JP2013104580A - Cold storage heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cold storage heat exchanger which can suppress corrosion of a container in which a cold storage material is enclosed.SOLUTION: The cold storage container 47 is enclosed with the cold storage material 50 together with a desiccant 51. Since the desiccant 51 is enclosed with the cold storage material 50, water content is removed from the cold storage container 47 by the desiccant 51. Thus, corrosion of the cold storage container 47 due to water content can be suppressed.

Description

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

  Conventionally, a refrigeration cycle apparatus is used as an air conditioner. Attempts have been made to provide limited cooling even when the refrigeration cycle apparatus is stopped. For example, in a vehicle air conditioner, a refrigeration cycle apparatus is driven by a traveling engine. For this reason, if the engine stops while the vehicle is temporarily stopped, the refrigeration cycle apparatus stops. In order to improve fuel efficiency, so-called idle stop vehicles that stop the engine while the vehicle is stopped, such as waiting for a signal, are increasing. In such an idle stop vehicle, there is a problem that the refrigeration cycle apparatus stops while the vehicle is stopped (the engine is stopped), thereby impairing the comfort in the passenger compartment. In addition, there is also a problem that if the engine is restarted even when the vehicle is stopped in order to maintain a feeling of air conditioning, improvement in fuel efficiency is hindered.

  Technologies for solving such problems are disclosed in Patent Documents 1 to 5. In Patent Documents 1 to 5, in order to maintain the air conditioning feeling even when the engine is stopped, the indoor heat exchanger has a cold storage function. Thus, cold energy is stored while the vehicle is running, and this cold air is used while the vehicle is stopped.

  Patent Document 1 describes a cool storage container in which a cool storage material is sealed arranged behind an air flow of a conventional evaporator. Further, Patent Documents 2 to 5 describe a configuration in which a small-capacity cold storage container is provided adjacent to a tube constituting a refrigerant flow path of an evaporator, and a cold storage material is enclosed therein.

JP 2009-188518 A JP 2010-91250 A JP 2010-112670 A JP 2010-149814 A JP 2011-12947 A

  If there is moisture in the cool storage container in which the cool storage material is sealed, corrosion may occur due to a chemical reaction between the moisture and the cool storage container.

  Then, this invention is made | formed in view of the above-mentioned problem, and it aims at providing the cool storage heat exchanger which can suppress the corrosion of the container which enclosed the cool storage material.

  The present invention employs the following technical means in order to achieve the aforementioned object.

In the first aspect of the present invention, a plurality of refrigerant pipes (45) having a refrigerant passage (45a) through which the refrigerant flows and arranged at intervals from each other,
A cold storage container for storing the cold storage material (50) therein, and a plurality of cold storage containers (47) disposed between two adjacent refrigerant tubes,
The cool storage container is a cool storage heat exchanger in which a desiccant (51) is enclosed together with a cool storage material.

  According to invention of Claim 1, the desiccant is enclosed with the cool storage material with the cool storage container. Therefore, even if there is moisture in the cold storage container, the moisture can be removed by the desiccant. Thereby, corrosion of the cold storage container caused by moisture can be suppressed.

  The invention described in claim 2 is characterized in that the desiccant is powdery. According to the invention described in claim 2, since the desiccant is in the form of powder, it is easy to handle and can be easily enclosed in the cold storage container. Moreover, since a desiccant disperse | distributes in a cool storage container as it is powdery, the water | moisture content collection effect can be improved more.

Further, in the invention according to claim 3, the regenerator material is mainly composed of paraffin,
The desiccant is characterized by being at least one of silica gel and zeolite.

  According to the invention of claim 3, the desiccant is at least one of silica gel and zeolite. Zeolite and silica gel have a relatively high moisture adsorption effect in a low humidity environment as a desiccant. The regenerator material is mainly composed of paraffin. Since the specific gravity of water is larger than that of paraffin, free water (water) stays downward in the cold storage container. Moreover, the specific gravity of powdery zeolite and silica gel is large with respect to paraffin like water. Therefore, these desiccants can effectively collect moisture located below in the cold storage container.

  Further, the invention according to claim 4 is characterized in that the desiccant is precipitated below the cold storage container. According to invention of Claim 4, since the desiccant has settled under the cool storage container, the water | moisture content settled under the cool storage container can be collected reliably.

  Further, the invention according to claim 5 is characterized in that the desiccant is scattered in the regenerator material. According to the invention described in claim 5, since the desiccant is scattered in the cold storage material, it is possible to reliably collect moisture scattered in the cold storage material.

  In addition, the code | symbol in the bracket | parenthesis of each above-mentioned means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a front view which shows the evaporator 40 of 1st Embodiment. It is a side view which shows the evaporator 40. FIG. It is an expanded sectional view which shows a part of III-III cross section of FIG. It is sectional drawing which shows the cool storage container 47 seeing from the front. The relationship between the amount of latent heat in the cool storage material 50 and temperature is shown. It is a graph which shows an example of the relationship between the particle system of the desiccant 51, and sedimentation time. It is sectional drawing which shows the cool storage container 47A of 2nd Embodiment seeing from the front.

  Hereinafter, a plurality of embodiments for carrying out the present invention will be described with reference to the drawings. In some embodiments, portions corresponding to the matters described in the preceding embodiments may be given the same reference numerals, or one letter may be added to the preceding reference numerals, and overlapping descriptions may be omitted. In addition, when a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those of the embodiment described in advance. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination does not hinder the combination.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a front view showing an evaporator 40 according to the first embodiment. FIG. 2 is a side view showing the evaporator 40. The evaporator 40 constitutes a refrigeration cycle apparatus (not shown). The refrigeration cycle apparatus is used for, for example, a vehicle air conditioner. Although not shown, the refrigeration cycle apparatus includes a compressor, a radiator, a decompressor, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path. The compressor is driven by a power source for running the vehicle. For this reason, when the power source stops, the compressor also stops. The compressor sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator. The radiator cools the high-temperature refrigerant. The radiator is also called a condenser. The decompressor decompresses the refrigerant cooled by the radiator. The decompressor can be provided by a fixed throttle, a temperature expansion valve, or an ejector. The evaporator 40 evaporates the refrigerant decompressed by the decompressor and cools the medium. The evaporator 40 cools the air supplied to the passenger compartment.

  The refrigeration cycle apparatus can further include an internal heat exchange for exchanging heat between the high-pressure side liquid refrigerant and the low-pressure side gas refrigerant, and a receiver or accumulator tank element that stores excess refrigerant. The power source can be provided by an internal combustion engine or an electric motor.

  The evaporator 40 is a cold storage heat exchanger and 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 to 44 positioned in pairs and a plurality of refrigerant pipes 45 connecting the headers 41 to 44.

  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 set and are arranged in parallel with 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 at its end. A first heat exchanging portion 48 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 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, the second heat exchange unit 49 is arranged on the upstream side, and the first heat exchange unit 48 is arranged on the downstream side.

  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 partitioned into a first partition and a second partition by a partition plate (not shown) provided approximately 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) 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, 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.

  Next, a specific configuration of the refrigerant pipe 45 and the like will be described. FIG. 3 is an enlarged cross-sectional view showing a part of the III-III cross section of FIG. In FIG. 3, the thickness of the cold storage container 47 is omitted, and the cold storage material 50 is hatched. The refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages 45a through which the refrigerant flows. The refrigerant tube 45 is also called a flat tube. This multi-hole tube can be obtained by an extrusion manufacturing method. The plurality of refrigerant passages 45 a extend along the longitudinal direction of the refrigerant pipe 45 and open at both ends of the refrigerant pipe 45. The plurality of refrigerant tubes 45 are arranged in a row. In each row, the plurality of refrigerant tubes 45 are arranged so that their main surfaces face each other. The plurality of refrigerant tubes 45 partition an air passage 460 for exchanging heat with air between two adjacent refrigerant tubes 45 and an accommodating portion 461 for accommodating a cold storage container 47 described later. .

  The evaporator 40 includes fins 46 for increasing the contact area with the air supplied to the passenger compartment. The fins 46 are provided by a plurality of corrugated fins 46. The fins 46 are disposed in an air passage 460 that is defined between two adjacent refrigerant tubes 45. The fin 46 is thermally coupled to the two adjacent refrigerant tubes 45. The 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 fin 46 has a shape in which a thin metal plate such as aluminum is bent in a wave shape, and includes an air passage 460 called a louver.

  Next, the cold storage container 47 will be described. FIG. 4 is a cross-sectional view showing the cold storage container 47 as viewed from the front. In FIG. 4, the thickness of the cold storage container 47 is omitted, and the cold storage material 50 is hatched. The evaporator 40 further includes a plurality of cold storage containers 47. The cold storage container 47 has a flat cylindrical shape. The cold storage container 47 is closed by crushing the cylinder in the thickness direction at both ends in the longitudinal direction, and a space for accommodating the cold storage material 50 is formed inside. The cold storage container 47 has a wide main surface on both surfaces. The two main walls that provide these two main surfaces are each arranged in parallel with the refrigerant pipe 45.

  The cold storage container 47 is disposed between two adjacent refrigerant tubes 45. The cold storage container 47 is thermally coupled to two refrigerant tubes 45 disposed on both sides thereof. The cold storage container 47 is joined to the two adjacent refrigerant pipes 45 by a joining material excellent in heat transfer. As the bonding material, a resin material such as a brazing material or an adhesive can be used. The cold storage container 47 is brazed to the refrigerant pipe 45. A large amount of brazing material is disposed between the cold storage container 47 and the refrigerant pipe 45 in order to connect them with a wide cross-sectional area. This brazing material can be provided by placing a brazing foil between the cold storage container 47 and the refrigerant pipe 45. As a result, the cold storage container 47 exhibits good heat conduction with the refrigerant pipe 45.

  The thickness of the cold storage container 47 is substantially equal to the thickness of the air passage 460. Therefore, the thickness of the cold storage container 47 is substantially equal to the thickness of the fin 46. The fin 46 and the cold storage container 47 can be interchanged. As a result, the arrangement pattern of the plurality of fins 46 and the plurality of cold storage containers 47 can be set with a high degree of freedom. The thickness of the cold storage container 47 is clearly larger than the thickness of the refrigerant pipe 45. This configuration is effective for accommodating a large amount of the cold storage material 50. The cold storage container 47 has substantially the same length as the fins 46. As a result, the cold storage container 47 occupies substantially the entire longitudinal direction of the accommodating portion 461 defined between the two adjacent refrigerant tubes 45. It is desirable to fill the gap between the cold storage container 47 and the headers 41 to 44 with a section of the fin 46 or a filler such as resin.

  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. In the plurality of gaps, a plurality of fins 46 and a plurality of cold storage containers 47 are arranged with a predetermined regularity. A part of the gap is an air passage 460. The remaining part of the gap is the accommodating part 461 of the cold storage container 47. Of the total interval formed between the plurality of refrigerant tubes 45, for example, 10% or more and 50% or less is the accommodating portion 461. A cool storage container 47 is disposed in the housing portion 461. The cold storage containers 47 are arranged almost uniformly distributed throughout the evaporator 40. The two refrigerant tubes 45 located on both sides of the cold storage container 47 define an air passage 460 for exchanging heat with air on the side opposite to the cold storage container 47. From another viewpoint, two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage container 47 is disposed between the two refrigerant tubes 45.

  Next, the cold storage container 47 will be described. The cold storage container 47 is made of metal such as aluminum and aluminum alloy. Further, as the material other than aluminum for the cold storage container 47, for example, a material containing a metal whose ionization tendency is lower than that of hydrogen as a main material or a component is used. When the cold storage container 47 is made of aluminum, zinc, chromium, iron, tin, magnesium, sodium, cobalt, nickel or the like, there is a possibility that it reacts with moisture to generate a corrosive gas (hydrogen).

  A desiccant 51 is enclosed in the cold storage container 47 together with the cold storage material 50. In FIG. 4, the size of the desiccant 51 is exaggerated. First, the cool storage material 50 enclosed in the cool storage container 47 will be described. FIG. 5 shows the relationship between the amount of latent heat and the temperature in the cold storage material 50. The necessary heat quantity of the cold storage material 50 is preferably about 200 kJ / kg or more in consideration of the capacity of the cold storage container 47. As a result, it is possible to secure the necessary cold storage capacity during idle stop. Further, the melting point capable of storing cold is preferably about 8 ° C. or higher because it is preferably at or above the cooling temperature zone during cooling. In general, organic materials have a low thermal conductivity and a large amount of supercooling except for paraffinic materials. In chemical heat storage, chemical stability, toxic poison, corrosiveness, reaction promoting means (pressure holding, stirring required). Therefore, in this embodiment, paraffin (for example, melting point 9.9 ° C.) is used as the cold storage material 50.

  As the other regenerator material 50, the regenerator material 50 that satisfies the above-mentioned requirements or that is close to the requirements but whose water is not the main component can be used. For example, polyglycol may be used. Moreover, since the specific gravity of water is large with respect to a paraffin when the paraffin is a main component, when the cold storage material 50 has a water | moisture content in the cold storage container 47, a water will precipitate in a paraffin. Further, in the cool storage container 47, some air is sealed above the cool storage material 50. The stress of the cold storage container 47 when the cold storage material 50 is expanded by the compression action of the air is relaxed.

  Next, the desiccant 51 enclosed with the cool storage material 50 in the cool storage container 47 is demonstrated. The desiccant 51 is used to collect moisture in the cold storage container 47. In the case where the moisture has a specific gravity relationship that precipitates in the regenerator material 50, it is preferable that the desiccant 51 is also precipitated in the regenerator material 50. In the present embodiment, since the cold storage material 50 is paraffin, the desiccant 51 preferably has a specific gravity greater than that of the cold storage material 50.

  FIG. 6 is a graph showing an example of the relationship between the particle system (particle size) of the desiccant 51 and the settling time. The settling time is the time taken for the desiccant 51 to settle under the cold storage container 47. In the graph shown in FIG. 6, the container height of the cold storage container 47 is set to 150 mm. The container height is determined by the cold storage capacity and the size of the evaporator 40. In the vehicle air conditioner, the height of the cold storage container 47 is preferably 150 mm or more in order to exhibit the cold storage capacity. If the settling time is less than 7 hours (hours) in the 150 mm cold storage container 47, for example, the desiccant 51 is precipitated in the cold storage container 47. Therefore, the lower limit value of the particle diameter is preferably set to a particle diameter that can reliably settle to the bottom of the cold storage container 47 in the cold storage container 47, and thus the particle diameter is preferably 10 μm or more. This is because if the particle size is less than 10 μm, it takes about 7 hours or more to settle in a stationary state, so that it can be determined that the particle does not actually settle due to vehicle vibration or the like.

  In addition, the upper limit of the particle size of the desiccant 51 is determined by the shape in the cold storage container 47, and in consideration of irregularities such as fins 46 in the cold storage container 47, the upper limit is 1 mm (= 1000 μm) or less. Is preferred. As a result, when the inner wall of the cold storage container 47 has irregularities, it can be reliably deposited without being irregularly caught by the irregularities. In other words, the maximum particle size of the desiccant 51 is determined due to the shape in the cold storage container 47.

  As such a desiccant 51, it is preferable to use at least one of silica gel and zeolite. Zeolite and silica gel have a relatively high moisture adsorption effect in the low humidity environment as the desiccant 51. Moreover, since the specific gravity of water is large with respect to a paraffin when the cold storage material 50 is a paraffin main component, in the cold storage container 47, a free water | moisture content (water | moisture content) stays below. The specific gravity of powdery zeolite and silica gel is large with respect to paraffin as well as water. Therefore, these desiccants 51 can effectively collect moisture in the paraffin located below.

  Specifically, when the cold storage container 47 is made of an aluminum material, the corrosion factor is moisture. Here, it can be understood that the corrosion reaction mainly involves the following reaction to generate hydrogen, and that moisture is the main factor of the reaction.

2Al + 6H ₂ O → 2Al (OH) ₃ + 3H ₂
Therefore, the above-described reaction in the cold storage container 47 can be suppressed by reliably removing moisture with the desiccant 51.

  Next, the operation of this embodiment will be described. When there is an air conditioning request from the passenger, for example, a cooling request, the compressor is driven by a power source. The compressor sucks the refrigerant from the evaporator 40, compresses it, and discharges it. The refrigerant discharged from the compressor is radiated by the radiator. The refrigerant discharged from the radiator is decompressed by the decompressor and supplied to the evaporator 40. The refrigerant evaporates in the evaporator 40 and cools the cold storage container 47 and cools the air through the fins 46. When the vehicle is temporarily stopped, the power source is stopped to reduce energy consumption, and the compressor is stopped. Thereafter, the refrigerant in the evaporator 40 gradually loses its cooling capacity. In this process, the cool storage material 50 gradually cools and cools the air. At this time, the heat of the air is conducted to the cold storage material 50 through the fins 46, the refrigerant pipe 45, and the cold storage container 47. As a result, even if the refrigeration cycle apparatus is temporarily stopped, the cool storage material 50 can cool the air. Eventually, when the vehicle starts running again, the power source drives the compressor again. For this reason, the refrigeration cycle apparatus cools the cold storage material 50 again, and the cold storage material 50 stores cold.

  As described above, the desiccant 51 is enclosed in the cool storage container 47 of this embodiment together with the cool storage material 50. As the material of the cold storage container 47, aluminum which is the same material as the evaporator 40 is often used in consideration of the brazing property with the evaporator 40. If there is moisture in the cold storage container 47, the aluminum may corrode. If hydrogen or the like is generated due to the corrosion of aluminum, the internal pressure may increase more than expected. Therefore, when hydrogen is generated, the pressure in the cold storage container 47 increases and the container may be deformed. However, in this embodiment, since the desiccant 51 is enclosed with the cool storage material 50, moisture can be removed from the cool storage container 47 by the desiccant 51. Thereby, corrosion of the cold storage container 47 due to moisture can be suppressed.

  Moreover, in this embodiment, since the desiccant 51 is a powder form, handling is easy and the enclosure to the cool storage container 47 becomes easy. Specifically, before the cool storage material 50 is sealed in the cool storage container 47, it may be put in the cool storage container 47, or the cool storage material 50 and the desiccant 51 may be mixed in advance. In addition, when the desiccant 51 is mixed, moisture originally contained in the cold storage material 50 can be removed, so that generation of moisture due to the cold storage material 50 can be suppressed.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 7 is a cross-sectional view showing the cold storage container 47A of the second embodiment as viewed from the front. In the present embodiment, the specific gravity of the desiccant 51 is different from that of the first embodiment. In FIG. 7, the thickness of the cold storage container 47A is omitted, the cold storage material 50 is hatched, and the size of the desiccant 51 is exaggerated.

  Paraffin is used as the cold storage material 50 in the same manner as in the first embodiment described above, but when the water does not contain enough water to generate free water, the water is scattered in the paraffin. In order to collect moisture in this state, the desiccant 51 is floated and uniformized in the paraffin by making the specific gravity of the desiccant 51 the same as that of paraffin. Further, in view of the influence of the particle size described above, it is possible to float the desiccant 51 in the paraffin as well as to make the specific gravity equal by setting the particle size of the desiccant 51 to 10 μm or less.

  With such a configuration, moisture that has not precipitated in the paraffin can be collected, so that adverse effects due to moisture generation can be prevented in advance.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In the first embodiment described above, the particle size of the regenerator material 50 is 10 μm or more, but is not limited to 10 μm or more, and the desiccant 51 combined with the desiccant 51 of the second embodiment may be used. That is, you may enclose both the desiccant 51 which precipitates, and the desiccant 51 scattered. This allows both moisture to be collected. Further, the desiccant 51 is not limited to powder and may be liquid.

  The refrigerant tube can be provided by a multi-hole extruded tube or a tube formed by bending a plate material on which dimples are formed. Furthermore, the fins can be omitted. Such a heat exchanger is also called a finless type. Instead of fins, protrusions extending from the refrigerant pipe may be provided to promote heat exchange with air.

  The present invention can be applied to an evaporator having various flow paths. For example, instead of the left and right U-turn type as in the first embodiment, the present invention may be applied to an evaporator such as a one-way type or a front and rear U-turn type.

  Furthermore, the present invention may be applied to refrigeration cycle apparatuses such as refrigeration, heating, and hot water supply. Furthermore, the present invention may be applied to a refrigeration cycle apparatus including an ejector.

  Moreover, you may provide an inner fin in the inside of a cool storage container. In such a configuration, an opening that exposes the top of the inner fin may be provided in the outer shell, and the top of the inner fin may be directly joined to the refrigerant pipe.

40 ... Evaporator (cold storage heat exchanger)
41 ... 1st header 42 ... 2nd header 43 ... 3rd header 44 ... 4th header 45 ... Refrigerant pipe 45a ... Refrigerant passage 46 ... Fin 47 ... Cold storage container 48 ... 1st heat exchange part 49 ... 2nd heat exchange part 50 ... cool storage material 51 ... desiccant 460 ... air passage 461 ... housing part

Claims (5)

A plurality of refrigerant pipes (45) having a refrigerant passage (45a) through which a refrigerant flows, and being spaced apart from each other;
A cold storage container for storing the cold storage material (50) therein, and a plurality of cold storage containers (47) arranged between two adjacent refrigerant pipes,
The cool storage heat exchanger is characterized in that a desiccant (51) is enclosed together with the cool storage material.   The cold storage heat exchanger according to claim 1, wherein the desiccant is powdery. The cold storage material is mainly composed of paraffin,
The regenerative heat exchanger according to claim 2, wherein the desiccant is at least one of silica gel and zeolite.   The cold storage heat exchanger according to any one of claims 1 to 3, wherein the desiccant is precipitated below the cold storage container.   The said desiccant is scattered in the said cool storage material, The cool storage heat exchanger as described in any one of Claims 1-3 characterized by the above-mentioned.

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