WO2018110087A1

WO2018110087A1 - Heat exchanger

Info

Publication number: WO2018110087A1
Application number: PCT/JP2017/038186
Authority: WO
Inventors: 高橋　栄三
Original assignee: 株式会社デンソー
Priority date: 2016-12-12
Filing date: 2017-10-23
Publication date: 2018-06-21
Also published as: JP2018096584A

Abstract

This heat exchanger (10) is provided with a plurality of plate-shaped members (151, 152) which form partitions between first flow paths (100) through which a first fluid flows, and second flow paths (200) through which a second fluid flows, such that the first flow paths and the second flow paths are alternately stacked. In the heat exchanger (10), a supply flow path (SP) for supplying the first fluid to each of the first flow paths is formed so as to pass through the plurality of plate-shaped members along the direction in which the first flow paths and the second flow paths are stacked. In the heat exchanger (10), portions of the first flow paths in the vicinity of the supply flow path are formed so as to be enlarged in both a forward direction and a reverse direction in comparison to other portions of the first flow paths, when the forward direction is defined as the direction in which the first fluid flows in the supply flow path, and the reverse direction is defined as the opposite direction to the forward direction.

Description

Heat exchanger

Cross-reference of related applications

This application is based on the Japanese Patent Application No. 2016-240054 filed on December 12, 2016, and claims the benefit of its priority. Which is incorporated herein by reference.

This disclosure relates to a heat exchanger.

For example, a refrigeration cycle for automobiles is provided with a heat exchanger for exchanging heat between refrigerant and cooling water. In such a heat exchanger that exchanges heat between two types of fluids, a flow path through which one fluid flows (hereinafter also referred to as “first flow path”) and a flow path through which the other fluid flows (hereinafter, referred to as “first flow path”). In general, the “second flow path” is formed as a layered space, and these are alternately stacked.

As an example of such a heat exchanger, the following Patent Document 1 discloses a first flow path (first layered space) into which transmission oil is introduced and a second flow path (second layered space) into which cooling water is introduced. ) And the heat exchanger of the structure laminated | stacked alternately is described. In the heat exchanger, a supply flow path for supplying a fluid to each first flow path is formed so as to penetrate a plurality of plate-like members (cup plates) that partition the first flow path and the second flow path. Has been. The transmission oil is distributed to the first flow paths while flowing along the supply flow paths.

JP 2012-107783 A

In the heat exchanger used for the refrigeration cycle for automobiles, when the configuration described in Patent Document 1 is adopted, the coolant flows through the first flow path and the cooling water flows through the second flow path. Become. The refrigerant is distributed to the respective first flow paths formed in layers while flowing along the supply flow path formed so as to penetrate the plate-like member. When the refrigerant flows into the first flow path from the supply flow path, the refrigerant changes its flow direction largely (about 90 degrees).

Incidentally, the refrigerant circulating in the refrigeration cycle is often in a gas-liquid mixture state when flowing into the heat exchanger. In order to efficiently perform heat exchange in the heat exchanger, it is preferable that the ratio of the gas-phase refrigerant and the liquid-phase refrigerant flowing into the first flow path is substantially uniform for all the first flow paths. .

However, in the refrigerant flowing in a gas-liquid mixed state, it is rare that the gas-phase refrigerant and the liquid-phase refrigerant are evenly dispersed. Accordingly, it may occur that a larger amount of liquid-phase refrigerant flows into some of the first flow paths while a larger amount of vapor-phase refrigerant flows into the other first flow paths.

Also, liquid phase refrigerant has a large inertial force, and its flow direction is difficult to change, whereas gas phase refrigerant has a small inertial force and tends to easily change its flow direction. For this reason, in a heat exchanger having a configuration in which the refrigerant flowing through the supply channel flows into the first channel after greatly changing the flow direction, the gas phase refrigerant and It is further difficult to allow the liquid-phase refrigerant to flow evenly.

This disclosure is intended to provide a heat exchanger capable of evenly flowing a gas-liquid mixed fluid into each of a plurality of stacked flow paths.

A heat exchanger according to the present disclosure is a heat exchanger that performs heat exchange between a first fluid and a second fluid, and includes a first flow path through which the first fluid flows and a second flow through which the second fluid flows. A plurality of plate-like members that partition between the first flow path and the second flow path are provided so that the roads are alternately stacked. A supply channel for supplying the first fluid to each first channel is formed so as to penetrate a plurality of plate-like members along the direction in which the first channel and the second channel are stacked. Has been. When the direction in which the first fluid flows in the supply flow path is the forward direction and the direction opposite to the forward direction is the reverse direction, a portion of the first flow path in the vicinity of the supply flow path is the first flow path. Compared to the other parts, it is formed so as to expand in both the forward direction and the reverse direction.

In the heat exchanger having such a configuration, a portion in the vicinity of the supply flow path in the first flow path through which the first fluid flows is enlarged, thereby forming a relatively large space. A part of the first fluid flowing through the supply channel flows into the space when the pressure is released when the first fluid passes through the plate-like member. As a result, a relatively large vortex of the first fluid is generated in the space, and the gas phase refrigerant and the liquid phase refrigerant are mixed by the vortex. The refrigerant sufficiently mixed by the vortex flows into each first flow path. Thus, in the heat exchanger of the said structure, the 1st fluid of gas-liquid mixing can be made to flow in equally with respect to each of the several laminated | stacked 1st flow path.

According to the present disclosure, there is provided a heat exchanger that can uniformly flow a gas-liquid mixed fluid into each of a plurality of stacked flow paths.

FIG. 1 is a side view of the heat exchanger according to the present embodiment. FIG. 2 is a diagram illustrating the heat exchanger according to the present embodiment as viewed from above. FIG. 3 is a cross-sectional view showing a III-III cross section in FIG. FIG. 4 is a schematic cross-sectional view for explaining a specific configuration of the container. FIG. 5 is a diagram schematically showing a path through which a refrigerant flows and a path through which cooling water flows in the heat exchanger of FIG. 1. FIG. 6 is a diagram showing inner fins arranged inside the heat exchanger. FIG. 7 is a perspective view showing the configuration of the inner fin shown in FIG. FIG. 8 is a diagram schematically illustrating the flow of the refrigerant flowing from the supply flow path into the refrigerant flow path. FIG. 9 is a diagram schematically showing the flow of the refrigerant flowing from the supply channel into the refrigerant channel in the heat exchanger according to the comparative example. FIG. 10 is a diagram schematically illustrating the flow of the refrigerant flowing from the supply channel into the refrigerant channel in the heat exchanger according to another comparative example.

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

The configuration of the heat exchanger 10 according to the present embodiment will be described. The heat exchanger 10 shown in FIG. 1 is configured as a heat exchanger for performing heat exchange between a refrigerant and cooling water (for example, LLC). Such a heat exchanger 10 is used as, for example, a water-cooled condenser or an evaporator of an automobile refrigeration cycle. The refrigerant corresponds to the “first fluid” in the present embodiment. The cooling water corresponds to the “second fluid” in the present embodiment.

The heat exchanger 10 includes a container 15. As shown in FIG. 3, the container 15 has a cup 151 and an inner plate 152 that are plate-like members, and these are brazed to each other in a state of being alternately stacked. . A space is formed between the cup 151 and the inner plate 152 adjacent to each other, and the space is a coolant channel 100 that is a channel through which a coolant flows, or a cooling water channel that is a channel through which coolant flows. 200. The coolant channel 100 and the cooling water channel 200 are both formed as flat (layered) thin spaces, and are alternately arranged along the stacking direction of the containers 15 (vertical direction in FIGS. 1 and 3). Is formed.

The refrigerant channel 100 corresponds to the “first channel” in the present embodiment. The cooling water channel 200 corresponds to the “second channel” in the present embodiment. Further, the cup 151 and the inner plate 152 partition the refrigerant channel 100 and the cooling water channel 200 so that the refrigerant channel 100 and the cooling water channel 200 are alternately stacked. All correspond to the “plate member” in the present embodiment.

As shown in FIGS. 3 and 6, inner fins 300 are arranged inside the container 15, that is, in each of the coolant channel 100 and the cooling water channel 200. The inner fin 300 is provided in order to increase the contact area with the refrigerant or the cooling water, thereby improving the heat exchange efficiency of the heat exchanger 10. The specific shape and arrangement of the inner fin 300 will be described later.

As shown in FIG. 2, the shape of the heat exchanger 10 (that is, the shape of the container 15) in a top view is generally rectangular. On the upper surface of the heat exchanger 10, a refrigerant inflow portion 101 and a cooling water outflow portion 202 are provided at positions near one end in the longitudinal direction (left side in FIG. 2). The refrigerant inflow portion 101 is a portion serving as an inlet for refrigerant supplied from the outside. The cooling water outflow portion 202 is a portion that becomes an outlet of the cooling water that has passed through the heat exchanger 10. The refrigerant inflow portion 101 and the cooling water outflow portion 202 are provided so as to be aligned along the short direction of the heat exchanger 10 in a top view.

As shown in FIG. 1, a refrigerant outflow portion 102 is provided at a position on the lower surface of the heat exchanger 10 and immediately below the refrigerant inflow portion 101. The refrigerant outflow portion 102 is a portion that becomes an outlet of the refrigerant that has passed through the heat exchanger 10. Further, a cooling water inflow portion 201 is provided at a position on the lower surface of the heat exchanger 10 and immediately below the cooling water outflow portion 202. The cooling water inflow portion 201 is a portion serving as an inlet for cooling water supplied from the outside. The refrigerant outflow portion 102 and the cooling water inflow portion 201 are also provided so as to be aligned along the short direction of the heat exchanger 10 in a top view.

In the following description, the direction from the refrigerant outflow portion 102 toward the refrigerant inflow portion 101 is referred to as an upward direction, and the opposite direction is referred to as a downward direction. However, the vertical relationship between the refrigerant inflow portion 101 and the refrigerant outflow portion 102 when the heat exchanger 10 is actually used may be different from that shown in FIG.

As shown in FIG. 3, a circular opening OP 1 is formed at a position directly below the refrigerant inflow portion 101 in the cup 151. Similarly, a circular opening OP 2 is formed at a position directly below the refrigerant inflow portion 101 in the inner plate 152. The cup 151 and the inner plate 152 in which the cooling water flow path 200 is formed are brazed in a state where the edge of the opening OP1 and the edge of the opening OP2 overlap each other. For this reason, the refrigerant flowing in from the refrigerant inflow portion 101 is distributed to the respective refrigerant flow paths 100 while flowing downward through the opening OP1 and the like. Since the edge of the opening OP1 and the edge of the opening OP2 are brazed so as to be watertight, the refrigerant does not flow into the cooling water flow path 200.

The above-described flow paths that are formed to supply the refrigerant to the respective refrigerant flow paths 100, that is, the cylindrical flow paths that are formed so that the refrigerant flows through the openings OP1 and the like are hereinafter referred to as “ Also referred to as “supply channel SP”. Such a supply flow path SP is a flow formed so as to penetrate a plurality of plate-like members (cup 151 and inner plate 152) along the direction in which the refrigerant flow path 100 and the cooling water flow path 200 are laminated. Road.

In the cup 151, an opening (not shown) is formed at a position opposite to the opening OP 1 on the diagonal line (a position denoted by reference numeral P 1 in FIG. 2). The shape of the opening is the same as the shape of the opening OP1. In addition, an opening (not shown) is also formed in the inner plate 152 at a position opposite to the opening OP2 on the diagonal line. The shape of the opening is the same as the shape of the opening OP2. Also at this position (P1), the cup 151 and the inner plate 152 in which the cooling water flow path 200 is formed are brazed in a state where the edges of the respective openings are overlapped with each other. The refrigerant supplied from the refrigerant inflow portion 101 passes through the respective refrigerant flow paths 100, and then merges again at a position denoted by reference symbol P1, and flows downward through the opening.

Although not shown, the flow path through which the cooling water supplied from the cooling water inflow portion 201 flows is also formed in the same manner as described above. Specifically, a circular opening is formed in the cup 151 at a position directly above the cooling water inflow portion 201. Similarly, a circular opening is also formed in the inner plate 152 at a position directly above the cooling water inflow portion 201. The cup 151 and the inner plate 152 in which the refrigerant flow path 100 is formed are brazed in a state where the edges of the openings are overlapped with each other. For this reason, the cooling water flowing in from the cooling water inflow portion 201 is distributed to the respective cooling water flow paths 200 while flowing upward through the openings. Since the edges of the openings are brazed so as to be watertight, the cooling water does not flow into the coolant channel 100.

In the cup 151, an opening (not shown) is also formed at a position on the opposite side of the opening directly above the cooling water inflow portion 201 (a position denoted by reference numeral P2 in FIG. 2). In addition, an opening (not shown) is formed at a position on the inner plate 152 opposite to the opening directly above the cooling water inflow portion 201 on the diagonal line. Also at this position (P2), the cup 151 and the inner plate 152 in which the coolant channel 100 is formed are brazed in a state where the edges of the respective openings are overlapped with each other. The refrigerant supplied from the cooling water inflow portion 201 passes through the respective cooling water flow paths 200, and then merges again at a position denoted by reference symbol P2, and flows upward through the opening.

Specific shapes of the cup 151 and the inner plate 152 in the vicinity of the supply flow path SP will be described with reference to FIG. In FIG. 4, illustration of the inner fins 300 disposed in each of the refrigerant channel 100 and the cooling water channel 200 is omitted. Further, in FIG. 4, for convenience of explanation, the diameter of the supply flow path SP is drawn so as to be smaller than the actual diameter shown in FIG. 3. In FIG. 4, the direction in which the refrigerant flows in the supply flow path SP is indicated by an arrow A01. In addition, the direction in which the refrigerant flowing into the refrigerant channel 100 from the supply channel SP flows is indicated by an arrow A02.

Each cup 151 has the same shape, and each inner plate 152 has the same shape. Therefore, in the following, the shape of the cup 151 marked with the symbol “α” and the shape of the inner plate 152 marked with the symbol “β” will be described. The cup 151 and the inner plate 152 partition the refrigerant flow path 100 shown in the center in the vertical direction in FIG.

The cup 151 has a heat exchange part 151a, an inlet part 151b, and a connection part 151c. The heat exchanging portion 151a occupies most of the cup 151, and is a portion where heat is exchanged between the refrigerant and the cooling water. The entire heat exchanging portion 151a has a flat plate shape and is perpendicular to the direction in which the supply flow path SP extends (the vertical direction in FIG. 4).

The inlet portion 151b is a portion of the cup 151 in the vicinity of the supply flow path SP. That is, it is a part of the cup 151 that surrounds the periphery of the supply flow path SP in a top view. The inlet portion 151b has a flat plate shape as a whole like the heat exchange portion 151a, and is perpendicular to the direction in which the supply flow path SP extends.

The direction in which the refrigerant flows in the supply flow path SP (that is, the direction indicated by the arrow A01) is hereinafter also referred to as “forward direction”. The direction opposite to the forward direction is also referred to as “reverse direction” below. The position where the inlet portion 151b is disposed is on the forward direction side relative to the position where the heat exchange portion 151a is disposed. The distance between the heat exchanging portion 151a and the inlet portion 151b along the forward direction (the distance between the surfaces defining the refrigerant flow path 100) is shown as “D11” in FIG.

The connecting portion 151c is a portion formed so as to connect the heat exchanging portion 151a and the inlet portion 151b. The connecting portion 151c is inclined with respect to the heat exchanging portion 151a and the inlet portion 151b. Specifically, the connection portion 151c is inclined with respect to the heat exchanging portion 151a and the like so that the width of the refrigerant passage 100 (the vertical dimension in FIG. 4) decreases as the distance from the supply passage SP increases. .

The inner plate 152 has the heat exchange part 152a, the inlet part 152b, and the connection part 152c similarly to said cup 151. FIG. The heat exchanging portion 152a occupies most of the inner plate 152, and the heat exchanging portion 152a, which is a portion where heat is exchanged between the refrigerant and the cooling water, has a flat plate shape as a whole. It is perpendicular to the direction in which the supply channel SP extends (the vertical direction in FIG. 4). The heat exchanging part 152a is opposed to the heat exchanging part 151a with the refrigerant channel 100 interposed therebetween.

The inlet portion 152b is a portion of the inner plate 152 in the vicinity of the supply flow path SP. That is, it is a portion of the inner plate 152 surrounding the supply channel SP in a circular shape when viewed from above. The inlet portion 152b has a flat plate shape as in the heat exchanging portion 152a, and is perpendicular to the direction in which the supply flow path SP extends. The inlet portion 152b is opposed to the inlet portion 151b with the refrigerant channel 100 interposed therebetween.

Further, the inlet portion 152b is in contact with the inlet portion 151b of the cup 151 on the opposite side of the cup 151 with the symbol “α” (the cup 151 on the upper side in FIG. 4), and the inlet portion 151b Are joined (brazed). That is, in this embodiment, a pair of adjacent plate-like members (cup 151 and inner plate 152) are joined in a state where the

respective inlet portions

151b and 152b are in contact with each other.

The position where the inlet part 152b is disposed is on the opposite side of the position where the heat exchange part 152a is disposed. The distance between the heat exchange part 152a and the inlet part 152b along the reverse direction (the distance between the surfaces that define the refrigerant flow path 100) is shown as “D12” in FIG.

The connection part 152c is a part formed so as to connect the heat exchange part 152a and the inlet part 152b. The connection part 152c is inclined with respect to the heat exchange part 152a and the inlet part 152b. Specifically, the connection part 152c is inclined with respect to the heat exchange part 152a and the like so that the width of the refrigerant flow path 100 (the vertical dimension in FIG. 4) decreases as the distance from the supply flow path SP increases. .

The connecting portion 152c is opposed to the connecting portion 151c with the refrigerant channel 100 interposed therebetween. As described above, the connection part 151c and the connection part 152c are inclined with respect to the heat exchange part 151a and the like. As a result, the pair of connecting

portions

151c and 152c that are adjacent to each other across the coolant channel 100 are formed so as to be closer to each other as the distance from the supply channel SP increases.

In the configuration as described above, a portion of the refrigerant flow channel 100 in the vicinity of the supply flow channel SP expands in both the forward direction and the reverse direction as compared with other portions of the refrigerant flow channel 100. Is formed. As a result, the width (D2) of the refrigerant flow path 100 in the part sandwiched between the inlet part 151b and the inlet part 152b is the width of the refrigerant flow path 100 in the part sandwiched between the heat exchange part 151a and the heat exchange part 152a. It is larger than (D1). In this embodiment, the relationship of D2 = D1 + D11 + D12 is established.

In the present embodiment, the amount of expansion in the forward direction (that is, D11) and the amount of expansion in the reverse direction (that is, D12) in the portion near the supply channel SP in the refrigerant channel 100 are The above portion of the coolant channel 100 is formed so as to be equal to each other. The effect of the cup 151 and the inner plate 152 being formed in the above shape will be described later.

In addition, in this embodiment, each cup 151 and the inner plate 152 are formed so that it may become the same as the above also about the shape of the cooling water flow path 200. That is, in this embodiment, the shape of each cooling water flow path 200 is substantially the same as the shape of the refrigerant flow path 100 as described above. Instead of such an aspect, an aspect in which the shape of the coolant channel 100 and the shape of the cooling water channel 200 are different from each other may be employed.

In FIG. 5, the path through which the refrigerant flows through the heat exchanger 10 is indicated by a solid arrow A11 or the like. Further, a path through which the cooling water flows through the heat exchanger 10 is indicated by a dashed-dotted arrow A21 or the like. In the present embodiment, the upper part and the lower part of the heat exchanger 10 are configured such that the directions in which the refrigerant flows are different from each other. Hereinafter, the upper portion of the heat exchanger 10, that is, the portion where the refrigerant inflow portion 101 and the cooling water outflow portion 202 are provided is also referred to as “first heat exchange portion 11”. Further, the lower part of the heat exchanger 10, that is, the part provided with the refrigerant outflow part 102 and the cooling water inflow part 201 is also referred to as “second heat exchange part 12”. In FIG. 1, the range AR1 of the first heat exchange unit 11 and the range AR2 of the second heat exchange unit 12 are indicated by arrows, respectively.

At a position serving as a boundary between the first heat exchange section 11 and the second heat exchange section 12, a flow path (supply flow path SP) extending downward from the refrigerant inflow section 101 and upward from the refrigerant outflow section 102 And the flow path that extends. That is, the container 15 arranged at the position functions as a partition plate. On the other hand, at the position denoted by reference numeral P1 in FIG. 2, a flow path (flow path formed by a circular opening) that connects between the first heat exchange section 11 and the second heat exchange section 12 is formed. Yes.

Similarly, in the position which becomes a boundary of the 1st heat exchanging part 11 and the 2nd heat exchanging part 12, the flow path extended upwards from cooling water inflow part 201, and downward from cooling water outflow part 202 A space between the extending channel is blocked. On the other hand, at the position denoted by reference numeral P2 in FIG. 2, a flow path (flow path formed by a circular opening) that connects between the first heat exchange section 11 and the second heat exchange section 12 is formed. Yes.

Referring to FIG. 5, the path through which the refrigerant flows through the heat exchanger 10 will be described. The refrigerant supplied from the refrigerant inflow portion 101 to the first heat exchanging portion 11 flows downward through the supply passage SP such as the opening OP1 formed in the cup 151 (arrow A11). In that case, a refrigerant | coolant is distributed to each refrigerant flow path 100, and flows through the refrigerant flow path 100 toward the opposite side on the diagonal of the container 15 (arrow A12). Thereafter, the refrigerants flowing through the respective refrigerant flow paths 100 merge again, and flow through the flow path formed by the circular opening from the first heat exchange unit 11 toward the second heat exchange unit 12 (arrow A13).

The refrigerant is again distributed from the supply flow path SP to the respective refrigerant flow paths 100 in the second heat exchange section 12, and flows through the refrigerant flow path 100 toward the opposite side on the diagonal line of the container 15 (arrow A14). Thereafter, the refrigerants flowing through the respective refrigerant flow paths 100 merge again, and flow through the flow path formed by the circular opening toward the refrigerant outflow portion 102 (arrow A15). Eventually, the refrigerant is discharged from the refrigerant outflow portion 102 to the outside.

The path through which the cooling water flows through the heat exchanger 10 will be described with reference to FIG. The cooling water supplied from the cooling water inflow portion 201 to the second heat exchange portion 12 flows upward through an opening formed in the cup 151 and the like (arrow A21). At that time, the cooling water is distributed to the respective cooling water flow paths 200 and flows through the cooling water flow paths 200 toward the opposite side on the diagonal line of the container 15 (arrow A22). Thereafter, the cooling water that has flowed through the respective cooling water flow paths 200 merges again, and flows through the flow path formed by the circular opening from the second heat exchange unit 12 toward the first heat exchange unit 11 (arrow A23).

The cooling water is again distributed to the respective cooling water flow paths 200 in the first heat exchange unit 11, and flows through the cooling water flow paths 200 toward the opposite side on the diagonal line of the container 15 (arrow A24). Thereafter, the refrigerant that has flowed through the respective cooling water flow paths 200 merges again, and flows through the flow path formed by the circular opening toward the cooling water outflow portion 202 (arrow A25). Finally, the cooling water is discharged from the cooling water outflow portion 202 to the outside.

As already described, the refrigerant flow path 100 and the cooling water flow path 200 are arranged so as to alternately overlap. For this reason, in the 1st heat exchange part 11, heat exchange is performed between the refrigerant | coolant (arrow A12) which flows through the refrigerant flow path 100, and the cooling water (arrow A24) which flows through the cooling water flow path 200. FIG. Similarly, also in the 2nd heat exchange part 12, heat exchange is performed between the refrigerant | coolant (arrow A14) which flows through the refrigerant flow path 100, and the cooling water (arrow A22) which flows through the cooling water flow path 200. FIG.

The configuration and arrangement of the inner fin 300 will be described with reference to FIGS. FIG. 6A shows the entire inner fin 300 disposed in the refrigerant flow path 100 of the first heat exchange unit 11 in a top view. FIG. 6B shows the entire inner fin 300 disposed in the cooling water flow path 200 of the first heat exchange unit 11 in a top view. The shapes of the inner fins 300 in a top view are symmetrical to each other in the vertical direction of FIG. As shown in FIG. 7, the inner fin 300 is formed by bending a single metal plate.

As shown in FIG. 6 (A), the outer shape of the inner fin 300 in the top view is substantially equal to the shape of the internal space of the container 15 in the top view. The inner fin 300 is disposed so as to occupy substantially the entire coolant channel 100.

In the inner fin 300, an opening is formed at a position directly below the refrigerant inflow portion 101 (a position denoted by reference numeral 111 in FIG. 6A). The opening is a part that receives the refrigerant from the refrigerant inflow portion 101 and serves as an inlet of the refrigerant to the refrigerant flow path 100. Hereinafter, a portion where an opening serving as a refrigerant inlet to the refrigerant flow path 100 is formed is referred to as a “refrigerant inlet 111” of the refrigerant flow path 100. The portion where the refrigerant inlet 111 is formed in the first heat exchanging portion 11 corresponds to the portion where the refrigerant flows along the arrow A11 in FIG.

In the inner fin 300, an opening is formed at a position immediately below a portion denoted by reference numeral P1 in FIG. 2 (position denoted by reference numeral 112 in FIG. 6A). The opening is a part into which the refrigerant flows through the refrigerant channel 100, that is, a part serving as an outlet of the refrigerant from the refrigerant channel 100. Hereinafter, a portion where an opening serving as a refrigerant outlet from the refrigerant channel 100 is formed is referred to as a “refrigerant outlet 112” of the refrigerant channel 100. The portion where the refrigerant outlet 112 is formed in the first heat exchange unit 11 corresponds to a portion where the refrigerant flows along the arrow A13 in FIG.

Thus, in this embodiment, the refrigerant inlet 111 that is the refrigerant inlet to the refrigerant flow path 100 and the refrigerant outlet 112 that is the refrigerant outlet from the refrigerant flow path 100 are in the longitudinal direction of the container 15 (FIG. 6). In (A), they are arranged separately on one side and the other side in the left-right direction). In FIG. 6A, the flow of the refrigerant from the refrigerant inlet 111 toward the refrigerant outlet 112 is indicated by an arrow. However, what is indicated by an arrow is a rough flow of the refrigerant, and the actual flow of the refrigerant is not such a linear flow.

Note that, as shown in FIG. 6B, at the positions of the refrigerant inlet 111 and the refrigerant outlet 112 as described above, an opening is also formed in the inner fin 300 arranged in the cooling water flow path 200. These are formed so that the coolant flows through the cooling water flow path 200 along the stacking direction of the containers 15. In this portion, for example, as shown in FIG. 3, the opening edge of the cup 151 and the opening edge of the inner plate 152 are welded. For this reason, the refrigerant passing through the refrigerant inlet 111 or the like does not flow into the cooling water flow path 200.

As shown in FIG. 6 (B), the inner fin 300 is arranged so as to occupy substantially the entire cooling water channel 200.

In the inner fin 300, an opening is formed at a position (position denoted by reference numeral 211 in FIG. 6B) that is directly below the portion denoted by reference numeral P2 in FIG. The opening is a part that receives the cooling water from the second heat exchange unit 12 and is a part that serves as an inlet of the cooling water to the cooling water flow path 200. Hereinafter, a portion where an opening serving as an inlet of the cooling water to the cooling water channel 200 is formed is referred to as a “cooling water inlet 211” of the cooling water channel 200. A portion where the cooling water inlet 211 is formed in the first heat exchange unit 11 corresponds to a portion where the cooling water flows along the arrow A 23 in FIG. 5.

In the inner fin 300, an opening is formed at a position directly below the cooling water outflow portion 202 (a position denoted by reference numeral 212 in FIG. 6B). The opening is a part into which cooling water flows through the cooling water channel 200, that is, a part serving as an outlet for cooling water from the cooling water channel 200. Hereinafter, a portion where an opening serving as an outlet for cooling water from the cooling water flow path 200 is formed is referred to as a “cooling water outlet 212” of the cooling water flow path 200. The part where the cooling water outlet 212 is formed in the first heat exchange unit 11 corresponds to the part where the cooling water flows along the arrow A25 in FIG.

Thus, in this embodiment, the cooling water inlet 211 that is the inlet of the cooling water to the cooling water passage 200 and the cooling water outlet 212 that is the outlet of the cooling water from the cooling water passage 200 are the longitudinal length of the container 15. They are arranged separately on one side and the other side in the direction (left-right direction in FIG. 6B). In FIG. 6B, the flow of cooling water from the cooling water inlet 211 toward the cooling water outlet 212 is indicated by arrows. However, an arrow indicates a rough flow of the cooling water, and the actual flow of the cooling water is not such a linear flow.

Note that, as shown in FIG. 6A, at the positions of the cooling water inlet 211 and the cooling water outlet 212 as described above, openings are also formed in the inner fins 300 arranged in the refrigerant flow path 100. These are formed so that the cooling water flows through the coolant channel 100 along the stacking direction of the containers 15. In this portion, for example, as shown in FIG. 3, the opening edge of the cup 151 and the opening edge of the inner plate 152 are welded. For this reason, the cooling water passing through the cooling water inlet 211 or the like does not flow into the refrigerant flow path 100.

The arrangement of the inner fins 300 in the second heat exchange unit 12 and the flow of refrigerant and cooling water flowing through the second heat exchange unit 12 are the same as those in the first heat exchange unit 11 described above. . Therefore, the specific description is abbreviate | omitted.

As described above, in the present embodiment, the refrigerant inlet 111 and the cooling water outlet 212 are arranged on one side (left side in FIG. 6) in the longitudinal direction of the container 15, and the cooling water inlet 211, the refrigerant outlet 112, However, it is arrange | positioned at the other side (right side in FIG. 6) in the longitudinal direction of the container 15. As shown in FIG. In the present embodiment, the direction from the refrigerant inlet 111 to the refrigerant outlet 112 is inclined with respect to the longitudinal direction of the container 15, and the direction from the cooling water inlet 211 to the cooling water outlet 212 is also the longitudinal direction of the container 15. It is inclined with respect to. With such a configuration, the refrigerant flow in the refrigerant flow path 100 and the cooling water flow in the cooling water flow path 200 intersect with each other in an X shape. That is, the flow of the refrigerant and the cooling water in the present embodiment is a so-called “X-shaped counter flow”.

The specific shape of the inner fin 300 will be described. As shown in FIG. 7, the inner fin 300 is formed by bending a single metal plate so that crests 310 and troughs 320 are alternately arranged. The crest 310 is a part that abuts on one of the cup 151 and the inner plate 152 that divides the refrigerant flow path 100 and the like, and the trough 320 is a part that abuts on the other of the cup 151 and the inner plate 152. The crest portion 310 and the trough portion 320 are parallel to each other, and the normal direction of the main surface thereof coincides with the stacking direction of the container 15 (the vertical direction in FIG. 1).

The adjacent mountain portions 310 and valley portions 320 are connected by a side wall portion 330. The side wall part 330 is a wall perpendicular to each of the peak part 310 and the valley part 320. Each side wall part 330 is arrange | positioned mutually parallel. In the present embodiment, a plurality of side walls 330 divide a fluid flow path (refrigerant flow path 100 or cooling water flow path 200) into a plurality of sections. As a result, a fluid passage 370 extending linearly is formed between the side wall portions 330 adjacent to each other.

7, the direction in which the fluid passage 370 extends is indicated by an arrow A30. The direction in which the plurality of fluid passages 370 are arranged, that is, the normal direction of the side wall 330 is indicated by an arrow A40.

A plate-like louver portion 340 is formed on each side wall portion 330 by cutting and raising a part thereof. The shape of the louver part 340 is a rectangle, and is connected to the peak part 310 or the valley part 320 on one side. A plurality of louver portions 340 are formed, and all of them are parallel to the direction in which the fluid passage 370 extends (arrow A30). Each louver portion 340 protrudes from the side wall portion 330 into the fluid passage 370.

Further, an opening 350 as a result of cutting and raising the louver portion 340 is also formed in the side wall portion 330. Adjacent fluid passages 370 communicate with each other through openings 350. The louver portion 340 protrudes from the edge of each opening 350 into the fluid passage 370. A plurality of louver portions 340 and openings 350 are formed in a line along the direction (arrow A30) in which the fluid passage 370 extends.

As shown in FIG. 7, all the louver parts 340 are connected to the mountain part 310 in the side wall part 330 to which the reference numeral 331 is attached. Hereinafter, such a side wall portion 330 is also referred to as a “side wall portion 331”. Moreover, in the side wall part 330 to which the code | symbol 332 is attached | subjected, all the louver parts 340 are in the state connected with the trough part 320. FIG. Hereinafter, such a side wall portion 330 is also referred to as a “side wall portion 332”. In the present embodiment, the side wall portions 331 and the side wall portions 332 are arranged so as to be alternately arranged along the direction of the arrow A40.

In each of the side wall portions 330, a portion where the louver portion 340 and the opening 350 are formed and a portion where the louver portion 340 and the opening 350 are not formed are along the direction in which the fluid passage 370 extends (arrow A30). It is formed so that it may line up alternately.

The explanation will be continued referring to FIG. 6 again. In the coolant channel 100 and the cooling water channel 200, the inner fin 300 is disposed in a state where the direction in which the fluid passage 370 extends (arrow A 30) matches the longitudinal direction of the container 15. For this reason, for example, in the refrigerant flow path 100 shown in FIG. 5A, the refrigerant flowing in from the refrigerant inlet 111 flows substantially along the longitudinal direction of the container 15. At that time, a part of the refrigerant flows into the adjacent fluid passage 370 through the opening 350. That is, the refrigerant flow includes a linear flow along the fluid passage 370 and a diffusive flow that passes through the opening 350. In the refrigerant flow path 100, the path through which the refrigerant diffuses and flows is secured as described above, so that heat exchange between the refrigerant and the cooling water flowing through the adjacent cooling water flow path 200 is performed efficiently.

A part of the refrigerant flowing through the refrigerant flow path 100 collides with the edge of the louver part 340, and the flow is divided. Further, the other part of the refrigerant collides with the edge of the opening 350 and the flow is also divided. Such a flow division causes a so-called leading edge effect, so that heat transfer to the refrigerant through the inner fins 300 is performed efficiently.

Further, in the portion of the inner fin 300 where the louver portion 340 is formed, the refrigerant pressure becomes relatively high due to the occurrence of the refrigerant collision as described above. On the other hand, in the portion of the inner fin 300 where the louver portion 340 is not formed, the refrigerant flows substantially linearly without colliding with the louver portion 340 and the like, so the pressure of the refrigerant becomes relatively low. For this reason, the pressure of the refrigerant flowing through the fluid passage 370 is high in the portion where the louver portion 340 is formed, and is low in the portion where the louver portion 340 is not formed. In other words, the fluid flowing along the fluid passage 370 flows while repeatedly increasing and decreasing its pressure.

¡Diffusion of fluid through the opening 350 is promoted due to such a change in pressure. That is, in the heat exchanger 10 according to the present embodiment, the refrigerant is not actively diffused due to an external force such as a driving force of the pump, but is passively caused by the pressure fluctuation. Diffusion will occur. Thereby, the diffusibility of the refrigerant can be enhanced while suppressing the pressure loss of the refrigerant, and as a result, good heat exchange performance is exhibited.

The above-described effects by disposing the inner fin 300 are also exhibited in the cooling water flow in the cooling water channel 200. That is, also in the cooling water flow path 200, the diffusibility of the cooling water is enhanced by the inner fins 300.

The flow of the refrigerant distributed from the supply flow path SP to each refrigerant flow path 100 will be described with reference to FIG. In FIG. 8, similarly to FIG. 4, the direction in which the refrigerant flows in the supply flow path SP is indicated by an arrow A01. In addition, the direction in which the refrigerant flowing into the refrigerant channel 100 from the supply channel SP flows is indicated by an arrow A02.

The refrigerant flowing through the supply flow path SP is in a gas-liquid mixed state. However, in the supply flow path SP, the gas-phase refrigerant and the liquid-phase refrigerant are not evenly distributed. According to what the present inventors have confirmed by simulation and the like, when the refrigerant flows through the supply flow path SP at a normal speed, a large amount of gas-phase refrigerant tends to flow in the central portion of the supply flow path SP. In the surroundings, a large amount of liquid-phase refrigerant tends to flow. In FIG. 8, a rough boundary between a region where a large amount of gas-phase refrigerant flows and a region where a large amount of liquid-phase refrigerant flows is indicated by a pair of dotted lines DL1. In the portion between the respective dotted lines DL1, a large amount of gas phase refrigerant flows. In the region outside the respective dotted lines DL1 (on the heat exchanging portion 151a side), a large amount of liquid-phase refrigerant flows.

The supply flow path SP has a shape in which the flow path cross-sectional area is narrowed at the

inlet portions

151b and 152b. For this reason, the refrigerant flowing along the supply channel SP along the arrow A01 increases its pressure when passing through the vicinity of the

inlet portions

151b and 152b (the position of the point P11 in FIG. 8).

As already described, in the present embodiment, the portion of the refrigerant flow channel 100 near the supply flow channel SP expands in both the forward direction and the reverse direction compared to the other portions of the refrigerant flow channel 100. It is formed to do. For this reason, the pressure of the refrigerant flowing along the supply channel SP along the arrow A01 is released immediately after passing through the vicinity of the

inlet portions

151b and 152b. The pressure of the refrigerant flowing through the supply flow path SP is lowest when passing through a position (position of a point P12 in FIG. 8) that coincides with the center of the refrigerant flow path 100 along the forward direction.

Note that a relatively large pressure drop occurs at the position of the point P12 as compared with the diameter of the supply flow path SP in terms of the size of the refrigerant flow path 100 in the top view (specifically, the short length of the refrigerant flow path 100). This is also due to the sufficiently large dimensions in the direction and the longitudinal direction).

The refrigerant whose pressure has been released has a velocity component in the direction of diffusing in the left-right direction in FIG. In FIG. 8, such a refrigerant flow is indicated by an arrow A102. A part of the refrigerant flowing along the arrow A102 collides with the inlet portion 151b, thereby generating a turbulent refrigerant flow. As a result, a relatively large vortex is generated in a wide space formed between the inlet portion 151b and the inlet portion 152b arranged on the upstream side (the upper side in FIG. 8). In FIG. 8, the flow of the refrigerant that forms such a vortex is indicated by an arrow A101.

The refrigerant flowing inside the dotted line DL1 and the refrigerant flowing outside the dotted line DL are mixed by the vortex indicated by the arrow A101. That is, the gas phase refrigerant and the liquid phase refrigerant are sufficiently mixed at the inlet portion of each refrigerant flow path 100. As a result, the gas-liquid mixing ratio of the refrigerant flowing into the respective refrigerant flow paths 100 is substantially uniform for all the refrigerant flow paths 100.

In the present embodiment, the pressure loss of the refrigerant passing through the heat exchanger 10 is reduced because each refrigerant channel 100 is enlarged in the vicinity of the supply channel SP. According to experiments and simulations conducted by the present inventors, the pressure loss of the refrigerant is reduced by 22% compared to a heat exchanger in which the refrigerant channel 100 is not enlarged in the vicinity of the supply channel SP. Has been confirmed.

As already described with reference to FIG. 4, in the present embodiment, in the portion near the supply flow path SP in the refrigerant flow path 100, the amount of expansion (D11) directed in the forward direction and the reverse direction. The cup 151 and the like are formed so that the enlargement amount (D12) is equal to each other. In such a configuration, since a larger vortex is likely to be formed at the inlet portion of each refrigerant flow path 100, the gas-liquid mixing ratio of the refrigerant flowing into each refrigerant flow path 100 may be made more uniform. it can.

In the present embodiment, the pair of

connection portions

151c and 152c adjacent to each other across the coolant channel 100 are formed so as to be closer to each other as the distance from the supply channel SP increases. In such a configuration, the depth of the space formed to expand at the inlet portion of the refrigerant flow path 100 is deep. As a result, a larger refrigerant vortex is likely to be formed along the

inlet portions

151b and 152b and the connecting

portions

151c and 152c.

The

inlet portions

151b and 152b and the

heat exchange portions

151a and 152a in this embodiment are all formed so as to be perpendicular to the direction in which the supply flow path SP extends. In other words, all of them are formed so as to be parallel to each other. As a result, the shapes of the respective refrigerant flow paths 100 can be made the same, and the heat exchange in the heat exchanger 10 can be performed uniformly throughout.

FIG. 9 shows the flow of the refrigerant in the heat exchanger 10 according to the comparative example. In this comparative example, the shape of the cup 151 is substantially the same as that of the above-described embodiment, while the shape of the inner plate 152 is entirely flat and is different from the above-described embodiment only in this respect. That is, in this comparative example, a portion of the refrigerant flow channel 100 near the supply flow channel SP is formed so as to expand only in the forward direction as compared with other portions of the refrigerant flow channel 100.

Even in such a configuration, a somewhat wide space is formed at the inlet portion of the refrigerant flow path 100, and a vortex of the refrigerant is formed in the space. However, since the width of the space is small compared to the above embodiment, the vortex of the formed refrigerant is also small. In FIG. 9, the flow of the refrigerant forming such a vortex is indicated by an arrow A111.

As a result, the gas phase refrigerant and the liquid phase refrigerant are not sufficiently mixed at the inlet portion of the refrigerant flow path 100. As a result, a larger amount of liquid-phase refrigerant may flow into some of the refrigerant flow paths 100, while a larger amount of gas-phase refrigerant may flow into other refrigerant flow paths 100.

Another comparative example will be described with reference to FIG. In this comparative example, the width of the refrigerant flow path 100 is substantially uniform as a whole, and the refrigerant flow path 100 is not enlarged even in the vicinity of the supply flow path SP in the refrigerant flow path 100. In such a configuration, the refrigerant vortex is hardly formed at the inlet portion of the refrigerant flow path 100. The gas-phase refrigerant and the liquid-phase refrigerant flow through the supply flow path SP while being unevenly distributed, and are supplied to the respective refrigerant flow paths 100 without being mixed. For this reason, as in the comparative example of FIG. 9, a larger amount of liquid-phase refrigerant flows into some of the refrigerant flow paths 100, while a larger amount of gas-phase refrigerant flows into other refrigerant flow paths 100. It can happen.

In contrast to these comparative examples, in the present embodiment, a relatively large vortex is formed at the inlet portion of the refrigerant flow path 100, so that the gas-liquid mixing ratio of the refrigerant flowing into the refrigerant flow path 100 is set to The road 100 can be generally uniform. The large vortex is formed because the portion near the supply flow path SP in the refrigerant flow path 100 is formed so as to expand in both the forward direction and the reverse direction (not one). Is attributed.

The embodiment has been described above with reference to specific examples. However, the present disclosure is not limited to these specific examples. Those in which those skilled in the art appropriately modify the design of these specific examples are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each of the specific examples described above and their arrangement, conditions, shape, and the like are not limited to those illustrated, and can be changed as appropriate. Each element included in each of the specific examples described above can be appropriately combined as long as no technical contradiction occurs.

Claims

A heat exchanger (10) for exchanging heat between a first fluid and a second fluid,
The first channel and the first channel so that the first channel (100) through which the first fluid flows and the second channel (200) through which the second fluid flows are alternately stacked. A plurality of plate-like members (151 and 152) that partition between the two flow paths are provided,
A supply channel (SP) for supplying the first fluid to each of the first channels has a plurality of plates along a direction in which the first channel and the second channel are stacked. It is formed so as to penetrate the member,
When the direction in which the first fluid flows in the supply flow path is the forward direction, and the direction opposite to the forward direction is the reverse direction,
A portion of the first flow path in the vicinity of the supply flow path is formed so as to expand toward both the forward direction and the reverse direction as compared with other portions of the first flow path. Heat exchanger.
The portion of the first flow path in the vicinity of the supply flow path is formed such that the expansion amount toward the forward direction and the expansion amount toward the reverse direction are equal to each other. The heat exchanger as described in.
Each of the plate members is
An inlet portion (151b, 152b) which is a portion in the vicinity of the supply flow path;
A heat exchange part (151a, 152a) that is a part where heat exchange is performed between the first fluid and the second fluid;
A connecting portion (151c, 152c) that is a portion connecting the inlet portion and the heat exchanging portion,
3. The heat exchanger according to claim 1, wherein the pair of adjacent plate-like members are joined in a state where the respective inlet portions are in contact with each other.
The heat exchanger according to claim 3, wherein each of the inlet portion and the heat exchange portion is formed to be perpendicular to a direction in which the supply flow path extends.
The heat exchanger according to claim 3 or 4, wherein the pair of connection portions adjacent to each other across the first flow path is formed so as to approach each other as the distance from the supply flow path increases.