JP6497262B2 - Laminate heat exchanger - Google Patents

Description

  The present invention relates to a stacked heat exchanger that exchanges heat between a refrigerant of a refrigeration cycle and a heat medium.

  Conventionally, a plurality of substantially flat plate-shaped heat transfer plates are overlapped at an interval to alternately form a refrigerant channel and a heat medium channel between the heat transfer plates to exchange heat between the refrigerant and the heat medium. A laminated heat exchanger is known. In such a stacked heat exchanger, Patent Document 1 discloses an integrated cylindrical modulator that separates the gas-liquid refrigerant flowing out of the heat exchanger and stores the refrigerant.

German Patent Application Publication No. 102011078136

  However, in the stacked heat exchanger described in Patent Document 1, a cylindrical modulator is integrated on the outside of a substantially case-shaped heat exchanger. For this reason, the physique increases in size, and a space where nothing is arranged at the time of mounting, a so-called dead space is generated. Furthermore, when a case-like heat exchanger that supercools the liquid refrigerant flowing out of the modulator is added to such a modulator-integrated heat exchanger, there is a problem that the size of the heat exchanger is further increased.

  In view of the above points, the present invention provides a stacked heat exchanger including a gas-liquid separation unit that separates gas-liquid refrigerant and a supercooling unit that supercools liquid-phase refrigerant that has flowed out of the gas-liquid separation unit. The purpose is to reduce the dead space on the mounting as well as to reduce the size.

In order to achieve the above object, according to the first aspect of the present invention, the heat exchange section (1) for exchanging heat between the refrigerant of the refrigeration cycle and the heat medium, and the gas-liquid of the refrigerant flowing into the inside are separated and the refrigeration cycle. A gas-liquid separator (2) that stores excess refrigerant therein, and the heat exchange part (1) is formed by laminating and joining a plurality of first plate-like members (11) to each other, A plurality of refrigerant passages (12) through which a refrigerant flows and a plurality of heat medium passages (13) through which a heat medium flows are formed between the plurality of first plate members (11). (12) and the plurality of heat medium passages (13) are arranged in the stacking direction of the plurality of first plate-like members (11), and the longitudinal direction of the refrigerant passage (12) and the heat medium passage (13). Is the same as the longitudinal direction of the first plate-like member (11) A refrigerant passage (12), condensing unit to the gas-phase refrigerant and the heat medium is condensed vapor phase refrigerant by heat exchange with (121), and a liquid phase refrigerant separated into gas and liquid by the gas-liquid separation section (2) supercooling part that the heat medium by heat exchange supercooled liquid phase refrigerant (122) is provided side by side in the longitudinal direction of the direction and the refrigerant passage perpendicular to the stacking direction (12), the refrigerant passage ( 12), the refrigerant flows from the condensing part (121) side toward the supercooling part (122) side, and in the heat medium passage (13), the heat medium passes from the supercooling part (122) side to the condensing part (121). ) Side, in the refrigerant passage (12), the condensing part (121) and the supercooling part (122) are partitioned by the heat insulating part (123), and the heat insulating part (123) 13) Projection formed on the first plate member (11) so that the side is recessed (112), and the heat insulating portion (123) extends over the entire area of the refrigerant passage (12) in a direction orthogonal to the stacking direction and in a direction orthogonal to the longitudinal direction of the refrigerant passage (12). The portion (123) constitutes a part of the heat medium passage (13), and the heat medium is circulated in the heat insulating portion (123), and the refrigerant is placed in the heat medium passage (13). The heat medium side inner fin (53) that promotes heat exchange between the heat medium and the heat medium is provided, and the heat medium is introduced into the heat insulating part (123) from the gap between the walls of the heat medium side inner fin (53). It is characterized by inflow .

  According to this, a condensing part (121) and a supercooling part (122) are provided in a refrigerant | coolant channel | path (12) along with the direction orthogonal to a lamination direction, A some 1st plate-shaped member (11). Both the condensing part (121) and the supercooling part (122) can be arranged in the refrigerant passage (12) formed between them. For this reason, it is not necessary to newly add a housing-like heat exchanger functioning as the supercooling section (122), so that the size of the physique can be reduced and the dead space on mounting can be reduced.

  By the way, when both the condensing part (121) and the supercooling part (122) are arranged in one refrigerant passage (12), the supercooling part (122) is moved by the heat of the high-temperature refrigerant flowing through the condensing part (121). There is a possibility that a thermal damage may occur in which the circulating low-temperature liquid phase refrigerant is heated. On the other hand, in this invention, generation | occurrence | production of a heat damage can be suppressed by partitioning a condensation part (121) and a supercooling part (122) with a heat insulation part (123) in a refrigerant path (12).

In order to achieve the above object, in the invention according to claim 10 , the heat exchange section (1) for exchanging heat between the refrigerant and the heat medium of the refrigeration cycle, and the gas-liquid of the refrigerant flowing into the inside are separated and the refrigeration cycle. And a gas-liquid separator (2) for storing excess refrigerant therein, and the heat exchanging part (1) has a plurality of stacked first plate-like members (11), and the first plate-like member ( 11) A refrigerant passage (12) through which a refrigerant flows or a plurality of heat medium passages (13) through which a heat medium flows is formed between the plurality of first plate-like members (11). A plurality of refrigerant passages (12) through which the refrigerant flows and a plurality of heat medium passages (13) through which the heat medium flows are formed between the first plate-like members (11). A plurality of refrigerant passages (12) and a plurality of heat medium passages (1 ), In the stacking direction of the plurality of first plate-shaped member (11) are arranged alternately in the longitudinal direction of the refrigerant passage (12) and the heat medium passages (13), the first plate member (11) It is the same as the longitudinal direction, and the refrigerant passage (12) is provided with a condensing unit (121) for exchanging heat between the gas-phase refrigerant and the heat medium to condense the gas-phase refrigerant and a gas-liquid separation unit (2). A supercooling section (122) for supercooling the liquid-phase refrigerant by exchanging heat between the gas-liquid separated liquid-phase refrigerant and the heat medium, a refrigerant passage (12) and a heat medium passage ( 13) are arranged side by side in the longitudinal direction , and in the refrigerant passage (12), the refrigerant flows from the condensation section (121) side toward the supercooling section (122) side, and in the heat medium passage (13), The heat medium is directed from the supercooling section (122) side to the condensing section (121) side. Flow, the refrigerant passage (12), between the condensation portion (121) and the supercooling part (122), and the supercooling part condensing unit (121) (122) and the heat insulating portion for insulating the (123) has distribution The heat insulating portion (123) is formed by the protruding portion (112) formed on the first plate member (11) so that the heat medium passage (13) side is recessed, and the heat insulating portion (123) And extending across the entire area of the refrigerant passage (12) in a direction orthogonal to the stacking direction and in a direction orthogonal to the longitudinal direction of the refrigerant passage (12), and the heat insulating portion (123) is one of the heat medium passage (13). The heat medium circulates inside the heat insulation part (123), and the heat medium side inner that promotes heat exchange between the refrigerant and the heat medium is located in the heat medium passage (13). Fins (53) are provided, and the heat medium side inner fin (53 The heat medium flows into the inside of the heat insulating part (123) from the gap between the wall parts .

  According to this, there can exist the same effect as the invention of Claim 1.

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

It is a top view which shows the heat exchanger which concerns on 1st Embodiment. It is sectional drawing which shows the heat exchanger which concerns on 1st Embodiment. It is the III section enlarged view of FIG. It is IV arrow line view of FIG. It is a V arrow view of FIG. It is a perspective view which shows the condensation side inner fin in 1st Embodiment. It is a perspective view which shows the supercooling side inner fin in 1st Embodiment. It is explanatory drawing which shows the surface by the side of the refrigerant path of the 1st plate-shaped member in 1st Embodiment. It is an expanded sectional view showing the important section of the heat exchanger concerning a 2nd embodiment. It is a top view which shows the heat exchanger which concerns on 3rd Embodiment. It is sectional drawing which shows the heat exchanger which concerns on 3rd Embodiment. It is an enlarged plan view which shows the principal part of the heat exchanger which concerns on 3rd Embodiment. It is an expanded sectional view showing the important section of the heat exchanger concerning a 3rd embodiment. It is a XIV arrow line view of FIG. It is a top view which shows the heat exchanger which concerns on 4th Embodiment. It is sectional drawing which shows the heat exchanger which concerns on 4th Embodiment. It is a front view which shows the heat exchanger which concerns on 5th Embodiment. It is a XVIII arrow directional view of FIG. It is XIX-XIX sectional drawing of FIG. FIG. 20 is an enlarged view of XX in FIG. 19. It is sectional drawing which shows the heat exchanger which concerns on 5th Embodiment. It is a front view which shows the heat exchanger in other embodiment (3).

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

(First embodiment)
1st Embodiment of this invention is described based on FIGS. The heat exchanger shown in FIG. 1 constitutes a refrigeration cycle of a vehicle air conditioner. The heat exchanger is a condenser that condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle. Note that the cooling water of the present embodiment corresponds to the heat medium of the present invention.

  As the cooling water, for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid can be used. In this embodiment, ethylene glycol antifreeze (LLC) is used as the cooling water.

  The heat exchanger forms a refrigerant flow path and a heat medium flow path alternately between the heat transfer plates by overlapping a plurality of substantially flat plate heat transfer plates with a space therebetween. Is a stacked heat exchanger for exchanging heat.

  The heat exchanger includes a heat exchanging unit 1 for exchanging heat between the refrigerant of the refrigeration cycle and the cooling water, and a gas-liquid separation unit 2 for separating the gas-liquid of the refrigerant flowing into the interior and storing excess refrigerant in the refrigeration cycle. I have.

As shown in FIGS. 1 and 2, the heat exchange unit 1 is integrally formed by stacking and joining a large number of first plate-like members 11. Hereinafter, the stacking direction of the first plate-like members 11 (the left-right direction in the examples of FIGS. 1 and 2) is referred to as the plate stacking direction. Also, one end side in the plate stacking direction (
The right end side in the examples of FIGS. 1 and 2 is referred to as one end side in the plate stacking direction. The other end side in the plate stacking direction (the left end side in the examples of FIGS. 1 and 2) is referred to as the other end side in the plate stacking direction.

  The first plate member 11 is a long and substantially rectangular metal plate (in this example, made of aluminum or aluminum alloy). The heat exchanger of this embodiment is arrange | positioned so that the longitudinal direction of the 1st plate-shaped member 11 may correspond with the gravity direction.

  On the outer peripheral edge of the substantially rectangular first plate-like member 11, an overhanging portion 111 that protrudes in a substantially plate stacking direction (in other words, a direction substantially orthogonal to the plate surface of the first plate-like member 11) is formed. Has been. The multiple first plate-like members 11 are joined to each other by brazing, with the overhanging portions 111 being laminated together. The multiple first plate-like members 11 are arranged such that the protruding tips of the overhang portions 111 face the same side (substantially right side in the example of FIG. 1).

  As shown in FIG. 2, a plurality of refrigerant passages 12 through which refrigerant flows and a plurality of cooling water passages 13 through which cooling water flows are formed between the plurality of first plate-like members 11. The cooling water passage 13 of the present embodiment corresponds to the heat medium passage of the present invention.

  More specifically, of the two first plate-like members 11 that divide the refrigerant passage 12, one of the first plate-like members 11a is partially directed toward the other first plate-like member 11b. A protruding portion 112 is provided.

  The protrusion 112 is joined to the other first plate member 11b. In other words, of the first plate-like member 11a, the first surface on the side where the protruding portion 112 protrudes, and the other first plate-like member 11b facing the first surface of the first plate-like member 11a. A refrigerant passage 12 is formed between the first plate-like member 11a, a second surface of the first plate-like member 11a opposite to the first surface, and a second surface of the first plate-like member 11a. A cooling water passage 13 is formed between the second surface of the other first plate-like member 11b facing the other.

  The plurality of refrigerant passages 12 and the plurality of cooling water passages 13 are arranged side by side in the plate stacking direction. More specifically, the refrigerant passages 12 and the cooling water passages 13 are alternately stacked (parallelly arranged) one by one in the plate stacking direction. The first plate-like member 11 serves as a partition wall that partitions the refrigerant passage 12 and the cooling water passage 13. Heat exchange between the refrigerant flowing through the refrigerant passage 12 and the cooling water flowing through the cooling water passage 13 is performed via the first plate member 11. The refrigerant passage 12 is disposed on the outermost side in the stacking direction.

  The refrigerant passage 12 exchanges heat between the gas-phase refrigerant and the cooling water to condense the gas-phase refrigerant and the liquid-phase refrigerant and the cooling water separated by the gas-liquid separation unit 2. And a supercooling section 122 that supercools the liquid-phase refrigerant. The condensing unit 121 and the supercooling unit 122 are provided side by side in a direction orthogonal to the plate stacking direction.

  In this embodiment, the condensing part 121 and the supercooling part 122 are provided along with the longitudinal direction of the 1st plate-shaped member 11, ie, the gravity direction. More specifically, in the refrigerant passage 12, the condensing unit 121 is disposed above the supercooling unit 122 in the gravity direction.

  As shown in FIG. 3, the protrusion 112 formed on one first plate-like member 11a is joined to the other first plate-like member 11b. By this projecting portion 112, the refrigerant passage 12 can be partitioned into a condensing portion 121 and a supercooling portion 122. In other words, the protruding portion 112 has a shape in which the cooling water passage 13 side is recessed, and the recessed portion communicates with the cooling water passage 13 and constitutes a part of the cooling water passage 13.

  That is, in the refrigerant passage 12, the condensing unit 121 and the supercooling unit 122 are partitioned by the heat insulating unit 123. The heat insulating portion 123 of this embodiment constitutes a part of the cooling water passage 13.

  Returning to FIGS. 1 and 2, the heat exchanging unit 1 includes the first tank space 14 for condensation, the second tank space 15 for condensation, and the first tank for supercooling in addition to the refrigerant passage 12 and the cooling water passage 13 described above. A space 16, a supercooling second tank space 17, a cooling water first tank space 18, and a cooling water second tank space 19 are provided.

In other words, in addition to the refrigerant passage 12 and the cooling water passage 13 described above, the first plate member 11 includes a first tank space for condensation 14, a second tank space for condensation 15, a first tank space 16 for supercooling, A second tank space 17 for supercooling, a first tank space 18 for cooling water, and a second tank space 19 for cooling water are formed.

  The condensing first tank space 14 and the condensing second tank space 15 distribute and collect the refrigerant to the condensing portions 121 of the plurality of refrigerant passages 12. The first subcooling tank space 16 and the second subcooling tank space 17 distribute and collect refrigerant to the subcooling sections 122 of the plurality of refrigerant passages 12. The cooling water first tank space 18 and the cooling water second tank space 19 distribute and collect the cooling water to the plurality of cooling water passages 13.

  Specifically, in the present embodiment, the first tank space for condensation 14 distributes the refrigerant to the condensing portions 121 of the plurality of refrigerant passages 12. The condensation second tank space 15 collects refrigerant with respect to the condensing portions 121 of the plurality of refrigerant passages 12.

  The subcooling first tank space 16 distributes the refrigerant to the subcooling portions 122 of the plurality of refrigerant passages 12. The supercooling second tank space 17 collects refrigerant with respect to the supercooling portions 122 of the plurality of refrigerant passages 12.

  The first tank space 18 for cooling water distributes the cooling water to the plurality of cooling water passages 13. The second tank space 19 for cooling water collects cooling water with respect to the plurality of cooling water passages 13.

  Condensing first tank space 14, Condensing second tank space 15, Supercooling first tank space 16, Supercooling second tank space 17, Cooling water first tank space 18, and Cooling water second tank space Reference numeral 19 denotes a communication hole formed in the first plate-like member 11.

  Hereinafter, in the refrigerant passage 12, the arrangement direction of the condensing unit 121 and the supercooling unit 122 is referred to as an arrangement direction. In the refrigerant passage 12, a direction perpendicular to both the arrangement direction and the plate stacking direction is referred to as a width direction. In the present embodiment, the arrangement direction coincides with the gravity direction and the longitudinal direction of the first plate-like member 11. In the present embodiment, the width direction coincides with the horizontal direction.

  As shown in FIG. 4, the first tank space 18 for cooling water is located on the supercooling portion 122 side (lower side in the gravity direction) in the arrangement direction with respect to the cooling water passage 13 of the heat exchange portion 1 and in the width direction. It is arranged on one side (left side in the example of FIG. 4). The second tank space 19 for cooling water is located on the condensing unit 121 side in the arrangement direction (upper side in the gravity direction) and the other side in the width direction (in the example of FIG. 4) with respect to the cooling water passage 13 of the heat exchange unit 1. (Right side)

  Therefore, in the cooling water passage 13, the cooling water flows from the supercooling part 122 side in the arrangement direction toward the condensing part 121 side and from one side in the width direction to the other side, as indicated by solid arrows in FIG. 4. It flows toward. In the present embodiment, in the cooling water passage 13, the cooling water flows from the lower side in the gravity direction toward the upper side and from the left side to the right side in FIG.

  As shown in FIG. 5, the first tank space 14 for condensing has a condensing part 121 of the heat exchanging part 1 on the condensing part 121 side in the arrangement direction (upward side in the gravity direction) and one side in the width direction ( It is arranged on the left side in the example of FIG. The second tank space 15 for condensation is located on the supercooling part 122 side in the arrangement direction (lower side in the gravity direction) and the other side in the width direction (right in the example of FIG. 5) with respect to the condensation part 121 of the heat exchange part 1. On the other side).

  Moreover, the first tank space 16 for supercooling has a condensing part 121 side (upper side in the gravity direction) in the arrangement direction and one side in the width direction (in FIG. 5) with respect to the supercooling part 122 of the heat exchange part 1. In the example, it is arranged on the left side). The second tank space 17 for supercooling is located on the side of the supercooling part 122 in the arrangement direction (lower side in the direction of gravity) and the other side in the width direction with respect to the supercooling part 122 of the heat exchange part 1 (example in FIG. 5). In the right side).

  For this reason, in each of the condensing unit 121 and the supercooling unit 122, the refrigerant flows from the condensing unit 121 side in the arrangement direction toward the supercooling unit 122 side in the width direction as shown by the broken line arrows in FIG. Flows from one side to the other. In the present embodiment, in each of the condensing unit 121 and the supercooling unit 122, the refrigerant flows from the upper side in the gravity direction to the lower side and from the left side to the right side in FIG.

  Therefore, in the present embodiment, when the heat exchange unit 1 is viewed from the plate stacking direction, the refrigerant flow flowing through the refrigerant passage 12 and the cooling water flow flowing through the cooling water passage 13 intersect each other. That is, when the heat exchange unit 1 is viewed from the plate stacking direction, the refrigerant flow flowing through the condensing unit 121 and the cooling water flow flowing through the cooling water passage 13 intersect each other, and the refrigerant flow flowing through the supercooling unit 122 The cooling water flow flowing through the cooling water passage 13 intersects.

  By the way, in the condensing part 121, as shown in FIG. 6, the condensing side inner part which divides | segments the flow path in the condensing part 121 into the several condensing side fine flow path 121a, and accelerates | stimulates heat exchange with a refrigerant | coolant and cooling water. Fins 51 are provided. The condensation-side inner fins 51 are offset fins in which the wall portions 51a that divide the condensation-side narrow channel 121a are arranged in a staggered manner along the refrigerant flow direction (that is, the arrangement direction).

  As shown in FIG. 7, the supercooling unit 122 divides the flow path in the supercooling unit 122 into a plurality of subcooling side narrow flow channels 122 a to promote heat exchange between the refrigerant and the cooling water. Side inner fins 52 are provided. The supercooling side inner fin 52 is a straight fin in which a wall portion 52a dividing the supercooling side narrow channel 122a extends linearly in the refrigerant flow direction (that is, the arrangement direction).

  As shown in FIG. 3, cooling water side inner fins 53 are also provided in the cooling water passage 13. In the present embodiment, an offset fin is employed as the cooling water side inner fin 53.

  The condensing side inner fin 51, the supercooling side inner fin 52, and the cooling water side inner fin 53 are respectively joined to both adjacent first plate members 11 by brazing.

  Returning to FIG. 1 and FIG. 2, among the many first plate-like members 11 constituting the heat exchanging unit 1, the outermost plate-like member 11 </ b> A located closest to one end in the plate stacking direction includes the first joint 31, A two joint 32, a first cooling water pipe 33 and a second cooling water pipe 34 are attached.

  The 1st joint 31 is a member for joining refrigerant | coolant piping, and forms the refrigerant | coolant inlet_port | entrance of a heat exchanger. The 2nd joint 32 is a member for joining refrigerant | coolant piping, and forms the refrigerant | coolant exit of a heat exchanger. The first cooling water pipe 33 forms a cooling water inlet of the heat exchanger. The second cooling water pipe 34 forms a cooling water outlet of the heat exchanger.

  As shown in FIG. 4, in this embodiment, the 1st joint 31 is arrange | positioned in the site | part corresponding to the 1st tank space 14 for condensation in 11 A of endmost plate members. The 2nd joint 32 is arrange | positioned in the site | part corresponding to the 2nd tank space 17 for supercooling in 11 A of endmost plate-shaped members. The 1st cooling water pipe 33 is arrange | positioned in the site | part corresponding to the 1st cooling water tank space 18 in 11 A of endmost plate-shaped members. The 2nd cooling water pipe 34 is arrange | positioned in the site | part corresponding to the 2nd tank space 19 for cooling water in 11 A of endmost plate members.

Here, returning to FIG. 1 and FIG. 2, the first plate-like member 11 located closest to the other end side in the plate stacking direction among the multiple first plate-like members 11 constituting the heat exchanging unit 1 is changed to the first plate-like member 11. It is called a ceiling board 11B. The first ceiling plate 11 </ b> B is thicker than the other first plate-like members 11 and has a longer length in the plate stacking direction of the overhanging portion 111.

  The gas-liquid separation unit 2 is connected to the surface of the first ceiling plate 11B opposite to the heat exchange unit 1. The gas-liquid separator 2 is integrally formed by stacking and joining a plurality of second plate-like members 21 to each other. The stacking direction of the second plate member 21 is parallel to the stacking direction (plate stacking direction) of the first plate member 11. In addition, the broken line in FIG. 2 has shown the liquid level of the liquid phase refrigerant | coolant stored in the gas-liquid separation part 2. FIG.

  The second plate member 21 is equal in length to the first plate member 11 in the arrangement direction and in the width direction. The second plate-like member 21 is longer than the first plate-like member 11 in the plate stacking direction of the overhanging portion 211.

  A plurality of gas-liquid separation passages 22 through which the refrigerant flowing from the condensing unit 121 of the heat exchange unit 1 flows are formed between the plurality of second plate-like members 21. The second plate-shaped member 21 is provided with a through hole (not shown) so that adjacent gas-liquid separation passages 22 communicate with each other.

  In the present embodiment, the length of the gas-liquid separation passage 22 in the plate stacking direction is longer than both the length of the refrigerant passage 12 in the plate stacking direction and the length of the cooling water passage 13 in the plate stacking direction. Moreover, the inner fin is not arrange | positioned in the gas-liquid separation channel | path 22 from the surface of internal capacity | capacitance or a weight.

  Here, among the multiple second plate-like members 21 constituting the gas-liquid separation unit 2, the second plate-like member 21 located closest to the other end side in the plate stacking direction is referred to as a second ceiling plate 21B. The second ceiling plate 21 </ b> B is thicker than the other second plate-like members 21.

  Ribs 212 are provided on the second ceiling plate 21B. The rib 212 is formed by denting a part of the second ceiling plate 21B to one end side (the heat exchange unit 1 side) in the plate stacking direction. A reinforcing plate 212A is joined to the second ceiling plate 21B of the present embodiment so as to cover the rib 212.

  The rib 212 can improve the strength of the gas-liquid separator 2. The strength of the gas-liquid separator 2 may be improved by adding a reinforcing plate or the like inside the gas-liquid separator 2. Further, the strength of the gas-liquid separation unit 2 may be further improved by joining a part of the multiple second plate-like members 21 constituting the gas-liquid separation unit 2 by surface matching or the like.

  As shown in FIG. 2, the 1st through-hole 113 is provided in the site | part corresponding to the 2nd tank space 15 for condensation in the 1st ceiling board 11B. The condensing second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113.

  In other words, the first through-hole 113 of the present embodiment has a heat exchange section side outflow section for flowing out the refrigerant condensed in the condensing section 121 to the outside, and the refrigerant condensed in the condensing section 121 in the gas-liquid separation section 2. It fulfills the function of the inflow part on the gas-liquid separation part side. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected by the first through hole 113.

  A second through hole 114 is provided in a portion of the first ceiling plate 11B corresponding to the first supercooling tank space 16. The first tank space 16 for supercooling communicates with the gas-liquid separation passage 22 through the second through hole 114.

  That is, the second through-hole 114 of the present embodiment has a gas-liquid separation part side outflow part that causes the liquid-phase refrigerant separated in the gas-liquid separation part 2 to flow out to the outside, and the gas-liquid separation part 2 has gas. It fulfills the function of the heat exchange section side inflow section that causes the liquid phase separated liquid to flow into the supercooling section 122. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part inflow part and the gas-liquid separation part side outflow part directly connected by the second through-hole 114.

  As described above, in the present embodiment, the condensing part 121 and the supercooling part 122 are provided side by side in the arrangement direction in the refrigerant passage 12 formed between the first plate-like members 11. Thereby, both the condensing part 121 and the supercooling part 122 can be arrange | positioned in the one refrigerant path 12. FIG. For this reason, since it is not necessary to newly add a housing-like heat exchanger functioning as the supercooling unit 122, it is possible to reduce the size of the physique and reduce the dead space on mounting.

  In the present embodiment, in the refrigerant passage 12, the condensing part 121 and the supercooling part 122 are partitioned by the heat insulating part 123. According to this, it is possible to suppress the occurrence of heat damage in which the low-temperature liquid-phase refrigerant flowing through the supercooling unit 122 is heated by the heat of the high-temperature refrigerant flowing through the condensing unit 121.

  In the present embodiment, the heat insulating portion 123 is configured as a part of the cooling water passage 13. Since the heat capacity of the cooling water is larger than that of the refrigerant, the heat insulation part 123 through which the cooling water circulates further suppresses the thermal interference between the refrigerant that circulates in the condensing part 121 and the refrigerant that circulates in the supercooling part 122. Heat exchange with water can be promoted.

  In addition, since the cooling water flows into the protruding portion 112 of the heat insulating portion 123 from the gap between the wall portions of the cooling water side inner fin 53 (offset fin), the cooling water flows inside the protruding portion 112. The cooling water has a large heat capacity with respect to the refrigerant, and the cooling water flowing through the protrusion 112 is heat-exchanged with both the refrigerant flowing through the supercooling unit 122 and the refrigerant flowing through the condensing unit 121. For this reason, heat exchange between the refrigerant and the cooling water can be promoted while suppressing thermal interference between the refrigerants.

  In the present embodiment, the heat insulating portion 123 is constituted by the protruding portion 112 formed by bending a part of the first plate-like member 11. For this reason, the heat insulation part 123 can be set without deteriorating the assembly workability of the heat exchange part 1. Furthermore, the increase in the number of parts for setting the heat insulation part 123 can also be prevented.

  In the present embodiment, in the cooling water passage 13, as shown by the arrows in FIG. 4, the cooling water is directed from the supercooling part 122 side in the arrangement direction toward the condensing part 121 side and on one side in the width direction. From the other side. Further, in each of the condensing unit 121 and the supercooling unit 122, as shown by a broken line arrow in FIG. 5, the refrigerant is directed from the condensing unit 121 side in the arrangement direction toward the supercooling unit 122 side and on one side in the width direction. From the other side. That is, in the present embodiment, when the heat exchange unit 1 is viewed from the plate stacking direction, the refrigerant flow flowing through the refrigerant passage 12 and the cooling water flow flowing through the cooling water passage 13 are crossed. According to this, in each of the condensing part 121 and the supercooling part 122, the heat exchange efficiency of a refrigerant | coolant and cooling water can be improved.

  Here, the surface of the first plate-like member 11 on the refrigerant passage 12 side in the present embodiment is shown in FIG. In FIG. 8, the condensing side inner fin 51 or the supercooling side inner fin 52 is arranged in a region indicated by point hatching.

As shown in FIG. 8, in the refrigerant passage 12, the vicinity of the portion forming the tank spaces 14 to 19 (the region surrounded by the broken line in FIG. 8) is a dead water area. The dead water area is an area where the inner fins 51 and 52 cannot be physically disposed, or a space for facilitating the flow of the refrigerant into the inner fins 51 and 52.

  In the present embodiment, the cooling water flow is introduced from the supercooling unit 122 side and flows to the condensing unit 121 side. For this reason, the inner fins 51 and 52 can also be arrange | positioned also to the area | region enclosed with the dashed-dotted line of FIG. . Therefore, in this embodiment, since the heat radiation area between the refrigerant and the cooling water can be increased and the heat exchange performance can be improved with respect to the comparative configuration, the heat exchanger can be further downsized.

  In the present embodiment, straight fins are used as the supercooling side inner fins 52. According to this, in the supercooling part 122, the pressure loss of a refrigerant | coolant can be reduced. In addition, although a straight fin is poor in refrigerant | coolant diffusibility with respect to an offset fin, since a liquid phase refrigerant | coolant flows through the supercooling part 122, the necessity for diffusing a refrigerant | coolant is low. Therefore, by adopting straight fins as the supercooling side inner fins 52, the supercooling section 122 can more efficiently supercool the refrigerant.

  Moreover, in this embodiment, the heat exchange part 1 and the gas-liquid separation part 2 are directly connected by the 1st through-hole 113 and the 2nd through-hole 114 which were formed in the 1st ceiling board 11B. According to this, since it is not necessary to provide piping for connecting the heat exchange unit 1 and the gas-liquid separation unit 2, it is possible to reduce the mounting space for the heat exchanger and the number of components.

  Moreover, in this embodiment, the heat exchanger is comprised so that the refrigerant | coolant flow may be U-turned in the gas-liquid separation part 2. FIG. Since the gas-liquid separator 2 corresponds to an enlarged portion of the refrigerant flow path, the bending loss of the refrigerant flow path can be ignored. For this reason, it is possible to make the refrigerant flow U-turn while suppressing the occurrence of bending loss or the like of the refrigerant.

  In the present embodiment, the gas-liquid separation space in the gas-liquid separation unit 2 is constituted by a large number of second plate members 21. Thereby, since a refrigerant | coolant liquid level is divided | segmented within the gas-liquid separation part 2, foaming of a refrigerant | coolant liquid level can be suppressed.

  Moreover, in this embodiment, since the condensing side inner fin 51 is arrange | positioned at the condensation part 121, it can suppress that a refrigerant | coolant separates into the gas-liquid separation part 2, and separates into two phases (a gaseous phase and a liquid phase). . In addition, since the second plate-like member 21 is cooled by the liquid phase refrigerant in the gas-liquid separation unit 2, even when bubbles (gas phase refrigerant) are slightly mixed when flowing into the gas-liquid separation unit 2, The bubbles are cooled and condensed by exchanging heat with the second plate member 21.

  Therefore, in this embodiment, the gas-liquid separation property of the gas-liquid separation unit 2 can be improved.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment in the configuration of the heat insulating portion 123. FIG. 9 is a drawing corresponding to FIG. 3 of the first embodiment.

  As shown in FIG. 9, the heat insulation part 123 of this embodiment is an air layer in which air exists. More specifically, the third plate member 41 is joined to one first plate member 11 a of the two first plate members 11 that define the coolant passage 12. The 3rd plate-shaped member 41 is joined to the surface by the side of the refrigerant path 12 of one 1st plate-shaped member 11a.

  The third plate-like member 41 is provided with a protruding portion 412 in which a part thereof is protruded toward the other first plate-like member 11b. The protrusion 412 is joined to the other first plate member 11b. The protrusion 412 can partition the refrigerant passage 12 into a condensing part 121 and a supercooling part 122.

  As described above, in the present embodiment, since the heat insulating portion 123 is formed of an air layer, even if the flow of the cooling water stops, the heat interference between the refrigerant between the condensing unit 121 and the supercooling unit 122. Can be reduced. Moreover, in this embodiment, the heat insulation part 123 is comprised by adding the 3rd plate-shaped member 41. FIG. For this reason, the heat insulation part 123 can be set without deteriorating the assembly workability of the heat exchange part 1.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. The third embodiment is different from the first embodiment in the configurations of the heat exchange unit 1 and the gas-liquid separation unit 2. In addition, the broken line in FIG. 11 has shown the liquid level of the liquid phase refrigerant | coolant stored in the gas-liquid separation part 2. FIG.

  As shown in FIG. 10, the supercooling first tank space 16 of the present embodiment collects refrigerant with respect to the supercooling portions 122 of the plurality of refrigerant passages 12. The subcooling second tank space 17 distributes the refrigerant to the subcooling portions 122 of the plurality of refrigerant passages 12. The second joint 32 communicates with the first tank space 16 for supercooling.

  As shown in FIGS. 10 and 11, in the present embodiment, the overhanging portion 211 of the second plate-like member 21 overhangs (protrudes) toward the other end side in the plate stacking direction. In the embodiment, the projecting direction (projecting direction) of the projecting portion 211 of the second plate member 21 is opposite to the projecting direction (projecting direction) of the projecting portion 111 of the first plate member 11. .

  Of the many second plate-like members 21 constituting the gas-liquid separation unit 2, the second plate-like member 21 located closest to one end in the plate stacking direction is referred to as a third ceiling plate 21A. The third ceiling plate 21A is thicker than the other second plate-like member 21. The first ceiling plate 11B of the heat exchanging unit 1 is joined to the surface of the third ceiling plate 21A opposite to the gas-liquid separation unit 2.

  As shown in FIG. 11, a third through hole 213 is provided in a portion of the third ceiling plate 21A corresponding to the first through hole 113 of the first ceiling plate 11B. The outer peripheral edge portion of the third through hole 213 is directly joined to the outer peripheral edge portion of the first through hole 113. The condensation second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113 and the third through hole 213.

  Here, the 1st through-hole 113 of this embodiment has fulfill | performed the function of the heat exchange part side outflow part which flows out the refrigerant | coolant condensed in the condensation part 121 outside. The third through-hole 213 of the present embodiment functions as a gas-liquid separation unit side inflow portion that causes the refrigerant condensed in the condensing unit 121 to flow into the gas-liquid separation unit 2. Further, as described above, the outer peripheral edge portion of the third through hole 213 is directly joined to the outer peripheral edge portion of the first through hole 113. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected without interposing other members.

  A fourth through hole 214 is provided in a portion of the third ceiling plate 21A corresponding to the second through hole 114 of the first ceiling plate 11B. The outer peripheral edge portion of the fourth through hole 214 is directly joined to the outer peripheral edge portion of the second through hole 114. The supercooling second tank space 17 communicates with the gas-liquid separation passage 22 via the second through hole 114 and the fourth through hole 214.

  Here, the 4th through-hole 214 of this embodiment has fulfill | performed the function of the gas-liquid separation part side outflow part which flows out the liquid phase refrigerant | coolant isolate | separated in the gas-liquid separation part 2 outside. The second through-hole 114 of the present embodiment functions as a heat exchange section side inflow section that allows the liquid-phase refrigerant separated from the gas-liquid separation section 2 to flow into the supercooling section 122. Further, as described above, the outer peripheral edge portion of the fourth through hole 214 is directly joined to the outer peripheral edge portion of the second through hole 114. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side inflow part and the gas-liquid separation part side outflow part directly connected without interposing other members.

  As shown in FIG. 12, the third ceiling plate 21A is provided with a recess 215. The recess 215 is formed by denting a part of the third ceiling plate 21A toward the other side in the plate stacking direction. By providing the recess 215 in the third ceiling plate 21A, a gap can be formed between the first ceiling plate 11B and the third ceiling plate 21A, that is, between the heat exchange unit 1 and the gas-liquid separation unit 2. it can.

  As shown in FIG. 13, in the present embodiment, the multiple first plate-like members 11 constituting the heat exchanging unit 1 are substantially cylindrical protrusions protruding toward one end side or the other end side in the plate stacking direction. The projecting portions 115 having the portions 115 are provided at portions corresponding to the four corners of the first plate-like member 11, the second tank space 15 for condensation, and the first tank space 16 for supercooling. It has been.

  By this projecting portion 115, the first tank space for condensation 14, the second tank space for condensation 15, the first tank space for supercooling 16, the second tank space for supercooling 17, the first tank space for cooling water 18, and the cooling Water second tank spaces 19 are respectively formed.

  In other words, the protruding portion 115 formed on one first plate-like member 11a and the protruding portion 115 formed on the other first plate-like member 11b are fitted together, and the first tank space for condensation 14, the condensation A second tank space 15, a supercooling first tank space 16, a supercooling second tank space 17, a cooling water first tank space 18 and a cooling water second tank space 19 are formed.

  Among the multiple first plate-like members 11 constituting the heat exchange unit 1, one first plate-like member 11 located on the one side in the plate lamination direction (the heat exchange unit 1 side) from the central portion in the plate lamination direction is In addition, it has a closing portion 116 that closes the protruding portion 115 that constitutes the first tank space 14 for condensation. Thereby, the 1st tank space 14 for condensation is divided into two spaces in the board lamination direction.

  In addition, among the multiple first plate-like members 11 constituting the heat exchanging unit 1, one first plate-like member located on the other side in the plate stacking direction (gas-liquid separation unit 2 side) than the central portion in the plate stacking direction. The member 11 has a closing portion 116 that closes the protruding portion 115 constituting the second tank space 15 for condensation. Thereby, the 2nd tank space 15 for condensation is divided into two spaces in the board lamination direction.

  The closing part 116 is formed integrally with the protruding part 115, that is, the first plate-like member 11.

  Therefore, as shown by the broken line arrows in FIGS. 10 and 14, the refrigerant flowing from the first joint 31 passes through the condensing part 121A on one end side in the plate stacking direction from the condensing first tank space 14 side to the condensing second tank. It flows toward the space 15 side and flows into the second tank space 15 for condensation. The refrigerant that has flowed into the second condensing tank space 15 flows through the condensing part 121B on the center side in the plate stacking direction from the second condensing second tank space 15 side toward the condensing first tank space 14 side, and the condensing second tank space 15 is reached. It flows into one tank space 14. The refrigerant flowing into the condensation first tank space 14 flows through the condensation section 121C on the other end side in the plate stacking direction from the condensation first tank space 14 side toward the condensation second tank space 15 side. The gas flows from the through hole 113 and the third through hole 213 into the gas-liquid separator 2. That is, the heat exchange unit 1 is configured such that the refrigerant flow makes a U-turn twice in the condensing unit 121.

The refrigerant that has flowed into the gas-liquid separation unit 2 is gas-liquid separated, and the liquid-phase refrigerant flows into the second tank space 17 for supercooling through the fourth through hole 214 and the second through hole 114. The liquid-phase refrigerant that has flowed into the second subcooling tank space 17 flows through the subcooling section 122 from the second subcooling tank space 17 side toward the first subcooling tank space 16 side, and is thus supplied to the second joint. It flows out of 32 to the outside.

  As described above, in the present embodiment, the condensing unit 121 is configured such that the refrigerant flow makes a U-turn twice. Thereby, since the flow velocity of the refrigerant | coolant which distribute | circulates the condensation part 121 becomes quick, the heat exchange efficiency in the condensation part 121 can be improved.

  Further, by configuring the condensing unit 121 so that the refrigerant flow makes a U-turn twice, the high-temperature refrigerant flowing in from the discharge side of the compressor is located in the condensing unit 121 adjacent to the gas-liquid separation unit 2. There is no direct inflow. Thereby, since the refrigerant | coolant which became low temperature after making two U-turns distribute | circulates in the site | part adjacent to the gas-liquid separation part 2 in the condensation part 121, the liquid in the gas-liquid separation part 2 with the heat | fever which a high temperature refrigerant | coolant has. Heating of the phase refrigerant can be suppressed.

  Moreover, in this embodiment, the recessed part 215 is provided in 21 A of 3rd ceiling boards, and the clearance gap is formed between the heat exchange part 1 and the gas-liquid separation part 2. FIG. Thereby, it can suppress more reliably that the liquid phase refrigerant | coolant in the gas-liquid separation part 2 is heated with the heat which a high temperature refrigerant | coolant has.

  In the present embodiment, as shown in FIGS. 10 and 14, the supercooling second tank space 17 is arranged at the lowest part in the gravity direction. According to this, a liquid phase refrigerant with a heavy specific gravity can be flowed more reliably from the gas-liquid separation part 2.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. 15 and 16. The fourth embodiment differs from the first embodiment in the configuration of the gas-liquid separator 2. In addition, the broken line in FIG. 16 has shown the liquid level of the liquid phase refrigerant | coolant stored in the gas-liquid separation part 2. FIG.

  As shown in FIGS. 15 and 16, the gas-liquid separation unit 2 of the present embodiment is configured by a known cylindrical modulator. Specifically, the gas-liquid separation unit 2 includes a main body 200, a cap 201, a filter 202, a desiccant 203, and the like.

  The main body 200 is formed in a cylindrical shape, separates the gas / liquid of the refrigerant flowing into the inside, and stores excess refrigerant in the refrigeration cycle. Specifically, the main body 200 is formed of a bottomed cylindrical tank that is open at one end in the longitudinal direction. The main body 200 is joined to the heat exchange unit 1 such that the opening side is on the lower side in the direction of gravity.

  The cap 201 is a substantially cylindrical lid member that closes the opening on the one end side of the main body 200. The cap 201 can be attached to and detached from the main body 200. The cap 201 is made of a compressor lubricating oil that circulates in the refrigeration cycle together with the refrigerant and a resin excellent in deterioration resistance and heat resistance with respect to the refrigerant, such as nylon and polyester.

  As shown in FIG. 16, the filter 202 is a member that forms a fine mesh on the whole and captures foreign matters such as dust in the refrigerant that passes through the filter 202, and is formed of the same resin material as the cap 201. Yes.

The desiccant 203 is one in which granular zeolite for water absorption is stored inside the bag body, and absorbs moisture in the refrigerant. This is to prevent each functional component constituting the refrigeration cycle from being corroded by moisture in the refrigerant, or freezing in the pores of the expansion valve to stagnate the refrigerant flow. The desiccant 203 is accommodated in a space above the filter 202 in the main body 200.

  A portion of the first ceiling plate 11B corresponding to the second tank space 15 for condensation is provided with a substantially cylindrical first protruding portion 117 that protrudes toward the gas-liquid separation portion 2 side (the other end side in the plate stacking direction). It has been. A first through hole 217 is formed at a portion of the main body 200 of the gas-liquid separator 2 that faces the first protrusion 117.

  The first through hole 217 is formed in a shape corresponding to the first protrusion 117. A first protrusion 117 is inserted into the first through hole 217. The outer peripheral surface of the first protrusion 117 is directly joined to the inner peripheral surface of the first through hole 217. Thereby, the second tank space 15 for condensation communicates with the internal space of the main body 200 of the gas-liquid separation unit 2 via the first protrusion 117 and the first through hole 217.

  Here, the 1st protrusion part 117 of this embodiment has fulfill | performed the function of the heat exchange part side outflow part which flows out the refrigerant | coolant condensed in the condensation part 121 to the exterior. The first through-hole 217 according to the present embodiment functions as a gas-liquid separation unit side inflow portion that allows the refrigerant condensed in the condensing unit 121 to flow into the gas-liquid separation unit 2. Further, as described above, the outer peripheral surface of the first protruding portion 117 is directly joined to the inner peripheral surface of the first through hole 217. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected without interposing other members.

  Further, a portion of the first ceiling plate 11B corresponding to the supercooling first tank space 16 has a substantially cylindrical second protruding portion protruding toward the gas-liquid separation portion 2 side (the other end side in the plate stacking direction). 118 is provided. A second through hole 218 is formed in a portion of the main body 200 of the gas-liquid separator 2 that faces the second protrusion 118.

  The second through hole 218 is formed in a shape corresponding to the second protrusion 118. A second protrusion 118 is inserted into the second through hole 218. The outer peripheral surface of the second protrusion 118 is directly joined to the inner peripheral surface of the second through hole 218. Thereby, the first tank space 16 for supercooling communicates with the internal space of the main body 200 of the gas-liquid separator 2 via the second protrusion 118 and the second through hole 218.

  Here, the 2nd through-hole 218 of this embodiment has fulfill | performed the function of the gas-liquid separation part side outflow part which flows out the liquid phase refrigerant | coolant isolate | separated in the gas-liquid separation part 2 outside. The second projecting portion 118 of the present embodiment functions as a heat exchange portion side inflow portion that causes the liquid-phase refrigerant separated in the gas-liquid separation portion 2 to flow into the subcooling portion 122. Further, as described above, the outer peripheral surface of the second protrusion 118 is directly joined to the inner peripheral surface of the second through hole 218. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side inflow part and the gas-liquid separation part side outflow part directly connected without interposing other members.

  In this embodiment, the 1st protrusion part 117 and the 2nd protrusion part 118 are integrally formed with the 1st ceiling board 11B. Specifically, the 1st protrusion part 117 and the 2nd protrusion part 118 are formed by giving a burring process to the 1st ceiling board 11B.

  In the present embodiment, similarly to the first embodiment, the condensing part 121 and the supercooling part 122 are provided side by side in the arrangement direction in the refrigerant passage 12 formed between the first plate-like members 11. . For this reason, an existing modulator (mass product) can be employed as the gas-liquid separation unit 2 without providing a refrigerant pipe for connecting the gas-liquid separation unit 2 and the heat exchange unit 1.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIGS. The fifth embodiment is different from the first embodiment in the configuration of the portion where the heat exchange unit 1 and the gas-liquid separation unit 2 are joined.

  As shown in FIG. 17, in the present embodiment, the arrangement direction of the condensing unit 121 and the supercooling unit 122 coincides with the horizontal direction. In the present embodiment, the width direction coincides with the gravity direction.

  As shown in FIGS. 18 and 19, the third ceiling plate 21 </ b> A located closest to the heat exchange unit 1 among the many second plate-like members 21 constituting the gas-liquid separation unit 2 is the other second plate. Compared with the plate-like member 21, the plate thickness is thicker.

  A plate-like coupling member 25 is disposed between the first ceiling plate 11B of the heat exchange unit 1 and the third ceiling plate 21A of the gas-liquid separation unit 2. The coupling member 25 is joined to the third ceiling plate 21A by brazing.

  The coupling member 25 is provided with a plurality of protruding portions 251 that are partially protruded toward the first ceiling plate 11B side. The protrusion 251 is joined to the first ceiling plate 11B by brazing. By providing the coupling member 25 with a plurality of protrusions 251, a gap is formed between the first ceiling plate 11 </ b> B and the third ceiling plate 21 </ b> A, that is, between the heat exchange unit 1 and the gas-liquid separation unit 2. be able to. This gap is an air layer in which air is present, and serves as a heat insulating part between the heat exchange part 1 and the gas-liquid separation part 2.

  One protrusion 251 among the plurality of protrusions 251 is disposed at a portion corresponding to the first through hole 113. As shown in FIG. 20, a first communication hole 252 communicating with the first through hole 113 is formed in the protrusion 251 corresponding to the first through hole 113. The condensation second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113 and the first communication hole 252.

  The protruding portion 251 functions as a partition that partitions the refrigerant flow path between the second tank space 15 for condensation and the gas-liquid separation passage 22 and the heat insulating air layer between the heat exchange portion 1 and the gas-liquid separation portion 2. Plays.

  The other protrusion 251 among the plurality of protrusions 251 is disposed at a portion corresponding to the second through hole 114. The protrusion 251 corresponding to the second through hole 114 has the same structure as the protrusion 251 corresponding to the first through hole 113 shown in FIG. Therefore, the reference numerals corresponding to the structure in the vicinity of the second through hole 114 are given in parentheses in FIG. 20, and the illustration of the structure in the vicinity of the second through hole 114 is omitted.

  As indicated by the reference numerals in parentheses in FIG. 20, the projecting portion 251 corresponding to the first through hole 113 is formed with a second communication hole 253 communicating with the second through hole 114. The supercooling first tank space 16 communicates with the gas-liquid separation passage 22 via the second through hole 114 and the second communication hole 253.

  The projecting portion 251 is a partition wall that partitions the refrigerant flow path between the first tank space 16 for supercooling and the gas-liquid separation passage 22 and the adiabatic air layer between the heat exchange portion 1 and the gas-liquid separation portion 2. Playing a role.

  Among the multiple second plate-like members 21 constituting the gas-liquid separation unit 2, the second ceiling plate 21B located closest to the other end side in the plate stacking direction and the second plate counted from the other end side in the plate stacking direction The fourth ceiling panel 21 </ b> C is thicker than the other second plate-shaped members 21. Thereby, the gas-liquid separation part 2 is reinforced.

  Inner fins 26 are joined to the surface of the second ceiling plate 21B and the fourth ceiling plate 21C on one end side in the plate stacking direction by brazing. The inner fin 26 is a reinforcing member that reinforces the gas-liquid separator 2.

  A collar 27 is disposed between the second plate members 21 other than the second ceiling plate 21B and the fourth ceiling plate 21C among the multiple second plate members 21 constituting the gas-liquid separation unit 2. ing. The collar 27 is a reinforcing member that reinforces the gas-liquid separator 2. The collar 27 is joined to both of the second plate-like members 21 adjacent to each other by brazing.

  The collar 27 has a cylindrical portion, and is disposed on the periphery of the through hole 219 provided in the second plate member 21. The through hole 219 is a communication hole that allows adjacent gas-liquid separation passages 22 to communicate with each other. The cylindrical portion of the collar 27 is provided with at least one notch. Thereby, the collar 27 does not disturb the communication between the adjacent gas-liquid separation passages 22.

  In this embodiment, the plate-shaped coupling member 25 interposed between the heat exchange part 1 and the gas-liquid separation part 2 is provided. The coupling member 25 couples the heat exchange unit 1 and the gas-liquid separation unit 2, and forms a gap where air exists between the heat exchange unit 1 and the gas-liquid separation unit 2. Thereby, the heat insulation between the heat exchange part 1 and the gas-liquid separation part 2 can be improved.

  In this embodiment, the coupling member 25 has a protruding portion 251 that protrudes from one side to the other side of the heat exchange unit 1 and the gas-liquid separation unit 2 to form a gap. Thereby, a clearance gap can be formed between the heat exchange part 1 and the gas-liquid separation part 2 by simple structure.

  In the present embodiment, the projecting portion 251 is formed with communication holes 252 and 253 that connect the refrigerant passage 12 and the internal space of the gas-liquid separation portion 2. Thereby, with a simple structure, a clearance gap is formed between the heat exchange part 1 and the gas-liquid separation part 2, and the refrigerant path 12 and the internal space of the gas-liquid separation part 2 can be communicated.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and within the scope not departing from the spirit of the present invention,
For example, various modifications are possible as follows.

  (1) Although the example which employ | adopted the offset fin as the cooling water side inner fin 53 was demonstrated in the said embodiment, you may employ | adopt not only this but a straight fin.

  (2) In the above embodiment, an example in which straight fins are employed as the supercooling side inner fins 52 has been described. However, the supercooling side inner fins 52 are not limited to this. For example, as the supercooling side inner fin 52, an offset fin in which wall portions 52a dividing the supercooling side narrow channel 122a are arranged in a staggered manner along the refrigerant flow direction may be adopted. According to this, it is possible to share the condensing side inner fin 51 and reduce the dead water region due to the refrigerant diffusibility of the inner fin.

  (3) In the above embodiment, an example in which the heat exchanger is arranged so that the arrangement direction coincides with the direction of gravity has been described, but the arrangement of the heat exchanger is not limited to this.

  For example, as shown in FIG. 22, if the second tank space 17 for supercooling is arranged at the lowermost part in the direction of gravity so that the liquid-phase refrigerant flows more reliably from the gas-liquid separator 2, the arrangement direction and You may arrange | position a heat exchanger so that a board lamination direction may correspond with a horizontal direction. In FIG. 22, a solid line arrow indicates a cooling water flow, and a broken line arrow indicates a refrigerant flow.

  (4) In the heat exchanger in which the gas-liquid separator 2 and the heat exchanger 1 are integrated as in the above embodiment, a desiccant may be provided inside the gas-liquid separator 2. For example, by setting a hole for inserting a desiccant on the outside of the gas-liquid separator 2 (the other end in the stacking direction, for example, the second ceiling plate 21B), and then applying a lid with a plug after the desiccant is inserted, the gas-liquid separation is performed. A desiccant may be provided inside the portion 2.

  (5) In the sixth embodiment, the coupling member 25 is provided with the protrusion 251 so that a gap is formed between the heat exchange unit 1 and the gas-liquid separation unit 2, but the coupling member 25 is notched. A gap may be formed between the heat exchange unit 1 and the gas-liquid separation unit 2 by providing a hole or a hole.

  (6) In the above embodiment, in the refrigerant passage 12, the heat insulating part 123 that insulates the condensing part 121 and the supercooling part 122 is disposed between the condensing part 121 and the supercooling part 122.

  At least one first plate-like member 11 of the two first plate-like members 11 forming the cooling water passage 13 is directed toward the other first plate-like member 11 facing one first plate-like member 11. The protrusion part which protrudes in this way is formed, and the condensation part 121 and the supercooling part 122 are separated and insulated by the protrusion part.

  The protruding portion has a shape in which the cooling water passage 13 side is recessed toward the refrigerant passage 12 side, and the recessed portion only needs to communicate with the cooling water passage 13.

  (7) The means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

DESCRIPTION OF SYMBOLS 1 Heat exchange part 2 Gas-liquid separation part 11 1st plate-shaped member 12 Refrigerant passage 13 Cooling water passage (heat-medium passage)
121 Condensing part 122 Supercooling part 123 Heat insulation part

Claims (12)

A heat exchange section (1) for exchanging heat between the refrigerant of the refrigeration cycle and the heat medium;
A gas-liquid separator (2) for separating the gas-liquid of the refrigerant flowing into the interior and storing excess refrigerant in the refrigeration cycle;
The heat exchange part (1) is formed by laminating and joining a plurality of first plate-like members (11),
A plurality of refrigerant passages (12) through which the refrigerant flows and a plurality of heat medium passages (13) through which the heat medium flows are formed between the plurality of first plate-like members (11),
The plurality of refrigerant passages (12) and the plurality of heat medium passages (13) are arranged side by side in the stacking direction of the plurality of first plate-like members (11),
The longitudinal direction of the refrigerant passage (12) and the heat medium passage (13) is the same as the longitudinal direction of the first plate member (11),
The refrigerant passage (12) is gas-liquid separated by a condensing unit (121) for exchanging heat between the gas-phase refrigerant and the heat medium to condense the gas-phase refrigerant, and the gas-liquid separation unit (2). A supercooling part (122) for supercooling the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant and the heat medium is arranged in a direction orthogonal to the stacking direction and in a longitudinal direction of the refrigerant passage (12). Provided,
In the refrigerant passage (12), the refrigerant flows from the condensation section (121) side toward the supercooling section (122) side,
In the heat medium passage (13), the heat medium flows from the supercooling part (122) side toward the condensing part (121) side,
In the refrigerant passage (12), the condensing part (121) and the supercooling part (122) are partitioned by a heat insulating part (123) ,
The heat insulating part (123) is formed by a protruding part (112) formed in the first plate-like member (11) so that the heat medium passage (13) side is recessed,
The heat insulating portion (123) extends over the entire area of the refrigerant passage (12) in a direction orthogonal to the stacking direction and in a direction orthogonal to the longitudinal direction of the refrigerant passage (12),
The heat insulating part (123) constitutes a part of the heat medium passage (13),
The heat medium circulates inside the heat insulating part (123),
A heat medium side inner fin (53) that promotes heat exchange between the refrigerant and the heat medium is provided in the heat medium passage (13),
The stacked heat exchanger , wherein the heat medium flows into the heat insulating portion (123) through a gap between the wall portions of the heat medium side inner fin (53) . The heat exchanging part (1) includes a heat exchanging part side outflow part (113, 117) for letting out the refrigerant condensed in the condensing part (121) to the outside, and the gas-liquid separation part (2). A heat exchanging portion side inflow portion (114, 118) for flowing the liquid phase refrigerant separated into gas and liquid into the supercooling portion (122),
The gas-liquid separation unit (2) includes a gas-liquid separation unit side inflow unit (113, 213, 217) for allowing the refrigerant condensed in the condensation unit (121) to flow into the gas-liquid separation unit (2). And a gas-liquid separation part side outflow part (114, 214, 218) for letting out the liquid refrigerant separated in the gas-liquid separation part (2) to the outside,
The heat exchange part side outflow part (113, 117) and the gas-liquid separation part side inflow part (113, 213, 217) are directly connected,
2. The stacked heat exchange according to claim 1 , wherein the heat exchange section side inflow section (114, 118) and the gas-liquid separation section side outflow section (114, 214, 218) are directly connected. vessel. The gas-liquid separation part (2) is formed by laminating and joining a plurality of second plate members (21),
A plurality of gas-liquid separation passages (22) through which the refrigerant flows are formed between the plurality of second plate-like members (21),
The stacked heat exchanger according to claim 1 or 2 , wherein the adjacent gas-liquid separation passages (22) communicate with each other. The gas-liquid separator (2) is configured to have a cylindrical main body (200) that separates the gas-liquid of the refrigerant flowing into the interior and stores excess refrigerant in the refrigeration cycle. The laminated heat exchanger according to claim 1 or 2 , characterized in that In the refrigerant passage (12), when the width direction is a direction orthogonal to both the arrangement direction of the condensing part (121) and the supercooling part (122) and the stacking direction,
The heat medium passage (13) has the heat medium from the supercooling part (122) side in the arrangement direction toward the condensing part (12) side and from one side in the width direction to the other side. Configured to flow toward
In the condensing unit (121) and the supercooling unit (122), respectively, the refrigerant is from the condensing unit (121) side in the arrangement direction toward the supercooling unit (122) side and the width. The stacked heat exchanger according to any one of claims 1 to 4 , wherein the stacked heat exchanger is configured to flow from the one side of the direction toward the other side. In the supercooling section (122), the flow path in the supercooling section (122) is divided into a plurality of subcooling side narrow flow paths (122a) to promote heat exchange between the refrigerant and the heat medium. A supercooling side inner fin (52) is provided,
The subcooling inner fin (52) is a straight fin in which a wall (52a) dividing the subcooling narrow channel (122a) extends linearly in the refrigerant flow direction. The laminated heat exchanger according to any one of claims 1 to 5 . A plate-like coupling member (25) interposed between the heat exchange part (1) and the gas-liquid separation part (2);
The coupling member (25) couples the heat exchange part (1) and the gas-liquid separation part (2), and connects the heat exchange part (1) and the gas-liquid separation part (2). The stacked heat exchanger according to any one of claims 1 to 6 , wherein a gap in which air exists is formed therebetween. The coupling member (25) has a protrusion (251) that protrudes from one side to the other of the heat exchange part (1) and the gas-liquid separation part (2) to form the gap. The stacked heat exchanger according to claim 7 , wherein: The projecting portion (251) is formed with communication holes (252, 253) for communicating the refrigerant passage (12) and the internal space of the gas-liquid separation portion (2). The laminated heat exchanger according to 8 . A heat exchange section (1) for exchanging heat between the refrigerant of the refrigeration cycle and the heat medium;
A gas-liquid separator (2) for separating the gas-liquid of the refrigerant flowing into the interior and storing excess refrigerant in the refrigeration cycle;
The heat exchange part (1)
A plurality of first plate-like members (11) stacked;
Between the first plate-like members (11), a refrigerant passage (12) through which the refrigerant flows or a plurality of heat medium passages (13) through which the heat medium flows are formed,
A plurality of first plate-like members (11) are formed by being stacked and joined to each other,
A plurality of refrigerant passages (12) through which the refrigerant flows and a plurality of heat medium passages (13) through which the heat medium flows are formed between the first plate members (11),
The plurality of refrigerant passages (12) and the plurality of heat medium passages (13) are alternately arranged in the stacking direction of the plurality of first plate-like members (11),
The longitudinal direction of the refrigerant passage (12) and the heat medium passage (13) is the same as the longitudinal direction of the first plate member (11),
The refrigerant passage (12) is gas-liquid separated by a condensing unit (121) for exchanging heat between the gas-phase refrigerant and the heat medium to condense the gas-phase refrigerant, and the gas-liquid separation unit (2). A supercooling part (122) for supercooling the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant and the heat medium is arranged in a direction orthogonal to the stacking direction and in a longitudinal direction of the refrigerant passage (12). Provided,
In the refrigerant passage (12), the refrigerant flows from the condensation section (121) side toward the supercooling section (122) side,
In the heat medium passage (13), the heat medium flows from the supercooling part (122) side toward the condensing part (121) side,
In the refrigerant passage (12), a heat insulating part (123) that insulates the condensing part (121) and the supercooling part (122) between the condensing part (121) and the supercooling part (122). ) it has been arranged,
The heat insulating part (123) is formed by a protruding part (112) formed in the first plate-like member (11) so that the heat medium passage (13) side is recessed,
The heat insulating portion (123) extends over the entire area of the refrigerant passage (12) in a direction orthogonal to the stacking direction and in a direction orthogonal to the longitudinal direction of the refrigerant passage (12),
The heat insulating part (123) constitutes a part of the heat medium passage (13),
The heat medium circulates inside the heat insulating part (123),
A heat medium side inner fin (53) that promotes heat exchange between the refrigerant and the heat medium is provided in the heat medium passage (13),
The stacked heat exchanger , wherein the heat medium flows into the heat insulating portion (123) through a gap between the wall portions of the heat medium side inner fin (53) . Among the two first plate members (11) forming the heat medium passage (13), at least one of the first plate members (11) includes the one first plate member (11). A protruding portion (112) protruding toward the other opposing first plate member (11) is formed,
Laminated heat exchanger according to claim 1 or 10 wherein the condensing portion (121) spaced apart from the supercooling unit (122), characterized in that it is insulated by the protrusion (112). The protrusion (112) has a shape in which the heat medium passage (13) side is recessed toward the refrigerant passage (12) side,
12. The stacked heat exchanger according to claim 11 , wherein a recessed portion of the projecting portion (112) communicates with the heat medium passage (13).

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