JP2022039474A - Regenerative heat exchanger - Google Patents

Abstract

To prolong a cooling time.SOLUTION: On the surface of a first plate member 471 facing an adjacent tube 45, and the surface of a second plate member 472 facing the other adjacent tube 45, an annular protrusion 47a is formed so as to protrude toward the tube 45 side. Between the first plate member 471 and the second plate member 472 on which the protrusion 47a is formed and the facing tubes 45, a gap space GS is formed. On the inner peripheral side of the protrusion 47a, a through hole 473 that communicates between a storage space of a cold storage material container 47 and the gap space GS is formed. Then, the storage space of the cold storage material container 47 is filled with a cold storage material 50, and at least gas having a thermal conductivity lower than that of the cold storage material 50 is sealed in the gap space GS.SELECTED DRAWING: Figure 4

Description

The present invention relates to a cold storage heat exchanger.

Conventionally, there is a cold storage heat exchanger described in Patent Document 1. The heat exchanger comprises a plurality of spaced refrigerant pipes and a cold storage container having a first side plate facing one refrigerant pipe and a second side plate facing the other refrigerant pipe. There is. Further, the second side plate has a recess in which the outer surface is formed in a concave shape along the extending direction of the refrigerant pipe, a joint portion joined to the other refrigerant pipe over the entire circumference of the outer peripheral side of the recess, and a recess. A communication hole that communicates the inside and the outside of the cold storage material container is formed.

Japanese Unexamined Patent Publication No. 2017-90015

The material described in Patent Document 1 is a cold storage material having high thermal conductivity not only in the inside of the cold storage material container but also in the space formed between the recess formed in the second side plate and the other refrigerant pipe. Is satisfied. Therefore, the heat exchange efficiency between the refrigerant flowing through the refrigerant pipe and the cold storage material is improved, but the thermal resistance of the cold storage heat exchanger is lowered and the latent heat of the cold storage material is released quickly. Therefore, for example, there is a problem that the cooling time at the time of idling stop in which the engine of the vehicle is temporarily stopped is shortened.

The present invention has been made in view of the above points, and an object thereof is to lengthen the cooling time.

In order to achieve the above object, the invention according to claim 1 forms a plurality of refrigerant pipes (45) having a refrigerant flow path through which a refrigerant flows, a storage space filled with a cold storage material, and a plurality of refrigerant pipes. It is provided with a cold storage material container (47) arranged between the two. Further, the cold storage material container has a first plate member (471) facing one adjacent refrigerant pipe and a second plate member (472) facing the other adjacent refrigerant pipe. Further, at least one of the surface of the first plate member facing the adjacent refrigerant pipe and the surface of the second plate member facing the other adjacent refrigerant pipe protrudes toward the facing refrigerant pipe side. An annular convex portion (47a) is formed. Further, the convex portion is joined to the facing refrigerant pipe. Further, a gap space (GS) is formed between at least one of the first plate member and the second plate member on which the convex portion is formed and the refrigerant pipe facing the first plate member. Further, a through hole (473) communicating between the storage space of the cold storage material container and the gap space is formed on the inner peripheral side of at least one of the convex portions of the first plate member and the second plate member. Then, the storage space of the cold storage material container is filled with the cold storage material, and at least a gas having a thermal conductivity lower than that of the cold storage material is sealed in the gap space.

According to such a configuration, at least a gas having a lower thermal conductivity than the cold storage material is enclosed in the gap space, so that the thermal resistance of the cold storage heat exchanger can be increased. Therefore, the cooling time can be made longer than in the case where a gas having a thermal conductivity lower than that of the cold storage material is not enclosed in the gap space at least.

Further, in order to achieve the above object, the invention according to claim 13 forms a plurality of refrigerant pipes (45) having a refrigerant flow path through which a refrigerant flows, and a plurality of accommodation spaces filled with a cold storage material. It is provided with a cold storage material container (47) arranged between the refrigerant pipes. Further, the cold storage material container has a first plate member (471) facing one adjacent refrigerant pipe and a second plate member (472) facing the other adjacent refrigerant pipe. Further, at least one of the surface of the first plate member facing the adjacent refrigerant pipe and the surface of the second plate member facing the other adjacent refrigerant pipe protrudes toward the facing refrigerant pipe side. An annular convex portion (47a) is formed. Further, the convex portion is joined to the facing refrigerant pipe. Further, a gap space (GS) is formed between at least one of the first plate member and the second plate member on which the convex portion is formed and the refrigerant pipe facing the first plate member. Then, the storage space of the cold storage material container is filled with the cold storage material, and at least a gas having a thermal conductivity lower than that of the cold storage material is sealed in the entire gap space.

According to such a configuration, at least a gas having a thermal conductivity lower than that of the cold storage material is enclosed in the entire gap space, so that the thermal resistance of the cold storage heat exchanger can be increased. Therefore, the cooling time can be made longer than in the case where a gas having a thermal conductivity lower than that of the cold storage material is not enclosed in the gap space at least.

The reference numerals in parentheses attached to each component or the like indicate an example of the correspondence between the component or the like and the specific component or the like described in the embodiment described later.

It is a block diagram of the refrigerating cycle apparatus including the cold storage heat exchanger of 1st Embodiment. It is a front view of the cold storage heat exchanger of 1st Embodiment. FIG. 3 is a view taken along the arrow III in FIG. 2, and is a side view of the cold storage heat exchanger of the first embodiment. FIG. 5 is a sectional view taken along line IV-IV in FIG. It is a V arrow view in FIG. It is a figure showing the inner fin of the cold storage heat exchanger of 1st Embodiment. It is a figure for demonstrating the force acting on the boundary between the cold storage material formed in the through hole and the air of a gap space. It is an enlarged view of part VIII in FIG. It is a figure which showed the relationship between the hole diameter of a through hole and the force by surface tension in the material which has a different contact angle. It is a figure showing the shape of the cold storage heat exchanger of the 2nd Embodiment, and is the figure corresponding to FIG. It is a figure showing the shape of the cold storage heat exchanger of the 2nd Embodiment, and is the figure corresponding to FIG. It is a figure showing the model at the time of calculating the flow rate corresponding to the encapsulation speed. It is a figure which showed the relationship between the hole diameter of a through hole and the flow rate corresponding to the encapsulation speed. It is a figure showing the shape of the cold storage heat exchanger of the 3rd Embodiment, and is the figure corresponding to FIG. It is a figure showing the shape of the cold storage heat exchanger of 4th Embodiment, and is the figure corresponding to FIG. It does not show the change in the outlet air temperature of the rear face outlet and the front face outlet of the air conditioning unit after the compressor is turned off. It is a schematic sectional drawing of the air-conditioning unit which has a rear face outlet and a front face outlet. It is a figure showing the shape of the cold storage heat exchanger of 5th Embodiment, and is the figure corresponding to FIG. It is a figure which showed the modification of the cold storage heat exchanger.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the following embodiments, the same or equal parts are designated by the same reference numerals, and the description thereof will be omitted.

(First Embodiment)
FIG. 1 shows a configuration of a refrigeration cycle apparatus provided with a cold storage heat exchanger according to the first embodiment. This refrigeration cycle device constitutes a vehicle air conditioner. The refrigeration cycle device 1 includes a compressor 10, a radiator 20, a decompressor 30, and a cold storage heat exchanger 40 as an evaporator. These components are connected in a ring shape by piping to form a refrigerant circulation path.

The compressor 10 is driven by an internal combustion engine, which is a power source 2 for traveling the vehicle. When the power source 2 is stopped, the compressor 10 is also stopped. The compressor 10 sucks the refrigerant from the cold storage heat exchanger 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 cold storage heat exchanger 40 evaporates the refrigerant decompressed by the decompressor 30 to cool the vehicle interior air.

In FIGS. 2 and 3, the cold storage heat exchanger 40 has a first heat exchange unit 48 and a second heat exchange unit 49 arranged in two layers. The second heat exchange unit 49 is arranged on the upstream side of the air flow, and the first heat exchange unit 48 is arranged on the downstream side of the air flow.

Specifically, the cold storage heat exchanger 40 has a plurality of branched refrigerant passage members. This refrigerant passage member is provided by a metal passage member such as aluminum. The refrigerant passage member is provided by the first to fourth headers 41 to 44 positioned in a set and a plurality of tubes 45 connecting between the headers 41 to 44. The tube 45 corresponds to a refrigerant pipe.

The first header 41 and the second header 42 form a set, and are arranged in parallel with each other at a predetermined distance. The third header 43 and the fourth header 44 are also paired, and are arranged in parallel with each other at a predetermined distance. A plurality of tubes 45 are arranged at equal intervals between the first header 41 and the second header 42. Each tube 45 communicates with the corresponding headers 41, 42 at its ends. The first heat exchange section 48 is formed by the first header 41, the second header 42, and a plurality of tubes 45 arranged between them.

A plurality of tubes 45 are arranged at equal intervals between the third header 43 and the fourth header 44. Each tube 45 communicates with the corresponding headers 43, 44 at its ends. The second heat exchange section 49 is formed by the third header 43, the fourth header 44, and a plurality of tubes 45 arranged between them.

A joint (not shown) as a refrigerant inlet is provided at the end of the first header 41. The inside of the first header 41 is divided into a first section and a second section by a partition plate (not shown) provided at substantially the center in the length direction thereof. Correspondingly, the plurality of 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 compartment to a plurality of tubes 45 belonging to the first group. The refrigerant flows into the second header 42 through the first group and is aggregated. The refrigerant is redistributed from the second header 42 to the plurality of tubes 45 belonging to the second group. The refrigerant flows into the second section of the first header 41 through the second group. In this way, in the first heat exchange section 48, a flow path for flowing the refrigerant in a U shape is formed.

A joint (not shown) as a refrigerant outlet is provided at the end of the third header 43. The inside of the third header 43 is divided into a first section and a second section by a partition plate (not shown) provided at substantially the center in the length direction thereof. Correspondingly, the plurality of 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 communicate with each other.

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 compartment to a plurality of tubes 45 belonging to the first group. The refrigerant flows into the fourth header 44 through the first group and is aggregated. The refrigerant is redistributed from the fourth header 44 to the plurality of tubes 45 belonging to the second group. The refrigerant flows into the second section of the third header 43 through the second group. In this way, also in the second heat exchange section 49, a flow path for flowing the refrigerant 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 tubes 45 are arranged at substantially constant intervals. A plurality of gaps are formed between the plurality of tubes 45. A plurality of air-side fins 46 and a plurality of cold storage material containers 47 are brazed to the plurality of gaps. The plurality of air-side fins 46 and the plurality of cold storage material containers 47 are arranged, for example, with predetermined regularity. A part of the gap is a cooling air passage 460. The remaining part of the gap is a storage portion in which the cold storage material container 47 is arranged.

The cold storage material container 47 accommodates, for example, a cold storage material 50 composed of paraffins, and is arranged so as to be substantially evenly dispersed throughout the cold storage heat exchanger 40. The cold storage material 50 is filled inside the cold storage material container 47 from the direction of arrow A in FIG. Two tubes 45 located on both sides of the cold storage material container 47 partition a cooling air passage 460 for heat exchange with air. Air flows in the direction of arrow AR shown in FIG.

The tube 45 is formed in a flat shape, and is configured as an inner fin tube in which an inner fin 450 is arranged in an internal refrigerant passage. Since the so-called extruded tube constructed by the extrusion method is sprayed with zinc, zinc is likely to be concentrated at the joint between the tube and the case, and corrosion is likely to leak. In the cold storage material container 47 of the present embodiment, the tube 45 is configured as an inner fin tube, and the corrosion resistance is improved as compared with the extruded tube. The refrigerant passage of the tube 45 extends along the longitudinal direction of the tube 45 and opens at both ends of the tube 45. The plurality of tubes 45 are arranged in a row. In each row, the plurality of tubes 45 are arranged so that their main surfaces (flat surfaces) face each other. A caulking portion is provided on the downstream side of the air flow in the tube 45.

The cold storage heat exchanger 40 is provided with an air-side fin 46 for increasing the contact area with the air supplied to the vehicle interior in the cooling air passage 460. The air-side fins 46 are arranged in an air passage partitioned between two adjacent tubes 45.

The air-side fins 46 are joined to two adjacent tubes 45 by a brazing filler metal. The air-side fin 46 is formed by bending a thin metal plate such as aluminum in a wavy shape, and includes an armor window-shaped louver 461.

The cold storage heat exchanger 40 solidifies the cold storage material to store cold heat when the refrigerant is evaporated in the cold storage heat exchanger 40 to exert an endothermic action, and releases the cold heat stored when the cold storage material melts. It is a cold storage heat exchanger that cools. The cold storage heat exchanger 40 includes a cold storage material container 47 having a storage space for accommodating the cold storage material. As shown in FIG. 4, the cold storage material container 47 is formed in a flat container shape and is arranged between a plurality of tubes 45. The cold storage material container 47 forms a storage space for accommodating the cold storage material 50 inside by joining a pair of plate members 471 and 472 having a substantially U-shaped cross section (bathtub shape).

The cold storage material container 47 includes first and second plate members 471 and 472 having a wide main wall. The first plate member 471 is arranged to face one of the adjacent tubes 45, and the second plate member 472 is arranged to face the other adjacent tube 45.

The main walls of the first and second plate members 471 and 472 are arranged in parallel with the tube 45, respectively. These two main walls have an uneven shape.

A first convex portion 47a, a second convex portion 47b, and a concave portion 47c are provided on the inner surface of the main wall of the first plate member 471. The inner surface of the main wall of the second plate member 472 is also provided with a first convex portion 47a, a second convex portion 47b, and a concave portion 47c.

The first convex portion 47a projects toward the outside of the cold storage material container 47. The first convex portion 47a forms an annular shape.

The second convex portion 47b is arranged on the inner peripheral side of the first convex portion 47a and projects toward the outside of the cold storage material container 47. In the present embodiment, ten second convex portions 47b are arranged on the inner peripheral side of one first convex portion 47a.

The amount of protrusion of the second convex portion 47b is smaller than that of the first convex portion 47a. Further, a through hole 473 penetrating the front and back is formed in the second convex portion 47b. Further, the top of the second convex portion 47b is a rectangular flat surface.

Further, the first convex portion 47a is joined to the opposite tube 45 by a brazing material. The brazing length of the first convex portion 47a joined to the tube 45, that is, the width of the joint portion between the tube 45 and the first convex portion 47a is 0.8 mm or more. As a result, corrosion resistance is ensured.
In the cold storage heat exchanger of the present embodiment, there is a gap space GS between the portion of the first plate member 471 and the second plate member 472 in which the first convex portion 47a forming an annular shape is formed and the tube 45 facing the tube 45. Is formed. That is, a gap space GS is formed between the second convex portion 47b and the tube 45 facing the second convex portion 47b.

Further, a through hole 473 that communicates between the accommodation space of the cold storage material container 47 and the gap space GS is formed on the inner peripheral side of the first convex portion 47a of the first plate member 471 and the second plate member 472. Specifically, a second convex portion 47b protruding toward the facing tube 45 side is formed on the inner peripheral side of the first convex portion 47a, and a through hole 473 is formed in the second convex portion 47b. The shape of the through hole 473 is a square.

Then, the cold storage material 50 is filled in the accommodation space of the cold storage material container 47, and the gap space GS is filled with a gas having a thermal conductivity lower than that of the cold storage material 50. Further, the gas occupies more than half of the volume of the gap space GS, and the cold storage material occupies the remaining volume of the volume of the gap space GS.

The cold storage material container 47 is arranged between two adjacent tubes 45. The cold storage material container 47 is thermally coupled to two tubes 45 arranged on both sides thereof by a first convex portion 47a. The cold storage material container 47 is joined to two adjacent tubes 45 by a joining material having excellent heat transfer. As the bonding material, a resin material such as a brazing material or an adhesive material can be used. The cold storage material container 47 of this example is brazed to the tube 45. More specifically, both the tube 45 constituting the first heat exchange section 48 and the tube 45 constituting the second heat exchange section 49 are joined to the outer surface of the cold storage material container 47.

As shown in FIG. 4, an inner fin 60 is thermally and mechanically coupled to the cold storage material container 47 and arranged on the inner side of the cold storage material container 47. The inner fin 60 is joined to the inner surface of the main wall of the cold storage material container 47 by a joining material having excellent heat transfer. This joining is done by brazing. By connecting the inner fin 60 to the inner side of the cold storage material container 47, deformation of the cold storage material container 47 is prevented and the pressure resistance is improved.

The inner fin 60 has a plurality of flat surface portions 61 perpendicular to the stacking direction of the tubes 45, and a connecting portion 62 that positions adjacent flat surface portions 61 at a predetermined distance. The cross-sectional shape of the inner fin 60 in the flow direction of the air flowing through the cooling air passage 460 is a wave shape. In this example, the inner fin 60 is formed by bending a thin metal plate such as aluminum in a wavy shape.

As shown in FIG. 6, the inner fin 60 of the present embodiment is arranged so as to undulate in a direction intersecting the longitudinal direction of the cold storage material container.

Since the inner surface of the cold storage material container 47 is uneven, the inner fin 60 is joined to the recess 47c of the main wall of the cold storage material container 47, that is, the portion protruding inward (inner surface protrusion) by brazing. , Mechanical strength and pressure resistance are improved. As a result, of the main wall of the cold storage material container 47, the first convex portion 47a protruding outward and the inner fin 60 are not joined.

All the flat surface portions 61 constituting one inner fin 60 are joined to the inner surface of the cold storage material container 47, respectively. Specifically, as shown in FIG. 4, the recess 47c of the main wall of the cold storage material container 47 extends in the flow direction (left-right direction of the paper surface) of the air flowing through the cooling air passage 460, and the recess 47c And the flat surface portion 61 of the inner fin 60 are in surface contact with each other.

In the cold storage heat exchanger of the present embodiment, the tube 45 facing the surface of the first plate member 471 facing the adjacent one tube 45 and the surface of the second plate member 472 facing the adjacent other tube 45. An annular first convex portion 47a protruding toward the side is formed. Further, in the cold storage heat exchanger of the present embodiment, a second convex portion 47b is formed on the inner peripheral side of the first convex portion 47a so as to project toward the facing tube 45 side.

Further, the amount of protrusion of the second convex portion 47b is smaller than that of the first convex portion 47a, and the second convex portion 47b is formed with a through hole 473 for passing the cold storage material.

Therefore, even if burrs are generated inside the cold storage material container 47 from the edge of the through holes 473 when forming the through holes 473 in the plate members 471 and 472 of the cold storage material container 47, the burrs do not come into contact with the inner fin 60. .. Therefore, an unbonded region is not formed between the plate members 471 and 472 and the inner fin 60. Therefore, the heat transfer property can be improved.

Further, in the cold storage heat exchanger of the present embodiment, the second convex portion 47b protruding toward the facing tube 45 side is formed on the inner peripheral side of the first convex portion 47a, so that the heat transfer property is improved. be able to.

Further, in the cold storage heat exchanger of the present embodiment, the first convex portion 47a is joined to the facing tube 45, and the plate members 471 and 472 on which the second convex portion 47b is formed are between the facing tube 45. The gap space GS is formed in.

Then, the cold storage material is filled in the accommodation space of the cold storage material container 47. Further, in the gap space GS between the portion of the first plate member 471 in which the second convex portion 47b is formed and the adjacent tube 45, a gas having a thermal conductivity lower than that of the cold storage material 50 is sealed. There is. Further, a gas having a thermal conductivity lower than that of the cold storage material 50 is also sealed in the gap space GS between the portion of the second plate member 472 where the second convex portion 47b is formed and the other adjacent tube 45. .. In this embodiment, air is sealed in the gap space GS as a gas having a thermal conductivity lower than that of the cold storage material 50.

As described above, in the cold storage heat exchanger of the present embodiment, since the gas having a lower thermal conductivity than the cold storage material 50 is sealed in the gap space GS, it is compared with the case where the cold storage material 50 is sealed in the gap space GS. Then, the thermal resistance of the cold storage heat exchanger becomes large, and the latent heat of the cold storage material 50 is gradually released. Therefore, the cooling time at the time of idling stop when the engine of the vehicle is temporarily stopped is long.

Further, the through hole 473 formed in the first plate member 471 and the second plate member 472 has a side length of less than 4 mm. Specifically, the length of one side of the through hole 473 of the present embodiment is about 2 mm.

Next, the filling of the cold storage material 50 into the cold storage material container 47 will be described. The cold storage material 50 is filled in the cold storage material container 47 after the brazing of the cold storage material container 47, the inner fin 60, the tube 45, and the like is completed.

The cold storage material 50 is filled inside the cold storage material container 47 from the direction of arrow A in FIG. When the cold storage material 50 is injected into the cold storage material container 47, the cold storage material 50 flows into the accommodation space formed between the first plate member 471 and the second plate member 472. At this time, the cold storage material 50 flows into the corrugated gap of the inner fin 60. In this way, the storage space of the cold storage material container 47 is filled with the cold storage material 50 having a predetermined capacity.

If the filling amount of the cold storage material 50 is too large, the cold storage material 50 flows into the gap space GS from the inside of the cold storage material container 47 through the through hole 473. Therefore, the cold storage material 50 is filled in the cold storage material container 47. At that time, the cold storage material 50 having a predetermined capacity is filled in the cold storage material container 47.

Therefore, in the cold storage heat exchanger of the present embodiment, when the cold storage material 50 is filled in the cold storage material container 47, the cold storage material 50 is not filled in the gap space GS, and air is sealed in the gap space GS. ..

In the cold storage heat exchanger of the present embodiment, the diameter of the through hole 473 is sufficiently small. Therefore, the cold storage material 50 is prevented from leaking from the inside of the cold storage material container 47 into the gap space GS through the through hole 473 due to the action of the force due to the surface tension of the cold storage material 50.

Next, the relationship between the force due to the surface tension of the cold storage material 50 and the hole diameter of the through hole 473 will be described with reference to FIGS. 7 to 9. Here, it is assumed that the through hole 473 has a circular shape.

As shown in FIGS. 7 to 8, a boundary between the cold storage material 50 and the air in the gap space GS is formed inside the through hole 473. On the cold storage material 50 side of this boundary, a force P1 + P2 applied by an internal pressure P1 acting on the inside of the cold storage material container 47 and a pressure P2 pushing the cold storage material 50 acting by the weight of the cold storage material 50 acts. Further, on the air side of this boundary, a force P3 + P4 obtained by adding an atmospheric pressure P3 due to the air inside the gap space GS and a force P4 due to the surface tension of the cold storage material 50 acts.

Assuming that the surface tension of the cold storage material 50 is σ, the contact angle is θ, and the diameter of the through hole 473 is D, the force P4 due to the surface tension can be expressed as P4 = (4σcosθ) / D. The surface tension σ of the cold storage material 50 is determined by the material of the cold storage material 50, and the contact angle θ is determined by the material of the cold storage material container 47 and the material of the cold storage material 50.

Here, when P1 + P2 is less than P3 + P4, the cold storage material 50 does not enter the gap space GS through the through hole 473. However, when P1 + P2 is P3 + P4 or more, the cold storage material 50 enters the gap space GS through the through hole 473.

FIG. 9 shows the relationship between the hole diameter of the through hole 473 and the force P4 due to surface tension in the material having contact angles of 1 degree, 30 degrees, and 60 degrees. As shown in the figure, when the contact angle is 1 degree, 30 degrees, or 60, it can be confirmed that the force P4 due to the surface tension increases sharply when the hole diameter of the through hole 473 becomes 4 mm or more. ..

That is, by setting the hole diameter of the through hole 473 to 4 mm or more, the force P4 due to the surface tension can be sufficiently increased, and the cold storage material 50 is prevented from entering the gap space GS through the through hole 473. It is possible.

In summer and the like, the ambient temperature of the cold storage heat exchanger rises to about 80 ° C. As described above, when the ambient temperature of the cold storage heat exchanger rises, the cold storage material 50 expands and the volume of the cold storage material container 47 increases, and the cold storage material container 47 is deformed or damaged. When the ambient temperature of the cold storage heat exchanger 40 rises from 20 ° C to 80 ° C, the volume of the cold storage material 50 increases by about 7%.

As described above, when the ambient temperature of the cold storage material container 47 rises and the cold storage material 50 filled in the cold storage material container 47 expands, the cold storage material 50 is cooled from the inside of the cold storage material container 47 to each gap space GS through the through hole 473. Material 50 leaks.

Then, the cold storage material 50 is collected below each gap space GS, and air is collected above the cold storage material 50 in each gap space GS. In this way, the cold storage material 50 flows into each gap space GS in which air is accumulated through the through hole 473, so that the cold storage material container 47 is prevented from being deformed or damaged due to the expansion of the cold storage material 50.

After that, when the ambient temperature of the cold storage material container 47 drops, the cold storage material 50 above the through hole 473 in the gap space GS is pushed out to the cold storage material container 47 side through the through hole 473 by the air in the gap space GS, and the cold storage material container 47 is cooled. It will return to the material container 47 side. The cold storage material 50 accumulated below the through hole 473 remains in the gap space GS.

(1) The cold storage heat exchanger of the above embodiment forms a storage space filled with a plurality of tubes 45 having a refrigerant flow path through which the refrigerant flows and a cold storage material 50, and is arranged between the plurality of refrigerant pipes. It is provided with a cold storage material container 47. Further, the cold storage material container 47 has a first plate member 471 facing one adjacent tube 45 and a second plate member 472 facing the other adjacent tube 45. Further, at least one of the surface of the first plate member 471 facing the adjacent tube 45 and the surface of the second plate member 472 facing the other adjacent tube 45 toward the facing tube 45 side. A protruding annular first convex portion 47a is formed. Further, the first convex portion 47a is joined to the facing tube 45. Further, a gap space GS is formed between the first plate member 471 and the second plate member 472 on which the first convex portion 47a is formed and the tube 45 facing the first plate member 471. Further, a through hole 473 that communicates between the accommodation space of the cold storage material container 47 and the gap space GS is formed on the inner peripheral side of the first convex portion 47a of the first plate member 471 and the second plate member 472. Then, the cold storage material 50 is filled in the accommodation space of the cold storage material container 47, and at least a gas having a thermal conductivity lower than that of the cold storage material 50 is sealed in the gap space GS.

According to such a configuration, at least a gas having a thermal conductivity lower than that of the cold storage material 50 is enclosed in the gap space GS, so that the thermal resistance of the cold storage heat exchanger can be increased. Therefore, the cooling time can be made longer than in the case where the gap space GS is not filled with at least a gas having a thermal conductivity lower than that of the cold storage material 50.

(2) In the above embodiment, the cold storage material 50 is filled in the accommodation space of the cold storage material container 47, and at least a gas having a thermal conductivity lower than that of the cold storage material 50 is sealed in the entire gap space GS.

According to such a configuration, at least a gas having a thermal conductivity lower than that of the cold storage material is enclosed in the entire gap space GS, so that the thermal resistance of the cold storage heat exchanger can be increased. Therefore, the cooling time can be made longer than in the case where the gap space GS is not filled with at least a gas having a thermal conductivity lower than that of the cold storage material.

(3) In the above embodiment, a second convex portion 47b is formed on the inner peripheral side of the first convex portion 47a so as to project toward the facing tube 45 side. The amount of protrusion of the second convex portion 47b is smaller than that of the first convex portion 47a, and the through hole 473 is formed in the second convex portion 47a. In this way, the through hole 473 can also be formed in the second convex portion 47a.

(4) As in the above embodiment, the gas can be air and the cold storage material 50 can be paraffin.

(5) In the above embodiment, the center of the through hole 473 is arranged at the center of the gap space GS in the vertical direction. As described above, the center of the through hole 473 can be arranged at the center in the vertical direction of the gap space GS or below the center.

(6) In the above embodiment, the gas occupies more than half of the volume of the gap space GS, and the cold storage material occupies the remaining volume of the volume of the gap space GS. In this way, the gas can occupy more than half of the volume of the gap space GS.

(7) In the above embodiment, the volume of the gap space GS is 7% or more of the volume of the storage space of the cold storage material container 47. In the cold storage heat exchanger mounted on a vehicle having a high temperature, the volume of the gap space GS is preferably 7% or more of the volume of the accommodation space of the cold storage material container 47.

(Second Embodiment)
The cold storage heat exchanger according to the second embodiment will be described with reference to FIGS. 10 to 13. The cold storage heat exchanger of the first embodiment has a length of one side of the through hole 473 of about 2 mm, but the cold storage heat exchanger of the present embodiment has a length of one side of the through hole 473 of 8. It is about millimeters. That is, the size of the through hole 473 of the cold storage heat exchanger of the present embodiment is larger than that of the through hole 473 of the cold storage heat exchanger of the first embodiment.

Further, in the cold storage heat exchanger of the present embodiment, in FIG. 10, two gap space GSs are formed on the upper side in the vertical direction and the lower side in the vertical direction, respectively. One through hole 473 is formed in each of the two gap spaces GS on the upper side in the vertical direction, and two through holes 473 are formed in each of the gap space GS on the lower side in the vertical direction. .. The center of each through hole 743 is arranged below the center in the vertical direction of the gap space GS.

Further, in the cold storage heat exchanger of the present embodiment, when the cold storage material 50 is filled in the cold storage material container 47, a part of the cold storage material 50 that has flowed out from the cold storage material container 47 through the through hole 473 to the gap space GS is a gap. It is accumulated in the space GS.

By forming two through holes 473 in the vertical direction like the two gap spaces GS on the lower side in the vertical direction, the space of the gas and the cold storage material 50 can be clearly separated inside the gap space GS. This is because by forming two through holes 473 in the vertical direction, a pressure difference applied to the upper and lower through holes 473 is generated. That is, due to the pressure difference applied to the upper and lower through holes 473, air enters the cold storage material container 47 from the upper through hole 473 in the vertical direction, and the cold storage material 50 invades the gap space GS side from the upper through hole 473 in the vertical direction. To do.

Further, in the cold storage heat exchanger of the present embodiment, the distribution of thermal resistance is different between the upper side in the vertical direction and the lower side in the vertical direction. Specifically, the thermal resistance of the portion where the cold storage material 50 has invaded the gap space GS is higher than that of the portion where the cold storage material 50 has not invaded the gap space GS. As described above, the cold storage heat exchanger of the present embodiment can adjust the distribution of thermal resistance, and the cooling release time can be adjusted to a desired time.

By the way, the cold storage heat exchanger of the present embodiment has a different hole diameter of the through hole 473 as compared with the cold storage heat exchanger of the first embodiment. Therefore, the encapsulation speed when encapsulating the cold storage material 50 in the gap space GS through the through hole 473 is also different. Specifically, the cold storage heat exchanger of the present embodiment has a faster filling speed when the cold storage material 50 is filled in the gap space GS through the through hole 473 than the cold storage heat exchanger of the first embodiment. ..

FIG. 12 shows a model for calculating the flow rate Q corresponding to the encapsulation speed using the formula of the orifice. The pressure of the cold storage material 50 is P1, the pressure of the air in the gap space GS is P2, the density of the cold storage material 50 is ρ, and the flow rate corresponding to the filling speed of the cold storage material 50 sealed in the gap space GS via the through hole 473. Q. Let D be the diameter of the through hole 473. At this time, the flow rate Q corresponding to the encapsulation speed is roughly proportional to the square of the diameter D of the through hole 473. The flow rate Q corresponding to the encapsulation speed is represented as shown in FIG.

Then, when the diameter D of the through hole 473 becomes larger than 1 mm, it can be confirmed that the flow rate Q corresponding to the encapsulation speed suddenly increases. That is, by making the diameter D of the through hole 473 larger than 1 mm, the encapsulation speed v when encapsulating the cold storage material 50 can be increased. That is, the cold storage material 50 can be sealed in the gap space GS in a relatively short time, and the productivity when the cold storage material 50 is sealed in the gap space GS can be improved.

As described above, in the cold storage heat exchanger of the present embodiment, the distribution of thermal resistance is different between the upper side in the vertical direction and the lower side in the vertical direction. Specifically, the thermal resistance of the portion where the cold storage material 50 has invaded the gap space GS is higher than that of the portion where the cold storage material 50 has not invaded the gap space GS. As described above, in the cold storage heat exchanger of the present embodiment, the distribution of thermal resistance can be adjusted, and the cooling release time can be controlled to a desired time.

(1) In the above embodiment, the opening area of the through hole formed on the lower side in the vertical direction of one gap space is equal to or larger than the opening area of the hole having a diameter of 1 mm. According to this, the cold storage material 50 can be sealed in the gap space GS in a relatively short time, and the productivity when the cold storage material 50 is sealed in the gap space GS can be improved.

(2) In the above embodiment, one through hole 473 is formed for one gap space GS, and more than half of one gap space GS in which one through hole 473 is formed becomes a gas. There is.

According to this, one through hole 473 is formed for one gap space GS, and more than half of one gap space GS in which one through hole 473 is formed is a gas, so that air can be introduced. It is possible to prevent the cold storage material container 47 from flowing into the cold storage material container 47 through the through hole 473.

(Third Embodiment)
The cold storage heat exchanger according to the third embodiment will be described with reference to FIG. In the cold storage heat exchanger of the first embodiment, 10 gap space GS is formed in FIG. 5, and one through hole 473 is formed for each gap space GS. On the other hand, in the cold storage heat exchanger of the present embodiment, 10 gap space GS are formed in FIG. 14, and one through hole 473 is formed for each of the five gap space GS among these gap space GS. Has been done.

That is, the cold storage heat exchanger of the present embodiment has a gap space GS in which the through hole 473 is not formed in FIG. In this way, the cold storage heat exchanger can be configured to have a gap space GS in which the through hole 473 is not formed.

Further, since there is a gap space GS in which the through hole 473 is not formed, it is possible to prevent air from flowing into the cold storage material container 47 side inside the gap space GS.

The cold storage heat exchanger of the present embodiment has a through hole on the inner peripheral side of at least one of the first plate member 471 or the second plate member 472 without forming the second convex portion 47b. 473 is formed.

Further, the cold storage heat exchanger of the present embodiment is provided with a plurality of gap space GS in which the through hole 473 is not formed, but is provided with the gap space GS in which the minute through hole 473 is formed. You may do so.

(Fourth Embodiment)
The cold storage heat exchanger according to the fourth embodiment will be described with reference to FIGS. 15 to 17. In FIG. 15, the cold storage heat exchanger of the present embodiment has two gap spaces GS formed on the upper side in the vertical direction and the lower side in the vertical direction, respectively. Then, four through holes 473 having a large hole diameter are formed in each of the two gap spaces GS on the upper side in the vertical direction, and four through holes having a small hole diameter are formed in the gap space GS on the lower side in the vertical direction. 473 are formed one by one.

The hole diameter of the through hole 473 formed in the two gap spaces GS on the upper side in the vertical direction is about 8 mm on a side. Further, the hole diameter of the through hole 473 formed in the gap space GS on the lower side in the vertical direction is about 2 mm on a side.

As a result, the cold storage material 50 easily flows into the gap space GS on the upper side in the vertical direction, and the heat exchange efficiency between the refrigerant flowing through the tube 45 and the cold storage material 50 is improved. Further, it is difficult for the cold storage material 50 to flow into the gap space GS on the lower side in the vertical direction, so that the lower side in the vertical direction of the cold storage heat exchanger has a longer cooling time of the cold storage heat exchanger than the upper side in the vertical direction. It is configured.

As described above, in the cold storage heat exchanger of the present embodiment, the number, arrangement and opening area of the through holes 473 are different between the upper side in the vertical direction and the lower side in the vertical direction, and the upper side in the vertical direction and the lower side in the vertical direction are different. The temperature distribution is different.

FIG. 17 is a diagram showing a schematic cross-sectional configuration of an air conditioning unit in which a cold storage heat exchanger is arranged. The air conditioning unit is provided with a front face outlet that blows temperature-controlled air toward the front seats of the vehicle and a rear face outlet that blows temperature-controlled air toward the rear seats of the vehicle. ..

Inside the air conditioning unit, a cold storage heat exchanger 40 for cooling the air and a heater core 20 for heating the air are arranged. Further, inside the air conditioning unit, a space where air blown from the front face outlet to the outside of the air conditioning unit flows and a space where air blown from the rear face outlet to the outside of the air conditioning unit flow are partitioned. ..

Then, the air in which the warm air from the heater core 20 and the cold air from the cold storage heat exchanger 40 are mixed is blown to the outside of the air conditioning unit from the front face outlet and the rear face outlet.

The front face outlet is arranged at the upper part of the air conditioning unit, and the rear face outlet is arranged at the lower part of the air conditioning unit. Further, there is a demand that the temperature of the air blown from the front face outlet should be lower than the temperature of the air blown from the rear face outlet.

FIG. 16 shows how the temperature of the blown air from the rear face outlet arranged at the bottom of the air conditioning unit changes when the compressor 10 is turned off and the temperature of the blown air from the front face outlet placed at the top of the air conditioning unit. Represents.

The air that has passed through the upper part of the cold storage heat exchanger of the present embodiment is blown from the front face outlet arranged at the upper part of the air conditioning unit. That is, the cold air quickly cooled at the upper part of the cold storage heat exchanger of the present embodiment is blown from the front face outlet.

On the other hand, the air that has passed through the lower part of the cold storage heat exchanger of the present embodiment is blown from the rear face outlet arranged at the lower part of the air conditioning unit. That is, the air slowly cooled at the lower part of the cold storage heat exchanger of the present embodiment is blown from the front face outlet.

(Fifth Embodiment)
The cold storage heat exchanger according to the fifth embodiment will be described with reference to FIG. In FIG. 18, the cold storage heat exchanger of the present embodiment has two gap spaces GS formed on the upper side in the vertical direction and the lower side in the vertical direction, respectively. A through hole 473 having a small hole diameter is formed in each of the two gap spaces GS on the upper side in the vertical direction, and through holes having different hole diameters are formed in the gap space GS on the lower side in the vertical direction. Two 473s are formed. Specifically, the hole diameter of the through hole 473 formed on the upper side of the two gap spaces GS on the lower side in the vertical direction is smaller than the through hole 473 formed on the lower side in the vertical direction of the gap space GS. It has become.

As described above, the hole diameter of the through hole 473 formed on the upper side of the two gap spaces GS on the lower side in the vertical direction is smaller than the through hole 473 formed on the lower side in the vertical direction of the gap space GS. ing.

Therefore, in one gap space GS, the cold storage material 50 can easily pass through the through hole 473 on the lower side in the vertical direction, and air can easily pass through the through hole 473 on the upper side in the vertical direction.

(1) In the above embodiment, a plurality of through holes 473 are formed, and the sizes of the plurality of through holes 473 are different from each other. In this way, the sizes of the plurality of through holes 473 can be made different from each other.

(2) In the above embodiment, the plurality of through holes 473 are arranged in the vertical direction of one gap space GS, and the hole diameter of the through hole 473 formed on the upper side in the vertical direction of one gap space GS is It is smaller than the through hole 473 formed on the lower side in the vertical direction of one gap space GS.

In this way, it can be made smaller than the through hole 473 formed on the lower side in the vertical direction of one gap space GS.

(Other embodiments)
(1) In the first and second embodiments, the through hole 473 is formed in the second convex portion 47b. On the other hand, even if the through hole 473 is formed on the inner peripheral side of at least one of the first convex portions 47a of the first plate member 471 or the second plate member 472 without forming the second convex portion 47b. good.

(2) In each of the above embodiments, a rectangular through hole 473 is formed on the inner peripheral side of at least one of the first convex portions 47a of the first plate member 471 or the second plate member 472. On the other hand, for example, as shown in FIG. 19, a circular through hole 473 may be formed.

The present invention is not limited to the above-described embodiment, and can be appropriately modified within the scope of the claims. Further, the above-mentioned embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential or when they are clearly considered to be essential in principle. stomach. Further, in each of the above embodiments, when numerical values such as the number, numerical values, quantities, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and when it is clearly limited to a specific number in principle. It is not limited to the specific number except when it is done. In addition, in each of the above embodiments, when the material, shape, positional relationship, etc. of the constituent elements, etc. are referred to, except when specifically specified or when the material, shape, positional relationship, etc. are limited to a specific material, shape, positional relationship, etc. in principle. , The material, shape, positional relationship, etc. are not limited.

1 Refrigeration cycle device 40 Cold storage heat exchanger 45 Tube 47 Cold storage material container 47a First convex part 47b Second convex part 47c Recessed 473 Through hole 50 Cold storage material

Claims (16)

A plurality of refrigerant pipes (45) having a refrigerant flow path through which the refrigerant flows,
A storage space filled with the cold storage material is formed, and a cold storage material container (47) arranged between the plurality of the refrigerant pipes is provided.
The cold storage material container has a first plate member (471) facing the one adjacent refrigerant pipe and a second plate member (472) facing the other adjacent refrigerant pipe.
The refrigerant pipe side facing the first plate member and at least one of the adjacent surfaces of the second plate member facing the refrigerant pipe and the other adjacent surface of the second plate member facing the refrigerant pipe. An annular protrusion (47a) projecting toward is formed.
The convex portion is joined to the facing refrigerant pipe, and the convex portion is joined to the facing refrigerant pipe.
A gap space (GS) is formed between at least one of the first plate member and the second plate member on which the convex portion is formed and the facing refrigerant pipe.
A through hole (473) communicating between the storage space of the cold storage material container and the gap space is formed on the inner peripheral side of at least one of the first plate member and the second plate member. Ori,
A cold storage heat exchanger in which the cold storage material is filled in the accommodation space of the cold storage material container, and at least a gas having a thermal conductivity lower than that of the cold storage material is sealed in the gap space. The convex portion is a first convex portion and is
A second convex portion (47b) protruding toward the facing refrigerant pipe side is formed on the inner peripheral side of the first convex portion.
The amount of protrusion of the second convex portion is smaller than that of the first convex portion.
The cold storage heat exchanger according to claim 1, wherein the through hole is formed in the second convex portion. The cold storage heat exchanger according to claim 1 or 2, wherein the gas is air. The cold storage heat exchanger according to any one of claims 1 to 3, wherein the cold storage material is paraffin. The cold storage heat exchanger according to any one of claims 1 to 4, wherein the center of the through hole is arranged below the center in the vertical direction of the gap space. The cold storage heat exchanger according to any one of claims 1 to 5, wherein the gas occupies more than half of the volume of the gap space, and the cold storage material occupies the remaining volume of the volume of the gap space. The cold storage heat exchanger according to any one of claims 1 to 6, wherein the volume of the gap space is 7% or more of the volume of the storage space of the cold storage material container. A plurality of the through holes are formed, and the through holes are formed.
The cold storage heat exchanger according to any one of claims 1 to 7, wherein the sizes of the plurality of through holes are different from each other. The plurality of the through holes are arranged in the vertical direction of one of the gap spaces.
According to claim 8, the hole diameter of the through hole formed on the upper side in the vertical direction of the one gap space is smaller than that of the through hole formed on the lower side in the vertical direction of the one gap space. The cold storage heat exchanger described. The cold storage heat exchanger according to claim 9, wherein the opening area of the through hole formed on the lower side in the vertical direction of the one gap space is equal to or larger than the opening area of the hole having a diameter of 1 mm. Only one through hole is formed for one said gap space, and the through hole is formed.
The cold storage heat exchanger according to any one of claims 1 to 7, wherein more than half of the one gap space in which the one through hole is formed is the gas. The cold storage heat exchanger according to claim 11, wherein the opening area of the through hole is equal to or less than the opening area of a hole having a diameter of 4 mm. A plurality of refrigerant pipes (45) having a refrigerant flow path through which the refrigerant flows,
A storage space filled with the cold storage material is formed, and a cold storage material container (47) arranged between the plurality of the refrigerant pipes is provided.
The cold storage material container has a first plate member (471) facing the one adjacent refrigerant pipe and a second plate member (472) facing the other adjacent refrigerant pipe.
The refrigerant pipe side facing the first plate member and at least one of the adjacent surfaces of the second plate member facing the refrigerant pipe and the other adjacent surface of the second plate member facing the refrigerant pipe. An annular protrusion (47a) projecting toward is formed.
The convex portion is joined to the facing refrigerant pipe, and the convex portion is joined to the facing refrigerant pipe.
A gap space (GS) is formed between at least one of the first plate member and the second plate member on which the convex portion is formed and the facing refrigerant pipe.
A cold storage heat exchanger in which the cold storage material is filled in the accommodation space of the cold storage material container, and a gas having a thermal conductivity lower than that of the cold storage material is sealed in the entire gap space. The convex portion is a first convex portion and is
A second convex portion (47b) protruding toward the facing refrigerant pipe side is formed on the inner peripheral side of the first convex portion.
The amount of protrusion of the second convex portion is smaller than that of the first convex portion.
A through hole (473) communicating between the storage space of the cold storage material container and the gap space is formed on the inner peripheral side of at least one of the first plate member and the second plate member. Ori,
The cold storage heat exchanger according to claim 13, wherein the through hole is formed in the second convex portion. The cold storage heat exchanger according to claim 13 or 14, wherein the gas is air. The cold storage heat exchanger according to any one of claims 13 to 15, wherein the volume of the gap space is 7% or more of the volume of the storage space of the cold storage material container.

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