JP6102612B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that exchanges heat between a refrigerant and a heat medium having a pressure lower than that of the refrigerant.

  Conventionally, Patent Document 1 describes a water / refrigerant heat exchanger for exchanging heat between refrigerant and water. In this prior art, a refrigerant flow path and a water flow path are alternately formed between heat transfer plates by overlapping a plurality of substantially flat heat transfer plates at intervals. Generally, in this type of water / refrigerant heat exchanger, the refrigerant has a higher pressure than water.

JP 2000-258082 A

  When a heat exchange system for exchanging heat between refrigerant and air is configured using the water / refrigerant heat exchanger of the above prior art and a water / air heat exchanger that exchanges heat between water and air, The temperature difference between the refrigerant and water in the exchanger is smaller than the temperature difference between the refrigerant and air.

  Therefore, in the water / refrigerant heat exchanger in this heat exchange system, it is difficult to surely exchange heat between the refrigerant and the air / refrigerant heat exchanger that exchanges heat between the refrigerant and air. As a result, the state of the outlet refrigerant of the water / refrigerant heat exchanger tends to become unstable compared to the state of the outlet refrigerant of the air / refrigerant heat exchanger. That is, the outlet refrigerant of the water / refrigerant heat exchanger is likely to be in a mixed state of a gas-liquid two-phase state and a single-phase state as compared with the outlet refrigerant of the air / refrigerant heat exchanger.

  Moreover, in the water / refrigerant heat exchanger of the above-described prior art, it is necessary to have a structure that can ensure pressure resistance against the pressure of the refrigerant.

  In view of the above points, the present invention improves the heat exchange performance between the refrigerant and the heat medium in the heat exchanger that exchanges heat between the refrigerant and the heat medium having a pressure lower than that of the refrigerant, and improves the pressure resistance against the pressure of the refrigerant. The purpose is to secure.

In order to achieve the above object, in the invention described in claim 1,
A heat exchange section (12) for exchanging heat between the refrigerant and the heat medium having a pressure lower than that of the refrigerant;
The heat exchange part (12) is formed by laminating and joining a large number of plate-like members (11),
A plurality of refrigerant flow paths (121) through which the refrigerant flows and a plurality of heat medium flow paths (122) through which the heat medium flows are formed between the multiple plate-like members (11),
The plurality of refrigerant channels (121) and the plurality of heat medium channels (122) are arranged side by side in the stacking direction of a large number of plate-like members (11),
The plurality of heat medium flow paths (122) are provided with inner walls ( 30 , 112) that join adjacent plate-like members (11) and cross the heat medium flow path (122) in the stacking direction. And
Among the plurality of heat medium flow paths (122), the first outermost heat medium flow path (122A) located on the most end side in the laminating direction of the plate-shaped members (11) is formed of a plurality of plate-shaped members (11). Of these, the first endmost plate member (11A) located on the most end side in the laminating direction of the plate-like members (11) and the first endmost plate-like member (11A) among the multiple plate-like members (11). Is formed between the one end side plate member (11B) adjacent to
The inner walls (30, 112) provided in the first outermost heat medium flow path (122A) are located on the other end side in the stacking direction of the plate-like members (11) among the plurality of heat medium flow paths (122). A portion having a larger plate thickness than the internal walls (30, 112) provided in the other heat medium flow path (122) excluding the second endmost heat medium flow path (122B) located ;
The second endmost heat medium flow path (122B) is the second endmost plate member (11C) located on the other end side among the many plate members (11) constituting the heat exchanging section (12). And the other end side plate member (11D) adjacent to the second outermost plate member (11C),
The inner walls (30, 112) provided in the second endmost heat medium flow path (122B) are other than the first endmost heat medium flow path (122A) among the plurality of heat medium flow paths (122). It has the site | part whose plate | board thickness is larger than the internal wall (30,112) provided in the heat-medium flow path (122) .

  According to this, the first endmost heat medium flow path (122A) is formed between the first endmost plate-like member (11A) and the one end side plate-like member (11B). A flow path (122A) will be formed in the one end side part in the lamination direction of a plate-shaped member (11) among heat exchange parts (12).

  Therefore, since the heat medium flow path (122A) is arranged on one end side in the stacking direction of the plate-like member (11) with respect to the refrigerant flow path (121), the plate-like member is more than with the refrigerant flow path (121). The heat exchange performance between the refrigerant and the heat medium can be improved as compared with the case where the heat medium flow path (122A) is not disposed on one end side in the stacking direction of (11).

Furthermore, the inner wall (30, 112) provided in the first outermost heat medium flow path (122A) is thicker than the inner wall (30, 112) provided in the other heat medium flow path (122). In the heat exchanging part (12), the strength of the part forming the first endmost heat medium flow path (122A) is set to the part forming the other heat medium flow path (122). Can be stronger. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  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 front view of the heat exchanger in a 1st embodiment. It is II arrow directional view of FIG. It is a perspective view of the offset fin in the heat exchanger of a 1st embodiment. It is a perspective view of the plate-shaped member in the heat exchanger of 2nd Embodiment. It is sectional drawing of the heat exchanger in 2nd Embodiment. It is a perspective view of the plate-shaped member in the heat exchanger of 3rd Embodiment. It is a perspective view of the offset fin in the heat exchanger of a 3rd embodiment. It is sectional drawing of the heat exchanger in 3rd Embodiment.

  Hereinafter, embodiments 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)
The heat exchanger 10 shown in FIGS. 1 and 2 constitutes a refrigeration cycle of a vehicle air conditioner. The heat exchanger 10 is a condenser that condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant of the refrigeration cycle and cooling water (a heat medium having a pressure lower than that of the high-pressure side refrigerant), or cooling with the low-pressure side refrigerant of the refrigeration cycle. This is an evaporator that exchanges heat with water (a heat medium having a pressure lower than that of the low-pressure side refrigerant) to evaporate the low-pressure side refrigerant.

  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 10 is integrally formed by laminating and joining a large number of plate-like members 11. Hereinafter, the laminating direction of the plate-like member 11 (vertical direction in the example of FIG. 1) is referred to as the plate laminating direction, and one end side in the plate laminating direction (the upper end side in the example of FIG. 1) is referred to as one end side of the plate laminating direction. The other end side in the plate stacking direction (lower end side in the example of FIG. 1) is referred to as the other end side in the plate stacking direction.

  The plate-like member 11 is an elongated, substantially rectangular plate material. As a specific material, for example, a double-sided clad material in which a brazing material is clad on both surfaces of an aluminum core material is used.

  On the outer peripheral edge portion of the substantially rectangular 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 plate-like member 11) is formed. Many plate-like members 11 are joined to each other by brazing in a state where the plate-like members 11 are laminated with each other.

  The many plate-like members 11 are arranged so that the protruding tips of the overhanging portions 111 face the same side (substantially downward in the example of FIG. 1).

  A large number of plate-like members 11 form a heat exchanging portion 12, a refrigerant first tank space 13, a refrigerant second tank space 14, a cooling water first tank space 15, and a cooling water second tank space 16. Yes. The heat exchange unit 12 includes a plurality of refrigerant channels 121 and a plurality of cooling water channels 122.

  The plurality of refrigerant flow paths 121 and the plurality of heat medium flow paths are formed between a large number of plate-like members 11. The longitudinal directions of the refrigerant flow path 121 and the cooling water flow path 122 coincide with the longitudinal direction of the plate-like member 11.

  The refrigerant channel 121 and the cooling water channel 122 are alternately stacked one by one in the plate stacking direction (in parallel). The plate-like member 11 serves as a partition wall that partitions the coolant channel 121 and the cooling water channel 122. Heat exchange between the refrigerant flowing through the refrigerant flow path 121 and the cooling water flowing through the cooling water flow path 122 is performed via the plate-like member 11.

  Cooling water flows through the flow path 122A located closest to one end side in the plate stacking direction among the refrigerant flow path 121 and the cooling water flow path 122 formed in the heat exchange section 12.

  In other words, among the plurality of cooling water passages 122, the first outermost cooling water passage 122A (first outermost heat medium passage) located closest to one end in the plate stacking direction is a large number of sheets constituting the heat exchange unit 12. The plate-like member 11 is formed between the first endmost plate-like member 11 </ b> A located closest to one end side in the plate stacking direction and the one end-side plate-like member 11 </ b> B adjacent to the first endmost plate-like member 11. .

  Therefore, the first outermost coolant channel 122A is disposed closer to the one end side in the plate stacking direction than the first outermost coolant channel 121A located closest to the one end side in the plate stacking direction among the plurality of refrigerant channels 121. Become.

  Therefore, compared with the case where 122 A of 1st endmost cooling water flow paths are not arrange | positioned rather than the 1st endmost refrigerant | coolant flow path 121 at the plate lamination direction one end side, the heat exchange performance of a refrigerant | coolant and cooling water can be improved.

  Cooling water flows through the flow path 122B located closest to the other end side in the plate stacking direction among the refrigerant flow path 121 and the cooling water flow path 122 formed in the heat exchange section 12.

  In other words, among the plurality of cooling water passages 122, the second outermost cooling water passage 122B (second outermost heat medium passage) located closest to the other end side in the plate stacking direction is a large number constituting the heat exchange unit 12. Formed between the second outermost plate member 11C located closest to the other end side in the plate stacking direction of the plate members 11 and the other end plate member 11D adjacent to the second outermost plate member 11C. Has been.

  Accordingly, the second endmost cooling water flow path 122B is disposed on the other end side in the plate stacking direction with respect to the second endmost refrigerant flow path 121B located closest to the other end side in the plate stacking direction among the plurality of refrigerant flow paths 121. It will be.

  Therefore, the heat exchange performance between the refrigerant and the cooling water can be improved as compared with the case where the second endmost cooling water flow path 122B is not disposed on the other end side in the plate stacking direction with respect to the second endmost refrigerant flow path 121B.

  The first tank space for refrigerant 13 and the first tank space for cooling water 15 are arranged on one side (left side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12. Has been. The second tank space for refrigerant 14 and the second tank space for cooling water 16 are arranged on the other side (right side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12. Has been.

  The refrigerant first tank space 13 and the refrigerant second tank space 14 distribute and collect the refrigerant with respect to the plurality of refrigerant flow paths 121. The first tank space for cooling water 15 and the second tank space for cooling water 16 distribute and collect the cooling water to the plurality of cooling water flow paths 122.

  The first tank space 13 for refrigerant, the second tank space 14 for refrigerant, the first tank space 15 for cooling water, and the second tank space 16 for cooling water are at the four corners of the plate-like member 11 (in the example of FIG. It is comprised by the communicating hole formed in the four corners.

  A first joint 21 and a first cooling water pipe 22 are attached to the first endmost plate-like member 11A. The first joint 21 is a member for joining refrigerant pipes, and forms the refrigerant inlet 101 of the heat exchanger 10. The first cooling water pipe 22 forms the cooling water outlet 102 of the heat exchanger 10.

  A second joint 23 and a second cooling water pipe 24 are attached to the second endmost plate member 11B. The second joint 23 is a member for joining refrigerant pipes and forms the refrigerant outlet 103 of the heat exchanger 10. The second cooling water pipe 24 forms the cooling water inlet 104 of the heat exchanger 10.

  The refrigerant inlet 101 and the refrigerant outlet 103 communicate with the first refrigerant tank space 13. The cooling water outlet 102 and the cooling water inlet 104 communicate with the first tank space 15 for cooling water.

  The first tank space 13 for refrigerant is partitioned into two spaces in the plate stacking direction. Therefore, as shown by the solid line arrow in FIG. 1, the refrigerant flowing from the refrigerant inlet 101 passes through the refrigerant flow paths 121 and 121A on one end side in the plate stacking direction from the refrigerant first tank space 13 side to the refrigerant second tank space 14. After flowing toward the side, the refrigerant flow paths 121 and 121B on the other end side in the plate stacking direction flow from the refrigerant second tank space 14 side toward the refrigerant first tank space 13 side and flow out from the refrigerant outlet 103. . That is, the heat exchanger 10 is configured such that the refrigerant flow makes a U-turn once.

  Similarly, the cooling water first tank space 15 is partitioned into two spaces in the plate stacking direction. Therefore, as shown by the one-dot chain line arrow in FIG. 1, the cooling water flowing from the cooling water inlet 104 passes through the cooling water flow paths 122 and 122B on the other end side in the plate stacking direction from the cooling water first tank space 15 side. After flowing toward the second tank space 16 side, the cooling water flow paths 122 and 122A on one end side in the plate stacking direction flow from the second tank space 16 side for cooling water toward the first tank space 15 side for cooling water. And flows out from the cooling water outlet 102. That is, the heat exchanger 10 is configured so that the flow of the cooling water makes a U-turn once.

  The heat exchanger 10 is configured such that the refrigerant flow and the cooling water flow are in opposite directions (opposite flow).

  The offset fins 30 shown in FIG. 3 are arranged between the plate-like members 11. The offset fins 30 are inner fins that are interposed between the plate-like members 11 and promote heat exchange between the refrigerant and the heat medium.

  The offset fin 30 is a plate-like member on which a partially raised portion 301 is formed. A large number of cut-and-raised portions 301 are formed in a direction F1 (that is, the longitudinal direction of the plate-like member 11) parallel to the flow direction of the refrigerant and the cooling water.

  The cut-and-raised portions 301 adjacent to each other in the direction F1 parallel to the flow direction of the refrigerant and the cooling water are offset from each other. In the example of FIG. 3, the large number of cut-and-raised parts 301 are staggered in a direction F1 parallel to the flow direction of the refrigerant and the cooling water.

  As a specific material of the offset fin 30, for example, a double-sided clad material in which a brazing material is clad on both sides of an aluminum core is used. The offset fins 30 are joined to both adjacent plate-like members 11 by brazing.

  Therefore, the offset fin 30 constitutes an internal wall that joins the adjacent plate-like members 11 and crosses the coolant channel 121 and the cooling water channel 122 in the plate stacking direction.

  The offset fins 30 provided in the first outermost cooling water channel 122A are more than the offset fins 30 provided in the other cooling water channels 122 except for the second outermost cooling water channel 122B among the plurality of cooling water channels 122. It has a part with a large plate thickness.

  For example, the offset fins 30 provided in the first outermost cooling water channel 122A are offset fins 30 provided in other cooling water channels 122 excluding the second outermost cooling water channel 122B among the plurality of cooling water channels 122. It is formed with the board | plate material with a board thickness large compared with.

  Thereby, the intensity | strength of the site | part which forms 122 A of 1st most end cooling water flow paths among the heat exchange parts 12 can be made stronger than the site | part which forms the other cooling water flow path 122. FIG. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  The offset fins 30 provided in the second outermost cooling water channel 122B are more than the offset fins 30 provided in the cooling water channels 122 other than the first outermost cooling water channel 122A among the plurality of cooling water channels 122. It has a part with a large plate thickness.

  The offset fins 30 provided in the second outermost cooling water channel 122B are compared with the offset fins 30 provided in other cooling water channels 122 other than the first outermost cooling water channel 122A among the plurality of cooling water channels 122. And it is formed with the board | plate material with large board thickness.

  Thereby, the intensity | strength of the site | part which forms the 2nd most end cooling water flow path 122B among the heat exchange parts 12 can be made stronger than the site | part which forms the other cooling water flow path 122. FIG. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  According to this embodiment, since the first endmost cooling water flow path 122A is formed between the first endmost plate-like member 11A and the one end side plate-like member 11B, the first endmost cooling water flow path 122A In the exchange part 12, it will form in the site | part of the one end side of a board lamination direction most.

  Therefore, since the cooling water flow path 122A is arranged at one end side in the plate stacking direction from the refrigerant flow path 121, compared with the case where the cooling water flow path 122A is not arranged at one end side in the plate stacking direction from the refrigerant flow path 121. Thus, the heat exchange performance between the refrigerant and the cooling water can be improved.

Furthermore, since the offset fin 30 provided in the first endmost cooling water flow path 122A has a portion having a larger plate thickness than the offset fin 30 provided in the other cooling water flow path 122, the heat exchange unit 12 strength of the portion forming a first endmost cooling water flow path 122A of the can stronger than parts to form the other cooling water passage 122. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  According to this embodiment, since the offset fins 30 are provided in the first endmost cooling water flow path 122A, the distribution of cooling water can be improved.

According to this embodiment, since the second outermost cooling water channel 122B is formed between the second top end plate member 11 C and the other end-side plate member 11 D, a second endmost cooling water channel 122B Is formed at a portion of the heat exchanging portion 12 that is closest to the other end side in the plate stacking direction.

  Therefore, since the cooling water flow path 122B is disposed on the other end side in the plate stacking direction from the refrigerant flow path 121, the cooling water flow path 122B is not disposed on the other end side in the plate stacking direction from the refrigerant flow path 121. In comparison, the heat exchange performance between the refrigerant and the cooling water can be improved.

Further, the offset fin 30 provided in the second endmost cooling water flow path 122B has a portion having a larger plate thickness than the offset fins 30 provided in the other cooling water flow paths 122. strength of the portion forming the second outermost cooling water channel 122B of the can stronger than parts to form the other cooling water passage 122. For this reason, the pressure | voltage resistance with respect to a refrigerant | coolant pressure is further securable.

  According to this embodiment, since the offset fins 30 are provided in the second endmost cooling water flow path 122B, the distribution of cooling water can be improved.

(Second Embodiment)
In the said 1st Embodiment, although the adjacent plate-shaped members 11 are joined and the internal wall which crosses the refrigerant | coolant flow path 121 and the cooling water flow path 122 in a plate lamination direction is comprised by the offset fin 30, this embodiment In the form, as shown in FIGS. 4 and 5, the inner wall is constituted by ribs 112 formed by stamping on the plate-like member 11.

  In the example of FIG. 4, the rib 112 is formed in a groove shape extending in a direction inclined with respect to the longitudinal direction of the plate-like member 11.

  The ribs 112 are driven out from both ends of the plate stacking direction toward the center. That is, the rib 112 is driven out from the one end side in the plate stacking direction toward the other end side in the portion on the one end side in the plate stacking direction of the heat exchange unit 12. At the other end of the heat exchanging portion 12 in the plate stacking direction, the rib 112 is driven out from the other end in the plate stacking direction toward the one end.

  The rib 112 provided in the first outermost cooling water channel 122A is thicker than the ribs 112 provided in the other cooling water channels 122 other than the second outermost cooling water channel 122B among the plurality of cooling water channels 122. It has a large part.

  For example, the first endmost plate-like member 11A that forms the first endmost cooling water flow path 122A is formed with the other cooling water flow paths 122 other than the second endmost cooling water flow path 122B among the plurality of cooling water flow paths 122. By forming the plate member 11 having a plate thickness larger than that of the plate-like member 11, the plate thickness of the rib 112 provided in the first outermost cooling water channel 122 </ b> A is set to the second outermost cooling water channel 122. It is larger than the plate thickness of the rib 112 provided in the other cooling water flow paths 122 excluding the cooling water flow path 122B.

  Thereby, the intensity | strength of the site | part which forms 122 A of 1st most end cooling water flow paths among the heat exchange parts 12 can be made stronger than the site | part which forms the other cooling water flow path 122. FIG. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  The rib 112 provided in the second outermost cooling water flow path 122B is thicker than the rib 112 provided in the other cooling water flow paths 122 other than the first outermost cooling water flow path 122A among the plurality of cooling water flow paths 122. It has a large part.

  For example, the second endmost plate-like member 11B that forms the second endmost cooling water flow path 122B is formed into a plate shape that forms the other cooling water flow paths 122 excluding the most end cooling water flow path 122A among the plurality of cooling water flow paths 122. By forming the plate 112 having a plate thickness larger than that of the member 11, the plate thickness of the rib 112 provided in the second endmost cooling water channel 122 </ b> B is changed to the endmost cooling water channel 122 </ b> A among the plurality of cooling water channels 122. It is made larger than the plate | board thickness of the rib 112 provided in the other cooling water flow paths 122 except for.

  Thereby, the intensity | strength of the site | part which forms the 2nd most end cooling water flow path 122B among the heat exchange parts 12 can be made stronger than the site | part which forms the other cooling water flow path 122. FIG. For this reason, the pressure resistance with respect to a refrigerant pressure is securable.

  In this embodiment, the inner wall is constituted by the ribs 112 formed by stamping on the plate-like member 11. Therefore, since the inner wall can be formed without using a member separate from the plate-like member 11, the configuration can be simplified.

(Third embodiment)
In the present embodiment, as shown in FIGS. 6 to 8, the offset fin 30 of the first embodiment and the rib 112 of the second embodiment are combined.

  In the present embodiment, as shown in FIG. 6, the rib 112 has a circular planar shape. A portion of the offset fin 30 corresponding to the rib 112 is cut out to form a through hole. In FIG. 7, for the convenience of illustration, the cut-and-raised portion 301 is formed on the entire offset fin 30, but in reality, a region surrounded by a two-dot chain line in FIG. 7 (part corresponding to the rib 112). The through hole is formed by cutting out the hole.

  As a result, as shown in FIG. 8, the rib 112 of the plate-like member 11 is arranged in a portion where the through-hole is formed (the portion that is hollowed out) in the offset fin 30, and the rib 112 and the offset fin 30. Interference with is avoided.

  According to the present embodiment, since both the offset fin 30 and the rib 112 are provided, it is possible to further secure pressure resistance against the refrigerant pressure.

  In the present embodiment, the offset fin 30 and the rib 112 constitute an inner wall. According to this, as compared with the case where only one of the offset fin 30 and the rib 112 is provided, the pressure resistance against the refrigerant pressure can be further ensured. Furthermore, the distribution of cooling water can be improved by the offset fins 30.

(Other embodiments)
The above embodiment can be variously modified as follows, for example.

  (1) In the above embodiment, the refrigerant flow paths 121 and the cooling water flow paths 122 are alternately stacked one by one in the plate stacking direction. For example, the refrigerant flow paths 121 and the cooling water flow paths 122 are in the plate stacking direction. A plurality of them may be alternately stacked.

  (2) In the above embodiment, a refrigerant flow path through which the refrigerant flows may be formed outside the heat exchange unit 12. For example, a refrigerant flow path through which the refrigerant flowing into the heat exchange unit 12 flows may be formed on one end side in the plate stack direction with respect to the heat exchange unit 12. Similarly, a refrigerant channel through which the refrigerant that has flowed out of the heat exchange unit 12 flows may be formed on the other end side in the plate stack direction than the heat exchange unit 12.

  (3) In the above embodiment, the heat exchanger 10 is configured such that the refrigerant flow and the cooling water flow make one U-turn, but the refrigerant flow and the cooling water flow do not make a U-turn. You may be comprised, and it may be comprised so that the flow of a refrigerant | coolant and the flow of cooling water may make a U-turn a plurality of times.

  (4) In the above embodiment, the heat exchanger 10 is configured such that the refrigerant flow and the cooling water flow are in opposite directions (opposite flow), but the refrigerant flow and the cooling water flow May be configured to be in the same direction (parallel flow).

  (5) In the above embodiment, cooling water is used as the heat medium, but various media such as oil may be used as the heat medium.

  A nanofluid may be used as the heat medium. A nanofluid is a fluid in which nanoparticles having a particle size of the order of nanometers are mixed. In addition to the effect of lowering the freezing point as in the case of cooling water using ethylene glycol (so-called antifreeze liquid), the following effects can be obtained by mixing the nanoparticles with the heat medium.

  That is, the effect of improving the thermal conductivity in a specific temperature range, the effect of increasing the heat capacity of the heat medium, the effect of preventing the corrosion of metal pipes and the deterioration of rubber pipes, and the heat medium at an extremely low temperature The effect which improves the fluidity | liquidity of can be acquired.

  Such effects vary depending on the particle configuration, particle shape, blending ratio, and additional substance of the nanoparticles.

  According to this, since the thermal conductivity can be improved, it is possible to obtain the same cooling efficiency even with a small amount of heat medium as compared with the cooling water using ethylene glycol.

  Moreover, since the heat capacity of the heat medium can be increased, the amount of heat stored in the heat medium itself (cold heat stored by sensible heat) can be increased.

  By increasing the amount of cold storage heat, even when the compressor of the refrigeration cycle is not in operation, equipment cooling using the cold storage heat and temperature control of heating can be performed for a certain amount of time. Motorization becomes possible.

  The aspect ratio of the nanoparticles is preferably 50 or more. This is because sufficient thermal conductivity can be obtained. The aspect ratio is a shape index that represents the ratio of the vertical and horizontal dimensions of the nanoparticles.

  Nanoparticles containing any of Au, Ag, Cu and C can be used. Specifically, Au nanoparticle, Ag nanowire, CNT (carbon nanotube), graphene, graphite core-shell nanoparticle (a structure such as a carbon nanotube surrounding the above atom is included as a constituent atom of the nanoparticle. Particles), Au nanoparticle-containing CNTs, and the like can be used.

DESCRIPTION OF SYMBOLS 11 Plate-shaped member 11A 1st outermost plate-shaped member 11B One end side plate-shaped member 11C 2nd most end plate-shaped member 11D Other end side plate-shaped member 12 Heat exchange part 121 Refrigerant flow path 122 Cooling water flow path (heat medium flow path)
122A 1st most end cooling water flow path (1st most end heat medium flow path)
122B 2nd most end cooling water flow path (2nd most end heat medium flow path)
30 Offset fin (inner fin, inner wall)
301 Cut and raised part

Claims (6)

Refrigerant and said heat exchange unit for heat exchange between the low pressure of the heat medium than the refrigerant comprises a (12),
The heat exchange part (12) is formed by laminating and joining a large number of plate-like members (11) to each other,
A plurality of refrigerant flow paths (121) through which the refrigerant flows and a plurality of heat medium flow paths (122) through which the heat medium flows are formed between the plurality of plate-like members (11).
The plurality of refrigerant channels (121) and the plurality of heat medium channels (122) are arranged side by side in the stacking direction of the plurality of plate-like members (11),
Inner walls ( 30 , 112) that join the adjacent plate-like members (11) to the plurality of heat medium flow paths (122) and cross the heat medium flow path (122) in the stacking direction. Is provided,
Of the plurality of heat medium channels (122), the first outermost heat medium channel (122A) located on the most end side in the stacking direction is the one end of the multiple plate-like members (11). A first end plate member (11A) positioned on the side, and one end plate member (11B) adjacent to the first end plate member (11A) among the plurality of plate members (11). Formed between
The inner walls (30, 112) provided in the first outermost heat medium flow path (122A) are located on the other end side in the stacking direction among the plurality of heat medium flow paths (122). 2 has a portion with a larger plate thickness than the internal walls (30, 112) provided in the other heat medium flow path (122) except for the outermost heat medium flow path (122B) ,
The second endmost heat medium flow path (122B) is a second endmost plate shape that is located closest to the other end side among the multiple plate-like members (11) constituting the heat exchanging portion (12). Formed between the member (11C) and the other end side plate member (11D) adjacent to the second endmost plate member (11C),
The inner walls (30, 112) provided in the second outermost heat medium flow path (122B) are the first outermost heat medium flow path (122A) of the plurality of heat medium flow paths (122). It has a site | part with a plate | board thickness larger than the said internal wall (30,112) provided in the said other heat-medium flow path (122) except for . The inner wall is an inner fin (30) that is interposed between the plate-like members (11) and promotes heat exchange between the refrigerant and the heat medium,
The inner fin (30) has a plurality of cut and raised portions (301) partially cut and raised in the flow direction of the heat medium, and the cut and raised portions (301) adjacent to each other in the flow direction of the heat medium. The heat exchanger according to claim 1, wherein the fins are offset fins that are offset from each other.   The heat exchanger according to claim 1, wherein the inner wall (30, 112) is a rib (112) formed by stamping on the plate-like member (11). The inner wall is interposed between the plate-like members (11) and promotes heat exchange between the refrigerant and the heat medium, and the adjacent plate-like members (11). ) Is a rib (112) formed by stamping on the plate-like member (11) on the one end side,
The inner fin (30) has a plurality of cut and raised portions (301) partially cut and raised in the flow direction of the heat medium, and the cut and raised portions (301) adjacent to each other in the flow direction of the heat medium. The heat exchanger according to claim 1, wherein the fins are offset fins that are offset from each other. The through hole for avoiding interference with the rib (112) is formed in a portion corresponding to the rib (112) in the inner fin (30). Heat exchanger.   The heat exchanger according to any one of claims 1 to 5, wherein the heat medium is an ethylene glycol antifreeze.

Images