WO2014181547A1

WO2014181547A1 - Refrigerant evaporator

Info

Publication number: WO2014181547A1
Application number: PCT/JP2014/002453
Authority: WO
Inventors: 長屋　誠一
Original assignee: 株式会社デンソー
Priority date: 2013-05-10
Filing date: 2014-05-09
Publication date: 2014-11-13
Also published as: JP2014219175A

Abstract

In this refrigerant evaporator (1), a first refrigerant collection section (23a) and a second refrigerant collection section (23b) are formed by dividing a tank internal space of a tank section (23) of a first evaporation section (20) in two in the longitudinal direction of tubes (211), and a first refrigerant distribution section (13a) and a second refrigerant distribution section (13b) are formed by dividing a tank internal space of a tank section (13) of a second evaporation section (10) in two in the longitudinal direction of tubes (111). The first refrigerant collection section (23a) and the second refrigerant distribution section (13b) are connected to each other, and the second refrigerant collection section (23b) and the first refrigerant distribution section (13a) are connected to each other.

Description

Refrigerant evaporator

Cross-reference of related applications

This disclosure is based on Japanese Patent Application No. 2013-1000048 filed on May 10, 2013, the contents of which are incorporated herein.

The present disclosure relates to a refrigerant evaporator.

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

However, like the refrigerant evaporator of Patent Document 1, when the refrigerant flow direction is changed by dividing one tank to which the communicating portion is connected among the pair of tank portions of each evaporation portion in the tube stacking direction, When the refrigerant from the heat exchange core part of the first evaporation part flows to the heat exchange core part of the second evaporation part, the liquid-phase refrigerant is distributed unevenly to a part of the heat exchange core part of the second evaporation part. There is.

Specifically, the liquid-phase refrigerant that has flowed into the first evaporation section tends to easily flow into a tube located near the introduction section of the liquid-phase refrigerant, and the laminated refrigerant is sufficiently supplied to the tube far from the introduction section. Can't flow. Therefore, the liquid refrigerant sufficiently flows on one side in the width direction of the heat exchange core part of the second evaporation part, while the state of the refrigerant on one side in the width direction of the heat exchange core part of the second evaporation part becomes superheat. .

Thus, when the distribution property of the liquid-phase refrigerant in the refrigerant evaporator deteriorates, a region where heat exchange between the fluid to be cooled and the refrigerant is not effectively performed occurs in the heat exchange core part of the second evaporation part, and the refrigerant radiates heat. When the chamber is viewed from the flow direction of the blown air, a temperature distribution is generated in the width direction of the heat exchange core portion.

This disclosure is intended to provide a refrigerant evaporator capable of suppressing deterioration of refrigerant distribution.

In order to achieve the above object, a refrigerant evaporator that performs heat exchange between a cooled fluid flowing outside and a refrigerant includes a first evaporator and a second evaporator arranged in series with respect to the flow direction of the cooled fluid. A part. Each of the first evaporation section and the second evaporation section is connected to a heat exchange core section configured by laminating a plurality of tubes through which the refrigerant flows, and both ends of the plurality of tubes, and a set of refrigerants flowing through the plurality of tubes or A pair of tank portions that perform distribution. The heat exchange core part in a 1st evaporation part has the 2nd core part comprised by the 1st core part comprised by some tube groups among several tubes, and the remaining tube group. The heat exchange core part in the second evaporation part includes a third core part composed of a tube group that faces at least a part of the first core part in the flow direction of the fluid to be cooled, and the fluid to be cooled. The fourth core portion is composed of a tube group facing at least a part of the second core portion in the flow direction. Of the pair of tank parts in the first evaporation part, one tank part includes a first refrigerant collecting part that collects refrigerant from the first core part, and a second refrigerant collecting part that collects refrigerant from the second core part. Consists of including. Of the pair of tank parts in the second evaporation part, one tank part includes a first refrigerant distribution part that distributes the refrigerant to the third core part, and a second refrigerant distribution part that distributes the refrigerant to the fourth core part. Composed. The first evaporation section and the second evaporation section are a first communication section that guides the refrigerant of the first refrigerant assembly section to the second refrigerant distribution section, and a second communication that guides the refrigerant of the second refrigerant assembly section to the first refrigerant distribution section. It is connected via a refrigerant replacement part having a part. The tank internal space of one tank portion in the first evaporation section is partitioned into a first tank internal space and a second tank internal space in the longitudinal direction of the tube, and the first tank internal space is inside the second tank. It arrange | positions from the space near the other tank part among a pair of tank parts in a 1st evaporation part rather than space. The tank internal space of one tank portion in the second evaporation unit is partitioned into a third tank internal space and a fourth tank internal space in the longitudinal direction of the tube, and the third tank internal space is the interior of the fourth tank. It arrange | positions from the space near the other tank part among a pair of tank parts in a 2nd evaporation part rather than space. The first tank internal space forms a second refrigerant assembly, and the second tank internal space forms the first refrigerant assembly. The third tank inner space forms a first refrigerant distributor, and the fourth tank inner space forms a second refrigerant distributor.

Thus, the tank internal space of one tank portion in the first evaporation portion is partitioned into the first tank internal space and the second tank internal space in the longitudinal direction of the tube, and one tank portion in the second evaporation portion is formed. A refrigerant flow path for guiding the refrigerant from the first core portion to the fourth core portion by partitioning the tank inner space into a third tank inner space and a fourth tank inner space in the longitudinal direction of the tube; The pressure loss of the refrigerant flowing through the refrigerant flow path can be adjusted by changing the length of the refrigerant flow path that guides the refrigerant from the core section to the third core section. Thereby, by making the pressure loss of the refrigerant flowing through the two refrigerant flow paths uniform, it is possible to suppress the uneven distribution of the liquid-phase refrigerant from each refrigerant distributor to the heat exchange core in the second evaporator. it can.

Therefore, in the configuration in which the flow direction of the refrigerant is changed at the communication portion that connects one tank portion of each evaporation portion, deterioration of the refrigerant distribution property can be suppressed, and the cooling performance of the fluid to be cooled in the refrigerant evaporator Can be suppressed.

In addition, a refrigerant introduction part for introducing a refrigerant into the other tank part is connected to a side closer to the first core part than the second core part in the other tank part of the first evaporation part. A refrigerant derivation unit for deriving a refrigerant from the inside of the other tank unit is connected to a side closer to the third core unit than the fourth core unit in the other tank unit of the second evaporation unit. The tube constituting the first core part is longer in the longitudinal direction than the tube constituting the second core part, and the tube constituting the fourth core part is longer than the tube constituting the third core part. Is long.

Thus, while making the length of the longitudinal direction of the tube which comprises the 1st core part longer than the longitudinal direction length of the tube which constitutes the 2nd core part, the longitudinal direction of the tube which constitutes the 4th core part The refrigerant flow path for guiding the refrigerant from the first core part to the fourth core part by the length of the tube by making the length of the tube longer than the length in the longitudinal direction of the tube constituting the third core part, The pressure loss of the refrigerant flowing through the refrigerant flow path can be adjusted by changing the length of the refrigerant flow path that guides the refrigerant from the second core section to the third core section.

It is a typical perspective view of the refrigerant evaporator concerning an embodiment. It is explanatory drawing of the refrigerant evaporator shown in FIG. It is explanatory drawing for demonstrating the flow of the refrigerant | coolant in the refrigerant evaporator which concerns on embodiment. It is explanatory drawing for demonstrating distribution of the liquid phase refrigerant | coolant which flows through each heat exchange core part of the refrigerant evaporator which concerns on a comparative example. It is explanatory drawing for demonstrating distribution of the liquid phase refrigerant | coolant which flows through each heat exchange core part of the refrigerant evaporator which concerns on embodiment.

Hereinafter, an embodiment of the present disclosure will be described with reference to FIGS. 1 to 5. 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 fluid to be cooled flowing outside.

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.

In FIG. 2, illustration of the

fins

112 and 212 in the heat

exchange core portions

11 and 21 described later is 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. In addition, the windward side evaporation part 10 in this embodiment comprises a 2nd evaporation part, and the leeward side evaporation part 20 comprises the 1st evaporation part.

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 addition, in this embodiment, the heat exchange core part in the windward side evaporation part 10 is called the windward heat exchange core part 11, and the heat exchange core part in the leeward side evaporation part 20 is called the leeward side 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 a 3rd core part, and the 2nd windward heat exchange core part 11b comprises a 4th core part.

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 a 1st core part, and the 2nd leeward side heat exchange core part 21b comprises a 2nd core part.

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 is formed of 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.

In the present embodiment, each tube 211 (hereinafter referred to as the first leeward side tube 211a) constituting the first leeward side heat exchange core part 21a is each tube 211 (hereinafter referred to as the first leeward side heat exchange core part 21b). The second leeward side tube 211b) is longer in the longitudinal direction. Further, each tube 111 (hereinafter referred to as the first windward side tube 111a) constituting the first windward side heat exchange core part 11a is each tube 111 (hereinafter referred to as the second side) that constitutes the second windward side heat exchange core part 11b. The length in the longitudinal direction is shorter than that of the windward tube 111b.

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 second upwind tank unit 13 is composed of a cylindrical member whose both ends are closed. 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.

A first partition member 131 is disposed inside the second upwind tank portion 13 at a portion opposite to the windward heat exchange core portion 11 with respect to the longitudinal end portion of the tube 111, and this first partition member. 131 divides the tank internal space into two in the tube longitudinal direction. The first partition member 131 has a through hole (not shown) into which the second upwind tube 111b is inserted and joined. In this embodiment, the 1st partition member 131 is arrange | positioned in the center position of the tube longitudinal direction (up-down direction in FIG. 1) in the inside of the 2nd windward side tank part 13. As shown in FIG.

Of the two tank internal spaces partitioned by the first partition member 131, the first windward side tube 111a communicates with the space closer to the first windward side tank unit 12 (the upper side in FIG. 1). The second windward tube 111b communicates with a space on the side farther from the windward side tank unit 12 (lower side in FIG. 1).

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.

Therefore, in the present embodiment, the first refrigerant distributor 13a constitutes the third tank space. Moreover, the 2nd refrigerant distribution part 13b comprises the 4th tank inner space.

The second leeward tank portion 23 is formed of a cylindrical member whose both ends are closed. 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.

A second partition member 231 is disposed inside the second leeward tank portion 23 at a portion on the opposite side of the longitudinal end portion of the tube 211 from the leeward heat exchange core portion 21, and this second partition member. The tank internal space is divided into two in the longitudinal direction of the tube by 231. The second partition member 231 is formed with a through hole (not shown) into which the first leeward side tube 211a is inserted and joined. In the present embodiment, the second partition member 231 is disposed at the center position in the tube longitudinal direction inside the second leeward tank portion 23.

Of the two tank internal spaces partitioned by the second partition member 231, the second leeward side tube 211 b communicates with the space closer to the first leeward side tank unit 22 (upper side in FIG. 1). The first leeward side tube 211a communicates with the space on the side farther from the leeward side tank unit 22 (lower side in FIG. 1).

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.

Therefore, in the present embodiment, the first refrigerant assembly portion 23a constitutes the second tank space. Moreover, the 2nd refrigerant | coolant gathering part 23b comprises the 1st tank inner space.

The second leeward tank unit 13 and the second leeward tank unit 23 are 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 unit 30 includes a first connecting member 30a that communicates the first refrigerant collecting unit 23a in the second leeward tank unit 23 and the second refrigerant distribution unit 13b in the second leeward tank unit 13; The second refrigerant member 23b in the second leeward tank unit 23 and the second refrigerant member 13b in the second leeward tank unit 13 communicate with the first refrigerant distributor 13a.

Each of the first connecting member 30a and the second connecting member 30b 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 unit 23. At the same time, the other end is connected to the intermediate tank 33.

In the present embodiment, one end side of the first connecting member 30a is connected to a side farther from the refrigerant introducing portion 22a in the stacking direction of the tubes 211 in the first refrigerant collecting portion 23a, and one end side of the second connecting member 30b is Of the two refrigerant collecting portions 23b, the refrigerant is connected to the side closer to the refrigerant introducing portion 22a in the stacking direction of the tubes 211. Further, the other end side of the first connecting member 30a is connected to a side of the second refrigerant distribution portion 13b that is far from the refrigerant deriving portion 12a in the stacking direction of the tubes 111, and the other end side of the second connecting member 30b is the first side. It connects to the side near the refrigerant | coolant derivation | leading-out part 12a in the lamination direction of the tube 111 among the refrigerant | coolant distribution parts 13a.

In the present embodiment, the first connecting member 30a constitutes the first communicating portion. Moreover, the 2nd connection member 30b comprises the 2nd communication part.

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

As shown in FIG. 3, 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 that has flowed into the first refrigerant collecting portion 23a flows into the second refrigerant distribution portion 13b of the second upwind tank portion 13 through the first connecting member 30a as indicated by the arrow F. Further, the refrigerant flowing into the second refrigerant collecting portion 23b flows into the first refrigerant distributing portion 13a of the second upwind tank portion 13 through the second connecting member 30b as indicated by an arrow G.

The refrigerant that has flowed into the second refrigerant distribution section 13b of the second upwind tank section 13 ascends the second upwind heat exchange core section 11b of the upwind heat exchange core section 11 as indicated by an arrow H. On the other hand, the refrigerant that has flowed into the first refrigerant distribution unit 13a ascends the first upwind heat exchange core unit 11a of the upwind heat exchange core unit 11 as indicated by an arrow I.

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 J and K, respectively. As indicated by the arrow L, the refrigerant is led out to the compressor (not shown) suction side from the refrigerant lead-out portion 12a formed on one end side of the first upwind tank portion 12.

FIG. 4 shows that the refrigerant evaporator 1 according to the comparative example, that is, the space in the tank of the second leeward tank portion 23 and the second leeward tank portion 13 is divided into two in the stacking direction of the tubes 111 and 1111, respectively. It is explanatory drawing for demonstrating distribution of the liquid phase refrigerant | coolant which flows through each heat

exchange core part

11 and 21 of the refrigerant | coolant evaporator 1 which is located, and FIG. 5 is each heat exchange core part of the refrigerant evaporator 1 which concerns on this embodiment. 11 is an explanatory diagram for explaining a distribution of a liquid-phase refrigerant flowing through 11 and 21. FIG.

4 (a) and 5 (a) show the distribution of the liquid-phase refrigerant flowing through the windward heat exchange core unit 11, and FIGS. 4 (b) and 5 (b) show the leeward heat exchange core unit 21. 4 (c) and FIG. 5 (c) show the synthesis of the distribution of the liquid phase refrigerant flowing through the heat

exchange core portions

11 and 21. FIG. 4 and 5 show the distribution of the liquid-phase refrigerant when the refrigerant evaporator 1 is viewed from the direction of the arrow Y in FIG. 1 (the direction opposite to the flow direction X of the blown air). A portion indicated by a portion indicates a portion where the liquid-phase refrigerant exists.

First, regarding the distribution of the liquid-phase refrigerant flowing through the leeward heat exchange core section 21, as shown in FIGS. 4B and 5B, the refrigerant evaporator 1 according to the comparative example and the refrigerant according to the present embodiment. The same is true for the evaporator 1, and a portion where the liquid-phase refrigerant hardly flows (a white portion on the lower right side in the figure) is generated in a part of the second leeward heat exchange core portion 21 b.

Moreover, about distribution of the liquid phase refrigerant | coolant which flows through the windward heat exchange core part 11 in the refrigerant evaporator 1 which concerns on a comparative example, as shown to Fig.4 (a), the 1st windward of the windward heat exchange core part 11 is shown. In the heat exchange core part 11a, the liquid-phase refrigerant is less likely to flow than in the second upwind heat exchange core part 11b. On the other hand, in the refrigerant evaporator 1 according to the present embodiment, as shown in FIG. 5A, the first windward heat exchange of the windward heat exchange core unit 11 is compared with the refrigerant evaporator 1 according to the comparative example. The liquid-phase refrigerant easily flows through the core portion 11a.

Further, as shown in FIG. 4C and FIG. 5C, when the refrigerant evaporator 1 according to the comparative example and the refrigerant evaporator 1 according to the present embodiment are viewed from the flow direction X of the blown air, respectively. The liquid-phase refrigerant flows over the entire region of the second leeward heat exchange core portion 11b and the second leeward heat exchange core portion 21b to be polymerized.

In the refrigerant evaporator 1 according to the present embodiment described above, the tank internal space of the second leeward tank unit 23 is divided into two in the longitudinal direction of the tube 211, whereby the first refrigerant assembly 23a and the second refrigerant are separated. The first refrigerant distribution portion 13a and the second refrigerant distribution portion 13b are formed by forming the collecting portion 23b and partitioning the space in the tank of the second upwind tank portion 13 into two in the longitudinal direction of the tube 11. ing.

For this reason, the refrigerant flow path for guiding the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b and the refrigerant from the second leeward heat exchange core portion 21b are used as the first windward heat. The pressure loss of the refrigerant flowing through these two refrigerant flow paths can be adjusted by changing the length of the refrigerant flow path leading to the replacement core portion 11a. Thereby, by making the pressure loss of the refrigerant flowing through the two refrigerant flow paths uniform, the distribution of the liquid-phase refrigerant from the respective

refrigerant distribution units

13a and 13b to the heat exchange core unit 11 in the second evaporation unit 10 is made uniform. Can be suppressed.

Therefore, in the configuration in which the flow direction of the refrigerant is changed in the refrigerant replacement unit 30 that connects one tank unit of each of the

evaporation units

10 and 20, deterioration of the refrigerant distribution property can be suppressed, and in the refrigerant evaporator 1 It becomes possible to suppress a decrease in the cooling performance of the blown air.

In the present embodiment, the length in the longitudinal direction of the first leeward side tube 211a is longer than the length in the longitudinal direction of the second leeward side tube 211b, and the length in the longitudinal direction of the second leeward side tube 111b. Is longer than the length in the longitudinal direction of the first upwind tube 111a. For this reason, depending on the length of the

tubes

111 and 211, the refrigerant flow path for guiding the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b, and the second leeward heat exchange core portion 21b. The pressure loss of the refrigerant flowing through these two refrigerant flow paths can be adjusted by changing the length of the refrigerant flow path from the refrigerant flow path leading to the first upwind heat exchange core portion 11a.

In the present embodiment, the refrigerant introduction part 22a is arranged at a position close to the first leeward heat exchange core part 21a in the first leeward heat exchange core part 21a and the second leeward heat exchange core part 21b. At this time, the refrigerant flow rate flowing into the first leeward side tube 211a is larger than the refrigerant flow rate flowing into the second leeward side tube 211b. Further, a large amount of gas-phase refrigerant is present in the first upwind tube 111a, and the pressure loss of the liquid phase refrigerant flowing through the first upwind tube 111a increases.

For this reason, the flow rate of the refrigerant flowing through the refrigerant flow path for guiding the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b causes the refrigerant from the second leeward heat exchange core portion 21b to It becomes more than the refrigerant | coolant flow volume which flows through the refrigerant | coolant flow path which leads to the 1 windward side heat exchange core part 11a, and the distribution of a refrigerant | coolant deteriorates.

At this time, as in the present embodiment, the length in the longitudinal direction of the first leeward side tube 211a is made longer than the length in the longitudinal direction of the second leeward side tube 211b, and the longitudinal direction of the second leeward side tube 111b. Is made longer than the length in the longitudinal direction of the first windward tube 111a, so that the pressure loss of the refrigerant flowing through the first leeward tube 211a and the second windward tube 111b is reduced to the second leeward tube. It becomes larger than the pressure loss of the refrigerant | coolant which distribute | circulates 211b and the 1st windward tube 111a.

Thereby, the pressure loss of the refrigerant flowing through the refrigerant flow path that guides the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b increases. For this reason, the pressure loss of the refrigerant flowing through the refrigerant flow path for guiding the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b and the refrigerant from the second leeward heat exchange core portion 21b Can be made uniform with the pressure loss of the refrigerant flowing through the refrigerant flow path leading to the first upwind heat exchange core portion 11a.

Therefore, the flow rate of the refrigerant flowing through the refrigerant flow path for guiding the refrigerant from the first leeward heat exchange core portion 21a to the second leeward heat exchange core portion 11b and the refrigerant from the second leeward heat exchange core portion 21b are the first. A difference with the flow rate of the refrigerant flowing through the refrigerant flow path leading to the windward heat exchange core portion 11a becomes small, and deterioration of refrigerant distribution can be suppressed.

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

In the above-described embodiment, the refrigerant evaporator 1 is arranged so that the first windward heat exchange core portion 11a and the first leeward heat exchange core portion 21a are superposed when viewed from the flow direction of the blown air. In addition, the example has been described in which the second leeward heat exchange core portion 11b and the second leeward heat exchange core portion 21b are superposed, but the present invention is not limited thereto. 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.

As in the above-described embodiment, it is desirable to arrange the windward side evaporator 10 in the refrigerant evaporator 1 on the upstream side in the flow direction X of the blown air with respect to the leeward side evaporator 20, but not limited to this, the windward side evaporator The part 10 may be arranged on the downstream side in the flow direction X of the blown air with respect to the leeward side evaporation part 20.

In the above-described embodiment, the example in which each heat

exchange core portion

11, 21 is configured by the plurality of

tubes

111, 211 and the

fins

112, 212 has been described. The

exchange core parts

11 and 21 may be configured. 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.

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 may be applied to, for example, a refrigeration cycle used in a water heater or the like.

In the above-described embodiment, the example in which the pair of

tank portions

12, 13, 22, and 23 disposed on the upper and lower sides of the heat

exchange core portions

11 and 21 are formed in a substantially cylindrical shape has been described. You may form in hollow cylinder shapes, such as a cylinder shape.

In the above-described embodiment, the example in which the first partition member 131 is disposed at the center position in the tube longitudinal direction inside the second upwind tank unit 13 has been described. You may arrange | position in the arbitrary positions in the site | part on the opposite side to the windward heat exchange core part 11 rather.

Moreover, although the above-mentioned embodiment demonstrated the example which has arrange | positioned the 2nd partition member 231 in the center position of the tube longitudinal direction inside the 2nd leeward side tank part 23, it is not restricted to this, The longitudinal direction of the tube 211 You may arrange | position in the arbitrary positions in the site | part on the opposite side to the leeward side heat exchange core part 21 rather than an edge part.

Claims

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 evaporating section (20) and the second evaporating section (10) include a first communicating section (30a) that guides the refrigerant in the first refrigerant collecting section (23a) to the second refrigerant distributing section (13b), And a refrigerant replacement part (30) having a second communication part (30b) for guiding the refrigerant of the second refrigerant assembly part (23b) to the first refrigerant distribution part (13a),
The tank internal space of the one tank section (23) in the first evaporation section (20) has a first tank internal space (23b) and a second tank internal space (23a) in the longitudinal direction of the tube (211). And is divided into
The first tank inner space (23b) is the other tank portion (22) of the pair of tank portions (22, 23) in the first evaporator (20) than the second tank inner space (23a). ) Near the side,
The tank internal space of the one tank section (13) in the second evaporation section (10) has a third tank internal space (13a) and a fourth tank internal space (13b) in the longitudinal direction of the tube (111). And is divided into
The third tank inner space (13a) is more than the fourth tank inner space (13b), the other tank portion (12 of the pair of tank portions (12, 13) in the second evaporation portion (10). ) Near the side,
The first tank inner space forms the second refrigerant collecting portion (23b), and the second tank inner space forms the first refrigerant collecting portion (23a),
The refrigerant evaporator in which the third tank inner space forms the first refrigerant distribution part (13a) and the fourth tank inner space forms the second refrigerant distribution part (13b).
In the other tank part (22) of the first evaporation part (20), the other tank part (22) is closer to the first core part (21a) than the second core part (21b). ) A refrigerant introduction part (22a) for introducing refrigerant into the interior is connected,
In the other tank part (12) of the second evaporation part (10), the other tank part (11b) is closer to the third core part (11a) than the fourth core part (11b). ) A refrigerant outlet part (12a) for extracting the refrigerant from the inside is connected,
The tube (211) constituting the first core portion (21a) is longer in the longitudinal direction than the tube (211) constituting the second core portion (21b),
The tube (111) constituting the fourth core part (11b) is longer in the longitudinal direction than the tube (111) constituting the third core part (11a). The refrigerant evaporator as described.