant assembly part (23b) that collects the refrigerant from the second core part (21b),
Of the pair of tank parts (12, 13) in the second evaporation part (10), one tank part (13) is a first refrigerant distribution part that distributes the refrigerant to the third core part (11a). 13a), including a second refrigerant distribution part (13b) for distributing the refrigerant to the fourth core part (11b),
The first evaporation section (20) and the second evaporation section (10) include first communication sections (31a, 32b) that guide the refrigerant of the first refrigerant assembly section (23a) to the second refrigerant distribution section (13b). , 33a) and a refrigerant replacement part (30) having a second communication part (31b, 32a, 33b) for guiding the refrigerant of the second refrigerant assembly part (23b) to the first refrigerant distribution part (13a). Are connected,
The first refrigerant distributor (13a) is connected to the second communication part (31b, 32a, 33b), and the refrigerant from the second refrigerant assembly part (23b) is supplied to the first refrigerant distributor ( 13a) is provided with a refrigerant inlet (14a) for flowing in,
The second refrigerant collecting portion (23b) is connected to the second communication portion (31b, 32a, 33b), and the refrigerant in the second refrigerant collecting portion (23b) is transferred to the first refrigerant distributing portion ( 13a) is provided with a refrigerant outlet (24b) for flowing out,
The refrigerant evaporator, wherein the number of the refrigerant outlet (24b) and the number of the refrigerant inlet (14a) are different. A refrigerant evaporator that exchanges heat between a cooled fluid flowing outside and a refrigerant,
A first evaporator (20) and a second evaporator (10) arranged in series with respect to the flow direction of the fluid to be cooled;
Each of the first evaporator (20) and the second evaporator (10)
A heat exchange core (11, 21) configured by laminating a plurality of tubes (111, 211) through which refrigerant flows;
A pair of tank parts (12, 13, 22, 23) connected to both ends of the plurality of tubes (111, 211) and collecting or distributing refrigerant flowing through the plurality of tubes (111, 211); Have
The heat exchange core part (21) in the first evaporation part (20) includes a first core part (21a) constituted by a part of a tube group among the plurality of tubes (211), and a remaining tube. Having a second core portion (21b) composed of a group;
The heat exchange core part (11) in the second evaporation part (10) includes at least a part of the first core part (21a) in the flow direction of the fluid to be cooled among the plurality of tubes (111). A third core portion (11a) composed of opposing tube groups, and a fourth core portion composed of a tube group facing at least part of the second core portion (21b) in the flow direction of the fluid to be cooled. (11b)
Of the pair of tank parts (22, 23) in the first evaporation part (20), one tank part (23) is a first refrigerant collecting part that collects refrigerant from the first core part (21a). (23a) includes a second refrigerant assembly part (23b) that collects the refrigerant from the second core part (21b),
Of the pair of tank parts (12, 13) in the second evaporation part (10), one tank part (13) is a first refrigerant distribution part that distributes the refrigerant to the third core part (11a). 13a), including a second refrigerant distribution part (13b) for distributing the refrigerant to the fourth core part (11b),
The first evaporation section (20) and the second evaporation section (10) include first communication sections (31a, 32b) that guide the refrigerant of the first refrigerant assembly section (23a) to the second refrigerant distribution section (13b). , 33a) and a refrigerant replacement part (30) having a second communication part (31b, 32a, 33b) for guiding the refrigerant of the second refrigerant assembly part (23b) to the first refrigerant distribution part (13a). Are connected,
The first refrigerant distributor (13a) is connected to the second communication part (31b, 32a, 33b), and the refrigerant from the second refrigerant assembly part (23b) is supplied to the first refrigerant distributor ( A refrigerant evaporator characterized in that a plurality of refrigerant inlets (14a) for introducing the gas into 13a) are provided.   The refrigerant evaporator according to claim 1 or 2, wherein a plurality of the second communication parts (31b, 32a, 33b) are provided and are respectively connected to the refrigerant inlet (14a). . The second refrigerant collecting portion (23b) is connected to the second communication portion (31b, 32a, 33b), and the refrigerant in the second refrigerant collecting portion (23b) is transferred to the first refrigerant distributing portion ( 13a) is provided with a refrigerant outlet (24b) for flowing out,
The refrigerant evaporator according to any one of claims 1 to 3, wherein the number of the refrigerant inlets (14a) is larger than the number of the refrigerant outlets (24b).   The refrigerant evaporator according to claim 4, wherein the number of the first medium outlets (24b) is one.   A plurality of the refrigerant inlets (14a) are provided, and at least one is provided on one side and the other side of the center line (C) in the stacking direction of the tubes (111) in the first refrigerant distributor (13a). The refrigerant evaporator according to any one of claims 1 to 5, wherein the refrigerant evaporators are arranged one by one. A plurality of the refrigerant inlets (14a) are provided,
All the refrigerant inlets (14a) are arranged on one side of the center line (C) in the stacking direction of the tubes (111) in the first refrigerant distribution part (13a),
On the other side of the center line (C) in the first refrigerant distribution part (13a), a flow rate adjusting means (15) for adjusting the flow rate of the refrigerant flowing in the first refrigerant distribution part (13a) is provided. The refrigerant evaporator according to any one of claims 1 to 5, wherein the refrigerant evaporator is provided.

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