JP5768844B2 - Cold storage heat exchanger - Google Patents

Description

  The present invention relates to a cold storage heat exchanger used in a refrigeration cycle apparatus.

  Conventionally, a regenerative cooling apparatus for truck driver nap described in Patent Document 1 is known. The container enclosing the regenerator material of Patent Document 1 is made of a resin film, and has a concave portion and a convex portion on the surface of the container. With this concave portion, a shape that can secure an air flow path cooled by the regenerator material is obtained. ing.

  Then, during cold storage, a refrigerant is passed through the refrigerant pipe that sandwiches the container to store cold, and a nap evaporator is configured to cool by supplying air passing through the air passage to a driver who takes a nap. ing. The vehicle interior evaporator that cools the driver during operation is installed separately from the nap evaporator, so that the refrigerant from the compressor flows in parallel to both evaporators.

JP-A-8-175167

  According to the technique of Patent Document 1, the cold storage heat exchanger that constitutes the nap evaporator only stores air and then flows air to exchange heat with the cold storage material. In addition, a cooling heat exchanger as another evaporator is necessary, which increases the cost.

  The present invention has been made paying attention to such problems existing in the prior art, and its purpose is to use a single heat exchanger for cold storage, indoor cooling with a refrigerant pipe, and It is to obtain a cold storage heat exchanger that can realize indoor cooling by allowing the cold storage material to cool.

  Descriptions of patent documents listed as prior art can be introduced or incorporated by reference as explanations of technical elements described in this specification.

In order to achieve the above object, the present invention employs the following technical means. That is, in the first aspect of the present invention, a plurality of refrigerant pipes (45) having a refrigerant passage and arranged at intervals from each other are sandwiched and joined between the refrigerant pipes , and the regenerator material (50). And a regenerator container (47) that divides a room for housing the inside, the inner fin (47f) is arranged inside the regenerator container (47) , and is not joined to the refrigerant pipe of the regenerator container (47). A member for stopping the inner fin (47f) is formed in the recess (47a2) , and the inner fin (47f) is disposed below the member for stopping the inner fin (47f), and the cold storage container (47) The air is sealed in a portion above the member that stops the inner fin (47f).

  In this invention, by enclosing air above the member that stops the inner fin formed in the cool storage material container (47), the cool storage material container is expanded when the cool storage material is expanded by the compression action of air. The stress applied to can be reduced.

The invention according to claim 2 is characterized in that the member for stopping the inner fin (47f) is a launch portion (47g) for stopping the inner fin (47f) inside the cold storage material container (47). In the present invention, the inner fin (47f) can be stopped inside the cool storage material container by the launch portion (47g).

In addition, the code | symbol in the parenthesis as described in a claim and said each means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a block diagram of the refrigerating cycle apparatus which comprises the vehicle air conditioner in 1st Embodiment of this invention. It is a top view of the evaporator in the said embodiment. It is a side view of the evaporator seen from the arrow III direction of FIG. FIG. 4 is a partial enlarged cross-sectional view schematically showing a part of a cross section taken along line IV-IV in FIG. 2. It is a partially expanded sectional view which shows the relationship of the refrigerant | coolant pipe | tube, the cool storage material container, and the air side fin which show typically a part of cross section along the VV line | wire of FIG. It is the internal side view which looked at the cool storage material container of FIG. 5 from the arrow IV direction. It is explanatory drawing for demonstrating a mode that condensed water is discharged | emitted when the evaporator of the said embodiment is mounted in the mounting direction of the orthogonal | vertical direction in the vehicle air conditioner. It is explanatory drawing for demonstrating a mode that the process liquid in the surface treatment process of the said evaporator is discharged | emitted. It is a partially expanded side view of the cool storage material container similar to FIG. 6 in 2nd Embodiment of this invention. It is a partially expanded sectional view which shows the relationship between a refrigerant | coolant pipe | tube, a cool storage material container, and an air side fin similar to FIG. 5 in the said 2nd Embodiment. It is the characteristic view which showed the relationship between the brazing area ratio of a cool storage material container and a refrigerant pipe, and the capability ratio of an evaporator in the said 1st Embodiment and the said 2nd Embodiment. It is explanatory drawing which illustrates typically the flow of the brazing material at the time of brazing in the structure of FIG. It is a side view of the cool storage material container which has the uneven | corrugated shape of a lattice arrangement | sequence as other embodiment. It is a side view of the cool storage material container which has the uneven | corrugated shape of diagonal arrangement | sequence as other embodiment. It is a side view of the cool storage material container which has the uneven | corrugated shape of a round zigzag arrangement | sequence as other embodiment. As other embodiment, it is a side view of the cool storage material container which has the uneven | corrugated shape of a circular grid | lattice arrangement | sequence. It is a partially expanded sectional view which shows the relationship between the refrigerant | coolant pipe | tube, the cool storage material container, and the air side fin which show typically a part of cross section along the VV line | wire of FIG. 3 in 3rd Embodiment of this invention. FIG. 18 (a) is a case where the outer surface bonding ratio X is moderately small, illustrating the performance deterioration due to the size of the bonding ratio between the inner fins of the evaporator of the third embodiment and the cold storage material container. FIG. 18B is a partially enlarged cross-sectional view when the outer surface bonding ratio X is too large. It is various graphs explaining the performance by the magnitude of the joining ratio of the inner fin of the evaporator of the said 3rd Embodiment, and a cool storage material container. It is a partial side view which shows the shape of the rib of the cool storage material container surface in the evaporator of 4th Embodiment of this invention. It is a partial side view which shows the shape of the rib of the cool storage material container surface in the evaporator of 5th Embodiment of this invention. It is a partial side view which shows the shape of the rib of the cool storage material container surface in the evaporator of 6th Embodiment of this invention. It is a partial side view which shows the shape of the rib of the cool storage material container surface in the evaporator of 7th Embodiment of this invention. It is a front view of the evaporator with a cool storage material formed with the lamination | stacking plate in 8th Embodiment of this invention. It is a left view of the evaporator with a cool storage material of FIG. It is typical sectional drawing which shows the evaporator by which the refrigerant | coolant pipe | tube was manufactured with the tube of the drone cup used as 8th Embodiment of this invention in contrast with the evaporator manufactured by the extrusion manufacturing method. It is typical sectional drawing which shows the evaporator by which the refrigerant pipe was manufactured with the tube of the drone cup used as 9th Embodiment of this invention in contrast with the evaporator manufactured by the extrusion manufacturing method. It is typical sectional drawing of the evaporator illustrated similarly to FIG. 4 regarding 10th Embodiment of this invention. FIG. 29 is a schematic cross-sectional view showing an enlarged portion of an arrow Z33 in FIG. 28. FIG. 29 is a schematic cross-sectional view showing an enlarged portion of an arrow Z34 in FIG. 28. It is a graph explaining the state from which the temperature of an evaporator changes with the intermittent operation of a compressor in 10th Embodiment of this invention. It is a side view which shows the state which formed the rib of the surface of the cool storage material container of the evaporator of FIG. 28 in the reverse V shape.

(First embodiment)
FIG. 1 is a configuration diagram of a refrigeration cycle apparatus that constitutes a vehicle air conditioner according to a first embodiment of the present invention. The refrigeration cycle apparatus 1 constituting the air conditioner includes a compressor 10, a radiator 20, a decompressor 30, and an evaporator (evaporator) 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path.

  The compressor 10 is driven by an internal combustion engine (or an electric motor or the like) that is a power source 2 for traveling the vehicle. When the power source 2 stops, the compressor 10 also stops. The compressor 10 sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator 20. The radiator 20 cools the high-temperature refrigerant. The radiator 20 is also called a condenser. The decompressor 30 decompresses the refrigerant cooled by the radiator 20. The evaporator 40 evaporates the refrigerant decompressed by the decompressor 30 and cools the passenger compartment air.

  FIG. 2 is a plan view of the evaporator 40 according to the first embodiment. FIG. 3 is a side view seen from the direction of arrow III in FIG. FIG. 4 is an enlarged cross-sectional view schematically showing a part of a cross section taken along line IV-IV in FIG. FIG. 5 is an enlarged cross-sectional view showing the relationship among the refrigerant pipe, the cool storage material container, and the air-side fins schematically showing a part of the cross section taken along the line VV in FIG. 3.

  2 and 3, the evaporator 40 has a refrigerant passage member branched into a plurality. The refrigerant passage member is provided by a metal passage member such as aluminum. The refrigerant passage member is provided by headers 41, 42, 43, 44 positioned in pairs and a plurality of refrigerant pipes 45 connecting the headers.

  2 and 3, the first header 41 and the second header 42 form a pair, and are arranged in parallel at a predetermined distance from each other. The third header 43 and the fourth header 44 also form a pair, and are arranged in parallel at a predetermined distance from each other. A plurality of refrigerant tubes 45 are arranged at equal intervals between the first header 41 and the second header 42.

  Each refrigerant pipe 45 communicates with the corresponding header 41, 42 at its end. A first heat exchange section 48 (FIG. 3) is formed by the first header 41, the second header 42, and a plurality of refrigerant tubes 45 arranged therebetween. A plurality of refrigerant tubes 45 are arranged at equal intervals between the third header 43 and the fourth header 44.

  Each refrigerant pipe 45 communicates with the corresponding header 43, 44 at its end. A second heat exchanging portion 49 is formed by the third header 43, the fourth header 44, and a plurality of refrigerant tubes 45 arranged therebetween.

  As a result, the evaporator 40 has a first heat exchange unit 48 and a second heat exchange unit 49 arranged in two layers. With respect to the air flow direction indicated by the arrow 400, the second heat exchange unit 49 is disposed on the upstream side, and the first heat exchange unit 48 is disposed on the downstream side.

  A joint (not shown) serving as a refrigerant inlet is provided at the end of the first header 41. The inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate (not shown) provided substantially at the center in the length direction. Correspondingly, the plurality of refrigerant tubes 45 are divided into a first group and a second group.

  The refrigerant is supplied to the first section of the first header 41. The refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group. The refrigerant flows into the second header 42 through the first group and is collected.

  The refrigerant is distributed again from the second header 42 to the plurality of refrigerant tubes 45 belonging to the second group. The refrigerant flows into the second section of the first header 41 through the second group. Thus, in the 1st heat exchange part 48, the flow path which flows a refrigerant | coolant in a U shape is formed.

  A joint (not shown) serving as a refrigerant outlet is provided at the end of the third header 43. The inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate (not shown) provided substantially at the center in the length direction.

  Correspondingly, the plurality of refrigerant tubes 45 are divided into a first group and a second group. The first section of the third header 43 is adjacent to the second section of the first header 41. The first section of the third header 43 and the second section of the first header 41 are in communication.

  The refrigerant flows from the second section of the first header 41 into the first section of the third header 43. The refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group. The refrigerant flows into the fourth header 44 through the first group and is collected. The refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant tubes 45 belonging to the second group.

  The refrigerant flows into the second section of the third header 43 through the second group. Thus, also in the 2nd heat exchange part 49, the flow path which flows a refrigerant | coolant in a U shape is formed. The refrigerant in the second section of the third header 43 flows out from the refrigerant outlet and flows toward the compressor 10.

  In FIG. 2, the plurality of refrigerant tubes 45 are arranged at substantially constant intervals. A plurality of gaps are formed between the plurality of refrigerant tubes 45. A plurality of air-side fins 46 and a plurality of cool storage material containers 47 are arranged and brazed with a predetermined regularity in the plurality of gaps. A part of the gap is a cooling air passage 460. The remaining part of the gap is an accommodating part 461 in which the cool storage material container 47 is arranged.

  10% or more and 50% or less of the total interval formed between the plurality of refrigerant tubes 45 is the accommodating portion 461. The cool storage material containers 47 are arranged almost uniformly distributed throughout the evaporator 40. The two refrigerant tubes 45 located on both sides of the cool storage material container 47 define a cooling air passage 460 for exchanging heat with air on the opposite side to the cool storage material container 47.

  From another viewpoint, as shown in FIG. 4, two refrigerant pipes 45a and 45b are arranged between the two air-side fins 46a and 46b, and one regenerator container 47 is provided between the two refrigerant pipes 45a and 45b. Is arranged.

  4 and 5, the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages on the inner side. The refrigerant pipe 45 (45a and 45b) is also called a flat pipe. This multi-hole tube can be obtained by an extrusion manufacturing method. The plurality of refrigerant passages 45c (FIG. 4) extend along a direction perpendicular to the paper surface of the refrigerant pipe 45 in FIG.

  The plurality of refrigerant tubes 45 are arranged in a row. In each row, the plurality of refrigerant tubes 45 are arranged so that the side surfaces thereof face each other. The plurality of refrigerant tubes 45 define a cooling air passage 460 for exchanging heat with air between two adjacent refrigerant tubes 45a and 45b and an accommodating portion 461 for accommodating the regenerator container 47. doing.

  The evaporator 40 includes an air-side fin member in the cooling air passage 460 for increasing the contact area with the air supplied to the passenger compartment. The air side fin member is provided by a plurality of corrugated air side fins 46 (46a and 46b).

  The air-side fin 46 is thermally coupled to two adjacent refrigerant tubes 45. The air-side fins 46 are joined to the two adjacent refrigerant tubes 45 by a joining material excellent in heat transfer. A brazing material can be used as the bonding material. The air-side fin 46 has a shape in which a thin metal plate such as aluminum is bent in a wave shape, and is called a louver.

  The evaporator 40 further includes a plurality of cold storage material containers 47. The cold storage material container 47 is made of metal such as aluminum. The cool storage material container 47 has a cylindrical shape having uneven portions on the left and right surfaces in FIG.

  The cold storage material container 47 is closed at both ends in the longitudinal direction (not shown) (upper and lower ends of FIGS. 2 and 5), and divides a room for accommodating the cold storage material 50 (FIG. 5). The cool storage material container 47 has a wide main surface on both side surfaces. The two main walls that provide these two main surfaces are each arranged in parallel with the refrigerant pipe 45.

  The cool storage material container 47 is disposed between two adjacent refrigerant tubes 45. The cool storage material container 47 is thermally coupled to the two refrigerant pipes 45 disposed on both sides thereof by the convex portions 47a1 of the outer shell 47a.

  The cool storage material container 47 is joined to the two adjacent refrigerant pipes 45 by a joining material excellent in heat transfer. Although a resin material such as a brazing material or an adhesive material can be used as the bonding material, the cold storage material container 47 of the first embodiment is brazed to the refrigerant pipe 45.

  A brazing material is disposed between the cold storage material container 47 and the refrigerant pipe 45 in order to connect them with a wide cross-sectional area. This brazing material can also be provided by placing a brazing material foil between the cold storage material container 47 and the refrigerant pipe 45. As a result, the cool storage material container 47 performs good heat conduction with the refrigerant pipe 45.

  The cold storage material container 47 has an outer shell 47a that provides the outer surface thereof. And the outer shell 47a of this cool storage material container has an uneven surface shape. The uneven surface shape improves the brazing property with the refrigerant pipe 45 in contact with the cold storage material container 47. That is, the brazing area is reduced so that no voids or gaps are generated.

  47a1 is a convex part and 47a2 is a concave part. The convex portion 47a1 is brazed to the refrigerant pipe 45. By adjusting the amount of Si (silicon) in the brazing material used for brazing, the ease of flowing into the brazing portion can be adjusted. The greater the amount of Si in the brazing material, the easier it is to flow into the brazing part. In addition, the recessed part 47a2 comprises the cool storage material side air passage 461a.

  Moreover, this uneven | corrugated shape is repeated in multiple times with respect to both the longitudinal direction (FIG. 5 up-down direction) of the cool storage material container 47 and the transversal direction of the cool storage material container 47 (up-down direction of FIG. 4). As will be described later, this uneven shape improves the drainage of condensed water and the like.

  As shown in FIG. 5, inside fins 47 f are provided with inner fins 47 f that are thermally and mechanically coupled to the cold storage container 47. The inner fins 47f are joined to the inner wall of the main wall of the cool storage material container 47 by a joining material excellent in heat transfer. This joining is made by brazing. Since the inner fin 47f is coupled to the inner side of the cold storage material container 47, deformation of the cold storage material container 47 is prevented and pressure resistance is improved.

  As shown in FIG. 5, the inner fin 47f has a shape in which a thin metal plate such as aluminum is bent in a wave shape. And since the surface of the cool storage material container 47 is uneven, the inner fin 47f is joined by brazing to the recess 47a2 of the outer shell 47a of the cool storage material container 47, that is, the part protruding inward (inner protrusion). , Improving mechanical strength and pressure resistance. As a result, of the outer shell 47a, the protruding portion 47a1 protruding outward and the inner fin 47f are not joined. In FIG. 5, reference numeral 460 denotes a cooling air passage, and 461a denotes a regenerator-side air passage.

  In FIG. 4, the inner fins 47 f are illustrated as plate members as viewed from the upper side of FIG. 5. FIG. 5 schematically shows the inner fin 47f bent in a wave shape. Actually, as is well known, countless cuts are formed on the surface of the plate by a press.

  6 is an internal side view of the inner wall of the cold storage material container 47 of FIG. 5 as viewed from the direction of the arrow IV. The cold storage material container 47 made of the aluminum molded product of FIG. 6 is a rectangular container having a height of 225 mm, a width of 50 mm, and a thickness of about 5 mm in FIG. A large number of convex portions 47a1 on the surface of the container are formed in a staggered arrangement. This zigzag arrangement is easy to punch out during press molding. Further, the lateral width of the brazed portion of the convex portion 47a1 is set to be about 2 to 5 mm or less in order to prevent the generation of voids.

  A regenerator material 50 (FIG. 5) and inner fins 47 f are accommodated inside the regenerator container 47 having a thickness of about 5 mm. Reference numeral 47g in FIG. 6 denotes a launch portion for stopping the inner fin 47f. The inner fins 47f and the regenerator material 50 are accommodated in the regenerator material container 47 up to the height of the substantially projecting portion 47g. Air is sealed in the cold storage material container 47 above the launching portion 47g. This air compression action relieves the stress of the cold storage material container 47 when the cold storage material 50 (FIG. 5) expands.

  The operational effects of the first embodiment will be described. By providing the plurality of concave portions 47a2 and the convex portions 47a1 on the surface of the cold storage material container 47, the cold storage material container 47 and the refrigerant pipe 45 are in contact with only the outer surface of the convex portion 47a1. Condensed water and the treatment liquid in the evaporator surface treatment process can be discharged from between the convex portions 47a1 (surfaces of the concave portions 47a2).

  FIG. 7 is an explanatory diagram for explaining a state in which condensed water is discharged when the evaporator is mounted on the vehicle air conditioner in a vertical mounting posture. In FIG. 7, the flow from the top direction to the ground direction of a large number of parallel condensed water on the surface of the concave portion 47a2 between the convex portions 47a1 arranged in a staggered manner is indicated by an arrow 47h1.

  Further, by eliminating flat contact over a wide range with the convex portion 47a1, generation of voids after brazing is prevented, and brazing performance is improved.

  As shown in FIG. 5, by providing a plurality of recesses 47a2 and protrusions 47a1 on the surface of the cool storage material container 47, the inner fin 47f of the cool storage material container 47 contacts the cool storage material container 47 only by the inner surface protrusions of the recess 47a2. Will be.

  As a result, a passage 50a is ensured between the inner fin 47f and the cool storage material container 47, and the sealing time can be shortened in the process of sealing the cool storage material 50 in the cool storage material container 47.

  FIG. 8 is an explanatory diagram for explaining how the processing liquid is discharged in the surface treatment process of the evaporator. The cool storage material container 47 dipped in the processing liquid is blown with air by a blower. The flow of the processing liquid on the surface of the concave portion 47a2 between the convex portions 47a1 arranged in a staggered pattern at this time is indicated by an arrow 47h2. Reference numerals 471 and 472 denote blower air blowing directions in the surface treatment fitting step.

  By making the uneven shape of the cold storage material container 47 repeated multiple times with respect to both the longitudinal direction and the short direction of the cold storage material container 47, drainage can be ensured regardless of the attachment angle of the evaporator. In particular, as shown in FIG. 7, a shape in which an oval convex portion 47 a 1 that is elongated in the longitudinal direction of the cold storage material container 47 is recommended in terms of drainage, press moldability, and enclosing property of the cold storage material 50 is recommended.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. FIG. 9 is a side view of a cold storage material container 47 similar to FIG. In the following embodiments, the same components as those in the first embodiment described above are denoted by the same reference numerals, description thereof will be omitted, and different configurations and features will be described.

  In FIG. 9, the center (head portion) of the outer surface convex portions of the plurality of convex portions 47a1 on the surface of the cold storage material container 47 of the second embodiment has a perforated shape. The cold storage material 50 is in direct contact with the refrigerant pipe 45 through the perforated portion 47a3 (as shown in FIG. 10).

  Further, the brazing width of the convex portion 47a1 in the left-right direction in FIG. 9 is desirably 2 to 5 mm or less.

  FIG. 10 is an enlarged cross-sectional view showing the relationship among the refrigerant pipe 45, the cold storage material container 47, and the air-side fins 46, similar to FIG. The cool storage material 50 enclosed in the cool storage material container 47 together with the inner fins 47 f protrudes from the inside of the cool storage material container 47 into the perforated portion 47 a 3 and is in direct contact with the surface of the refrigerant pipe 45. In FIG. 10, reference numeral 460 denotes a cooling air passage, and reference numeral 461a denotes a cool storage material side air passage.

  Since the cold storage material 50 is filled in the cold storage material container 47 after the refrigerant pipe 45 and the convex portion 47a1 of the cold storage material container 47 are brazed, the cold storage material 50 does not leak to the outside from the perforated portion 47a3.

  Contact when the outer surface of the regenerator container 47 is in full contact with the surface of the refrigerant pipe 45 adjacent to the outer surface without the irregular shape (the concave portion 47a2 and the convex portion 47a1) or the perforated portion 47a3. Assuming that the area is 100%, and if the contact area, that is, the brazing area when the concavo-convex shape or the perforated portion 47a3 is partially contacted as described above, that is, the brazing area is 10% or more (preferably 20% or more), It has been confirmed in the first embodiment and the second embodiment that the heat exchange capability of the apparatus evaporator can be sufficiently secured as will be described later.

  FIG. 11 is a characteristic diagram showing the relationship between the brazing area ratio of the cool storage material container 47 and the refrigerant pipe 45 and the capacity ratio of the evaporator. When the outer surface of the cold storage material container 47 is in full contact with the surface of the refrigerant pipe 45 adjacent to the outer surface without the uneven shape or the perforated part 47a3, the brazing area ratio is 100%. The capacity ratio of the evaporator is 100%. As can be seen from FIG. 11, even if the uneven shape or the perforated portion 47a3 exists, if the brazing area ratio at the time of partial contact is 10% or more, the capacity ratio of the evaporator is 90% or more. Secured.

  In addition, when the perforated portion 47a3 is formed, the brazing material used for the brazing portion of the cold storage material container 47 and the refrigerant pipe 45 is used for the brazing material and the cold storage material container 47 formed on the inner surface of the cold storage material container 47. It is desirable to distinguish it from the brazing material formed on the outer surface. The brazing material is more fluid as the amount of silicon Si contained in the brazing material is larger.

  FIG. 12 is an explanatory diagram schematically illustrating the flow of the brazing material during brazing in the structure of FIG. The flow of the inner surface brazing material formed on the inner surface of the cold storage material container 47 is indicated by an arrow 47IN, and the flow of the outer surface brazing material formed on the outer surface of the cold storage material container 47 is indicated by an arrow 47OUT.

  The brazing material is more fluid as the amount of silicon Si contained in the brazing material is larger. It is preferable for brazing that the flowability of the inner surface brazing material is superior to that of the outer surface brazing material. The reason for this will be described below.

  The outer surface brazing material includes a sacrificial anticorrosive material, and the outer surface brazing material does not flow so much into the brazing portions of the cold storage material container 47 and the refrigerant pipe 45. It is preferable for securing and improving the corrosion resistance of the brazed portion of the cold storage material container 47 and the refrigerant pipe 45. Therefore, the flow of the brazing material indicated by the arrow 47IN is increased by increasing the silicon Si amount of the inner surface brazing material to improve the fluidity.

  Thus, since it brazes with the flow of the inner surface brazing material from the inside and the flow of the outer surface brazing material from the outside, it becomes a structure in which the joining property of the cold storage material container 47 is kept good.

(Modification of the above embodiment)
The present invention is not limited to the above-described embodiments, and can be modified or expanded as follows. For example, in the first embodiment described above, the staggered concavo-convex shape is formed on the surface of the cold storage material container 47, but the lattice shape concavo-convex shape as shown in FIG. . Further, an oblique arrangement as shown in FIG. 14, a circular staggered arrangement as shown in FIG. 15, and a circular lattice arrangement as shown in FIG.

(Third embodiment)
17 is a partially enlarged view of the third embodiment showing the relationship between the refrigerant pipe, the cold storage material container, and the air-side fins schematically showing a part of the cross section along the line VV in FIG. It is sectional drawing. In the third embodiment, the outer surface bonding ratio or the inner surface bonding ratio is set within a predetermined range.

  In FIG. 17, 460 is a cooling air passage, and 461a is a cool storage material side air passage. When forming the uneven rib on the surface of the regenerator material container 47, the area ratio of the outer surface of the regenerator material container 47 forming the convex portion 47a1 (the portion indicated by the phantom line of the two-dot chain line in FIG. 17) is X%. When the area ratio of the inner surface of the cold storage material container 47 that forms the recess (the portion of the cold storage material container 47 in contact with the inner fin 47f side) is Y%, X + Y is 100%.

  Then, as shown in FIG. 17, inner fins 47 f having a uniform width are provided in the cold storage material container 47, and the inner fins 47 f may or may not contact the surface of the cold storage material container 47 due to the uneven shape. There is a part. When X of the imaginary line portion is large (Y is small), the ratio that the contact area between the surface of the cold storage material container 47 and the inner fin 47f cannot be secured becomes large, and as a heat exchanger (in this case, an evaporator) The performance of is reduced.

  On the other hand, when X is small (Y is large), a sufficient contact area between the cold storage material container 47 and the refrigerant pipe 45 (45a, 45b) cannot be secured, and the amount of the cold storage material 50 and the brazing material can be reduced. However, the performance as a heat exchanger decreases.

  Further, the inner fin 47f has a wavy bent portion, and the top portion of the wave of the bent portion partially contacts the inner surface of the cold storage material container 47, and the wave height of the bent portion (left and right in FIG. 17). The width in the direction is uniform. Thus, if the wave heights of the bent portions of the inner fin 47f are made uniform, the inner fin 47f can be easily manufactured and assembled.

  FIG. 18 illustrates performance degradation due to the joining ratio of the heat exchange inner fin 47f and the cool storage material container 47 described above. Part (a) of FIG. 18 is a case where the outer surface bonding ratio X is reasonably small, and part (b) of FIG. 18 is a case where the outer surface bonding ratio X is too large.

  18A shows a case where the heat transfer distance from the refrigerant pipes 45a and 45b to the inner fin 47f and the cold storage material 50 is short and the amount of heat transfer is large. In the case of FIG. The case where the heat transfer distance from the refrigerant pipes 45a and 45b to the inner fin 47f and the cold storage material 50 is long and the heat transfer amount is small is shown.

  Thus, by providing unevenness, the inner fin 47f and the cool storage material container 47 do not contact each other, and naturally, the inner fin 47f and the cool storage material container 47 are not brazed, so that the performance as a heat exchanger is uneven. Affected by the dimensions of

  Moreover, FIG. 19 explains the performance by the magnitude | size of the joining ratio of the said inner side fin 47f and the cool storage material container 47, (a) part of FIG. 19 is the cool-down time after fully storing cold, It is the graph which showed the relationship with a joining ratio. The part (b) of FIG. 19 is a graph showing the relationship between the cool storage time (seconds) and the joining ratio. The part (c) of FIG. 19 is a graph showing the relationship between the cooling time (seconds) and the joining ratio when the cool storage is not completed completely and the cool storage is performed for a limited time.

  18 and 19, when the joining ratio X is large, the internal volume of the cold storage material 50 adjacent to the joined portion increases. Therefore, if the state of sufficient cool storage is achieved, the cool-down time increases approximately proportionally as the joining ratio X increases, as shown in the graph in part (a) of FIG.

  When the time for solidifying the entire cold storage material 50 is defined as the cold storage time, when the joining ratio X is large as shown in FIG. 18 (b), the heat transfer path is as shown in FIG. b) It becomes long like a part and the efficiency of the air side fin 46 (46a and 46b) falls.

  Therefore, as shown in the graph in part (b) of FIG. 19, when the joining ratio X is large, the cool storage time becomes considerably long. In addition, since the coolable time has a correlation with the driving time of the automobile and is a limited time, it is necessary to efficiently use the mounted cool storage material 50 and store it completely. In the graph in FIG. 19B, the limited time is indicated by TL.

  The cool-down time when the cool is stored within the limited time TL is as shown in the graph of part (c) of FIG. 19, and the cool-down time is maximized at a junction rate of around 50%. Therefore, considering from these graphs, in order to store the cold within a limited time and secure the cooling time with a small amount of the cold storage material 50, the joining ratio X is preferably 50% or less.

  Note that the ratio X of the contact area when the outer surface of the refrigerant pipe 45 to which the cool storage material container 47 is joined is partially set to the outer surface (X + Y portion) of the cool storage material container 47 is 20% or more and 50%. If it is less, it is more preferable. According to this, the decrease in the heat exchange performance as the cold storage heat exchanger can be more reliably made within 1% while reducing the contact area ratio X.

  And by limiting the joining ratio and securing a sufficient amount of heat transfer in this way, the amount of heat is accumulated in the regenerator material 50 within the limited necessary time, and it is allowed to cool for a sufficiently long time using the accumulated amount of heat. Therefore, the red light at the intersection increases the effect of assisting the air conditioning in the passenger compartment when the engine is stopped.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described. In the above-described embodiment, a plurality of convex portions 47a1 or a plurality of concave portions 47a2 are formed in the cold storage material container 47, and the shapes thereof are shown in FIGS. 6, 7, 8, 9, 13, 14, 15, 15. Although set as shown in FIG. 16, in the fourth embodiment, a rib composed of a plurality of convex portions 47 a 1 is formed in an inverted V shape (inclined shape).

  FIG. 20 shows the shape of the rib on the surface of the cold storage material container 47 of the fourth embodiment of the present invention, and is assembled to the vehicle so that the lower side in FIG. The plurality of convex portions 47a1 or the plurality of concave portions 47a2 on the surface of the regenerator container 47 are formed in a shape in which inclined portions where the condensed water flows separately on the left and right sides of the mountain top portion are formed on both sides. Yes.

  Thus, since the convex part 47a1 or the concave part 47a2 is formed in an inclined shape, the generated condensed water is quickly divided into right and left along the inclined part and discharged to the outside, so that the condensed water is frozen. Thus, the freezing crack that the volume expands and the refrigerant pipe 45 and the cold storage material container 47 are destroyed can be avoided.

  Further, even if condensed water remains and freezes, frozen ice escapes along the inclined portion, so that freezing cracks can be suppressed. Moreover, since it flows in an inclined part divided into right and left, the length of each inclined part can be shortened, and the discharge performance of condensed water improves.

  Specifically, the convex portion 47a1 or the concave portion 47a2 has a protruding height of the inclined rib of 0.2 mm or more, and is an interval between the plural convex portions 47a1 or an interval between the plural concave portions 47a2. The pitch of the ribs is set to 3 mm or more. In addition, a plurality of ribs are arranged such that three or more ribs are stacked from the top of the cold storage material container 47 toward the ground.

  When the cool storage material container 47 air-conditions the passenger compartment air, the cool storage material side between the coolant pipe 45 integrated with the cooling fins 46 in the cooling air passage 460 (FIG. 17 and the like) and the cool storage material container 47. When condensed water stagnates in the air passage 461a and freezing (frost) occurs at a low load, the cold storage heat exchanger 47 and the refrigerant pipe 45 may be destroyed.

  For this reason, in the fourth embodiment, the rib formed of the inverted V-shaped convex portion 47a1 that can reduce the amount of condensed water stagnating in the space between the refrigerant tube 45 and the cold storage heat exchanger 47 is used as the refrigerant tube. It arrange | positions in the space between 45 and the cool storage heat exchanger 47. FIG.

  Thereby, it is possible to prevent the condensed water on the upper side (vertical direction) of the cold storage heat exchanger 47 from flowing into the inverted V-shaped rib on the lower side of the cold storage heat exchanger 47. As a result, the amount of condensed water stagnating between the refrigerant pipe 45 and the cold storage heat exchanger 47 can be reduced. Furthermore, when freezing occurs, the generated ice can escape from the space between the refrigerant pipe 45 and the cold storage heat exchanger 47 in the direction of the external space (the front and back direction in FIG. 17).

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described. FIG. 21 shows the shape of the rib on the surface of the cold storage material container 47 of the fifth embodiment of the present invention, and is assembled to the vehicle so that the lower side in FIG. In the above-described fourth embodiment, the ribs are arranged at an equal pitch so as to overlap the cold storage material container 47 from the top to the ground. However, in the fifth embodiment, as shown in FIG. Ribs are arranged.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described. FIG. 22 is a partial side view showing the rib shape on the surface of the cool storage material container 47 in the evaporator according to the sixth embodiment of the present invention. In the above-described fourth and fifth embodiments, the ribs are arranged in a continuous inclined shape so as to overlap from the top direction to the ground direction of the cold storage material container 47, but this sixth embodiment is as shown in FIG. In addition, the shape of the rib is obtained by dividing the center of the inclined shape by a recess.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described. FIG. 23 is a partial side view showing the shape of the ribs on the surface of the cool storage material container 47 in the evaporator according to the seventh embodiment of the present invention. In the above-described sixth embodiment, the divided inclined ribs are arranged at a continuous equal pitch, and are arranged so as to overlap from the top of the cold storage material container 47 to the ground. As shown in FIG. 23, ribs divided at the center of the inclined shape are arranged at unequal pitches.

  The inverted V-shaped or inclined ribs shown in FIGS. 20 to 23 are arranged such that a plurality of convex portions 47a1 or a plurality of concave portions 47a2 are overlapped. An inclined portion where the condensed water flows separately from the left and right sides of the mountain top portion extends to both ends 47 t of the outer surface of the cold storage material container 47.

  According to this, since most of the generated condensed water is discharged to the outside from both ends 47t of the outer surface of the cold storage material container 47, it is difficult for the condensed water to accumulate in the lower part of the cold storage material container 47. The freezing crack that 45 and the cool storage material container 47 destroy can be avoided.

  In addition, in the plurality of convex portions 47a1 or the plurality of concave portions 47a2, the inclined portions where the condensed water flows separately from the left and right at the top of the mountain extend to both ends 47t of the outer surface of the cold storage material container 47. The crossing angle θ (FIG. 20) between the straight line connecting the ends 47t with the shortest distance and the inclined convex portion 47a1 or concave portion 47a2 is set in the range of 30 to 60 degrees. Thereby, even if the vehicle is inclined on a slope, sufficient condensed water discharge performance can be obtained.

  Further, 80% or more of the facing portions of the plurality of convex portions 47a1 and the refrigerant pipe 45 are in close contact with each other by brazing. Accordingly, the condensed water is reliably discharged to the outside of the cold storage material container 47 along the inclination of the convex portion 47a1.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described. In the above-described embodiment, as shown in FIGS. 2 and 3 in particular, a tank called headers 41, 42, 43, 44 and a plurality of refrigerant pipes 45 other than the header connecting the headers are configured. Has been.

  Each refrigerant pipe 45 communicates with the corresponding header 41, 42, 43, 44 at its end. The refrigerant tube 45 is a multi-hole flat tube formed by an extrusion method having a plurality of refrigerant passages on the inner side. Incidentally, Japanese Patent Application Laid-Open No. 2004-3787 discloses that a multi-hole flat tube extruded by an extrusion method is passed through a pressure roller to form uneven ribs on the surface.

  On the other hand, in the eighth embodiment, the tank portion and the refrigerant pipe are integrally formed by overlapping a pair of plates, and a large number of these plates are stacked to form a heat exchanger. Such a laminated heat exchanger is known in Japanese Patent Application Laid-Open No. 2001-221535.

  On the surface of the cup-shaped tube (also referred to as a drone cup tube) formed in such a manner as above, a concave-convex rib composed of a convex portion 47a1 and a concave portion 47a2 is formed on the surface through the pressure roller. This is disclosed in the same Japanese Patent Application Laid-Open No. 2004-3787.

FIG. 24 is a front view of the evaporator with a cold storage material in the eighth embodiment formed by the laminated plate. FIG. 25 is a left side view of the evaporator with the cold storage material of FIG. As shown in FIGS. 24 and 25, the tank portion of the evaporator and the refrigerant pipe are integrally formed by overlapping a pair of plates, and a large number of these plates are stacked, and the regenerator container 47 is sandwiched between the stacked portions. ing. 24 and 25, the unevenness on the surface of the cold storage material container 47 or the refrigerant pipe 45 is not shown. 24 and 25, the same reference numerals are given to the portions corresponding to FIG.

  FIG. 26 is a schematic cross-sectional view showing an evaporator according to the eighth embodiment in which the refrigerant pipe 45 is manufactured using a Delon cup tube and an evaporator manufactured by an extrusion method. A portion (a) of FIG. 26 is the eighth embodiment, and the refrigerant pipe 45 is manufactured by the tube of the drone cup.

  In part (a) of FIG. 26, an air-side fin 46 installed in the cooling air passage 460 is provided at the left end, and a refrigerant composed of a drone cup in which a refrigerant pipe fin 45f is interposed inside one side of the air-side fin 46. A pipe 45 is provided, and a regenerator container 47 having an uneven rib formed on the surface is joined to the surface of the refrigerant pipe 45 opposite to the air-side fins 46.

  And the set of these air side fins 46, the refrigerant | coolant pipe | tube 45, and the cool storage material container 47 comprises one unit, and many of these units are piled up and the evaporator is comprised. In addition, the air side fin 46 may be joined to the right side of the cool storage material container 47 shown in the (a) part of FIG. 26, and the units may be arranged on the right side, or the inner fin is stored on the right side of the cool storage material container 47. The units may be arranged by joining the refrigerant pipes 45.

  The part (b) of FIG. 26 is in proportion to the modification of the first embodiment in which the refrigerant pipe 45 is formed by the extrusion method as in the first embodiment, and is the same as the first embodiment of FIG. The difference is that the inner fin 47 f is not provided in the cold storage material container 47. FIG. 26 clearly shows the correspondence between the evaporator formed by the extrusion manufacturing method and the evaporator formed by the so-called drone cup manufacturing method in which plates are stacked.

(Ninth embodiment)
Next, a ninth embodiment of the present invention will be described. FIG. 27 is a schematic cross-sectional view showing an evaporator in which a refrigerant pipe is manufactured using a tube of a Delon cup according to a ninth embodiment of the present invention, in contrast to an evaporator manufactured by an extrusion manufacturing method.

  The (a) part of FIG. 27 is the ninth embodiment, and the refrigerant pipe 45 is manufactured by the tube of the drone cup. In FIG. 27, an air side fin 46 installed in the cooling air passage 460 is provided at the left end, and a refrigerant pipe 45 made of a drone cup with a refrigerant pipe fin 45f interposed inside is provided on one side of the air side fin 46. ing.

  And the unevenness | corrugation which consists of the convex part 45a1 and the recessed part 45a2 which comprise the rib of the surface of this refrigerant | coolant pipe | tube 45 is formed. A cold storage container 47 having no irregularities is joined to the surface of the refrigerant pipe 45 opposite to the air-side fins 46. Moreover, the cool storage material side air passage 461a is formed in the recessed part 45a2.

  And the set of these air side fins 46, the refrigerant | coolant pipe | tube 45, and the cool storage material container 47 comprises one unit, and many of these units are piled up and the evaporator is comprised. In addition, the air side fin 46 may be joined to the right side of the cool storage material container 47 shown in the (a) part of FIG. 27, and the units may be arranged on the right side, and the inner fin 47 f is stored on the right side of the cool storage material container 47. The refrigerant pipes 45 may be joined to arrange the units.

  27 (b) is a comparative example that can be referred to as a modified example of the first embodiment in which the refrigerant pipe 45 is formed by the extrusion manufacturing method as in the first embodiment of FIG. The difference is that the surface of the cool storage material container 47 has no irregularities, the ribs of the convex portions 45a1 and the recesses 45a2 are formed on the surface of the refrigerant tube 45, and the inner fin 47f is provided in the cool storage material container 47. This is not done. FIG. 27 clearly shows the correspondence between the evaporator formed by the extrusion manufacturing method and the evaporator formed by the so-called drone cup manufacturing method in which plates are stacked.

(10th Embodiment)
Next, a tenth embodiment of the present invention will be described. FIG. 28 is a schematic cross-sectional view of an evaporator illustrated in the same manner as FIG. 4 of the first embodiment, regarding the tenth embodiment of the present invention. FIG. 29 is a schematic cross-sectional view showing, on an enlarged scale, the arrow Z33 portion of FIG.

  FIG. 30 is a schematic cross-sectional view showing, on an enlarged scale, the arrow Z34 portion of FIG. FIG. 31 is a graph for explaining a state in which the temperature of the evaporator (evaporator) changes with the intermittent operation of the clutch coupled to the compressor (compressor) in the tenth embodiment. FIG. 32 is a side view showing a state in which the ribs on the surface of the regenerator container 47 of the evaporator of FIG. 28 are formed in an inverted V shape.

  In FIG. 28, the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages on the inner side. On both sides of the left and right refrigerant tubes 45a and 45b, there are provided a cooling air passage 460 for exchanging heat with air and a cold storage material container 47 in which inner fins 47f are stored.

  The part where the refrigerant pipe 45 and the cold storage material container 47 are in contact is joined by a brazing material 33r as shown in FIG. If the void 33v is present in the brazing material 33r, the condensed water 33v1 in the void may accumulate.

  Further, as shown in FIG. 30, there is a space 34v in the cool storage material side air passage 461a in which the recess 47a2 is formed on the surface of the cool storage material container 47 in FIG. 28, and this space 34v is not shown in the evaporator. When conditioned air is ventilated by the fan, air flows, moisture in the air is condensed in the space 34v, and condensed water 34v1 is likely to accumulate. The space 34v forms a cool storage material side air passage 461a when the cool storage material container 47 is allowed to cool.

  As shown in FIG. 31, the temperature of the evaporator (evaporator) is repeatedly changed according to the engagement of the clutch corresponding to the compressor 10 in FIG. 1, and the condensed water is repeatedly frozen and melted. In order to prevent the freezing crack at this time, the width W of the joining plane part of FIG. 29 is set to 0.8 mm or less.

  Further, the condensed water 34v1 accumulated in the space 34v in FIG. 30 in which the concave portion 47a2 is formed on the surface of the cold storage material container 47 is seen from the direction of the arrow Z36 in FIG. 30 in the rib composed of the convex portion 47a1 adjacent to the concave portion 47a2. 32, the condensed water 34v1 in the space 34v is discharged to the outside of the cold storage material container 47 as indicated by an arrow Y36.

  Moreover, the width dimension of the recessed part 47a2 between convex parts 47a1 is set so that condensed water may not be sucked up from the bottom by the clearance gap between convex parts 47a1 like arrow Y361. As a result, even if the condensed water becomes ice, the ice slides down the surface of the cold storage material container 47 on the recess 47a2, is discharged to the outside, and does not generate stress that causes freeze cracking.

  As described above, in the cold storage heat exchanger 47 in which the cold storage material container 47 of FIG. 28 is integrated with the cooling fins 46a and 46b in the cooling air passage 460 for air-conditioning the passenger compartment air, the refrigerant pipe 45 and the cold storage material container When the condensate stagnates in the regenerator-side air passage 461a between 47 and freezing (frost) occurs at a low load, the regenerator heat exchanger 47 and the refrigerant pipe 45 try to break down, according to the tenth embodiment. For example, an inverted V-shaped rib capable of reducing the amount of condensed water stagnating in the space between the refrigerant pipe 45 and the cold storage heat exchanger 47 is disposed in the space between the refrigerant pipe 45 and the cold storage heat exchanger 47 in FIG. doing.

  Thereby, it is possible to suppress the condensed water on the upper side (upward direction) of the cold storage heat exchanger 47 from flowing from the upper side of the cold storage heat exchanger 47 into the lower inverted V-shaped rib. As a result, the amount of condensed water stagnating between the refrigerant pipe 45 and the cold storage heat exchanger 47 can be reduced. Further, when freezing occurs, the generated ice can escape from the space between the refrigerant pipe 45 and the cold storage heat exchanger 47 to the external space.

1 Refrigerating cycle equipment 40 Evaporator (evaporator)
45 (45a and 45b) Refrigerant tube 45c Refrigerant passage of refrigerant tube 46 (46a and 46b) Air side fin 47 Cold storage material container 47a Outer shell of cold storage material container 47a1, 45a1 Convex part 47a2, 45a2 Concave part 47a3 Perforated part 47f Inner fin 50 Cool storage material 460 Cooling air passage 461a Cool storage material side air passage

Claims (2)

A plurality of refrigerant pipes (45) having a refrigerant passage and spaced from each other, and a cold storage material container that is sandwiched and joined between the refrigerant pipes and divides a room for storing the cold storage material (50) (47)
Inside the cold storage material container (47), an inner fin (47f) is arranged,
In the recess (47a2) formed in the cold storage material container (47) and not joined to the refrigerant pipe, a member for stopping the inner fin (47f) is formed,
The inner fin (47f) is arranged below a member for stopping the inner fin (47f),
A cold storage heat exchanger, wherein air is sealed in a portion inside the cold storage material container (47) and above a member that stops the inner fin (47f). The regenerative heat exchange according to claim 1, wherein the member that stops the inner fin (47f) is a launching portion (47g) that stops the inner fin (47f) inside the regenerator container (47). vessel.

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