WO2013186983A1

WO2013186983A1 - Cold storage heat exchanger

Info

Publication number: WO2013186983A1
Application number: PCT/JP2013/003040
Authority: WO
Inventors: 貴志壇上; 山田　淳司; 井上　誠司; 西田　伸
Original assignee: 株式会社デンソー
Priority date: 2012-06-14
Filing date: 2013-05-13
Publication date: 2013-12-19
Also published as: JP2013256262A; US20150168047A1

Abstract

A cold storage heat exchanger (40) that exchanges heat with air flowing at the periphery of the heat exchanger, the heat exchanger including: refrigerant passages (45a) in which a refrigerant circulates; and cold storage containers (47, 47C, 47D, 47E, 47F, 47J) in which are housed cold storage materials (50a, 50b) that exchange heat with the refrigerant circulating in the refrigerant passages (45a) and retain an amount of heat. A plurality of the cold storage materials (50a, 50b) having different melting points are housed in the cold storage containers (47, 47C, 47D, 47E, 47F, 47J).

Description

Cold storage heat exchanger

Cross-reference of related applications

This disclosure is based on Japanese Application No. 2012-135042, filed on June 14, 2012, the contents of which are incorporated herein by reference.

The present disclosure 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.

Patent Documents 1 to 5 disclose techniques for solving such problems. 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 that encloses a cool storage material arranged behind the air flow of a conventional evaporator. Patent Documents 2 to 5 describe a system 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 The evaporator with a cool storage function of patent documents 2-5 collects cold air in the cool storage material by solidifying the cool storage material in the cool storage container during the operation of the air-conditioning compressor. And during the idle stop, the solid cool storage material is melted and the cool air is released into the air, so that the temperature change of the blown air is suppressed until the cool storage material is completely melted, and the air conditioning feeling is maintained. Can do.

However, when used in a temperature environment where the cold storage material cannot solidify during idle stop, a sufficient amount of cold air cannot be stored. Therefore, since it is not possible to release cold air for a long time, there is a problem that the idle stop time is shortened in order to maintain the air conditioning feeling.

Therefore, the present disclosure has been made in view of the above-described problems, and an object thereof is to provide a cold storage heat exchanger that can maintain a cold storage function in a wide range of air temperatures.

In order to achieve the above-mentioned object, in one aspect of the present disclosure, a cold storage heat exchanger that exchanges heat with air flowing around, the cold storage heat exchanger includes a refrigerant passage through which a refrigerant flows, a refrigerant A cold storage container that houses therein a cold storage material that exchanges heat with the refrigerant flowing through the passage to keep the amount of heat from the refrigerant, and the cold storage container contains a plurality of cold storage materials having different melting points. In the regenerator heat exchanger, the plurality of regenerator materials include a regenerator material having a high melting point and a regenerator material having a low melting point, and the regenerator material having a high melting point is provided upstream of the regenerator material having a low melting point.

According to this disclosure, a plurality of cool storage materials having different melting points are accommodated in the cool storage container. And the cool storage material with high melting | fusing point is provided in the upstream of an air flow rather than the cool storage material with low melting | fusing point. Therefore, for example, when the temperature of the refrigerant is equal to or lower than the melting point of the high melting point regenerator material and is equal to or higher than the melting point of the low melting point regenerator material, only the high melting point regenerator material is solidified. Therefore, cold storage can be performed even when the temperature of the refrigerant is high. Moreover, when the temperature of a refrigerant | coolant becomes still lower, all the cool storage materials will solidify. Therefore, since cold storage can be performed in stages according to the temperature of the refrigerant, the cold storage function can be maintained in a wider range of air temperatures.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings. The drawing
It is a front view which shows the evaporator 40 of 1st Embodiment. It is a side view which shows the evaporator 40 of 1st Embodiment. FIG. 3 is an enlarged cross-sectional view showing a part of a III-III cross section of FIG. 1. It is sectional drawing which shows the cool storage container 47 of 1st Embodiment. It is a figure for demonstrating the cool storage state of two

cool storage materials

50a, 50b of 1st Embodiment. It is an expanded sectional view showing a part of section of evaporator 40A of a 2nd embodiment. It is sectional drawing which shows the cool storage container 47 of 2nd Embodiment. It is sectional drawing which shows the cool storage container 47C of 3rd Embodiment. It is sectional drawing which shows the cool storage container 47D of 4th Embodiment. It is sectional drawing which shows the cool storage container 47E of 5th Embodiment. It is sectional drawing which shows the cool storage container 47F of 6th Embodiment. It is sectional drawing which shows the evaporator 40G of 7th Embodiment. It is sectional drawing which shows an example of the evaporator 40H of 8th Embodiment. It is sectional drawing which shows the other example of the evaporator 40I of 8th Embodiment. It is an expanded sectional view showing a part of evaporator 40 of a 9th embodiment. It is sectional drawing which shows the cool storage container 47 of 9th Embodiment. It is a figure for demonstrating the cool storage state of the two

cool storage materials

50a and 50b of 9th Embodiment.

Hereinafter, a plurality of embodiments 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)
The first embodiment will be described with reference to FIGS. 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 for storing excess refrigerant. The power source can be provided by an internal combustion engine or an electric motor.

As shown in FIGS. 1 and 2, the evaporator 40 is a cold storage heat exchanger and has a refrigerant passage member branched into a plurality of branches. 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 a pair and a plurality of refrigerant tubes 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.

At the end of the third header 43, a joint (not shown) as a refrigerant outlet is provided. 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. In FIG. 3, the thickness of the cool storage container 47 is omitted, and the

cool storage materials

50a and 50b are 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. 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 squeezing the cylinder in the thickness direction at both ends in the longitudinal direction, and spaces for accommodating the

cold storage materials

50a and 50b are 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. And it arrange | positions so that the refrigerant | coolant pipe | tube 45 may contact at least one surface, and this embodiment both surfaces.

A plurality of cold storage containers 47 are disposed between two adjacent refrigerant pipes 45, and in this embodiment, two cold storage cases 60 are arranged. Each cold storage case 60 is arranged along the flow direction of the intake air. In other words, the plurality of cool storage cases 60 are arranged to be different cool storage cases 60 on the upstream side and the downstream side of the air flow. Each cold storage case 60 accommodates

cold storage materials

50a and 50b having different melting points independently.

As shown in FIG. 4, each of the cold storage cases 60 is provided with one or more sealing ports 61 for sealing the

cold storage materials

50a and 50b. The sealing port 61 is provided on the upstream side (windward side) or the downstream side (leeward side) of the air flow in the outer periphery of the cold storage case 60. Hereinafter, when the cold storage case 60 is not specified, the cold storage case 47 is referred to.

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 each 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.

Also, 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

cool storage material

50a, 50b. The lengths of the cold storage containers 47 are equal to each other. Further, the length in which the two cold storage cases 60 are arranged 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. Accordingly, the two cold storage cases 60 arranged have the same area in contact with the refrigerant pipe 45. In other words, the two cold storage cases 60 arranged have the same area for heat exchange with the refrigerant pipe 45. Further, the gap between the cold storage container 47 and the headers 41 to 44 can be filled 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. In another aspect, two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage container 47 including two cold storage cases 60 is disposed between the two refrigerant tubes 45. Yes.

The cold storage container 47 is made of metal such as aluminum and aluminum alloy. In addition, as the material other than aluminum for the cold storage container 47, for example, a material containing a metal having a lower ionization tendency than hydrogen as a main material or a component is used.

Next, the

regenerator materials

50a and 50b will be described. The

cold storage materials

50a and 50b are materials that exchange heat with the refrigerant flowing through the refrigerant passage 45a to keep the amount of heat from the refrigerant. The

cold storage materials

50a and 50b are retained by solidifying the heat from the refrigerant, and are released to the outside by melting the retained heat. The cold storage material 50a having a high melting point is provided upstream of the cold storage material 50b having a low melting point. Therefore, in FIG. 3, the cool storage material 50a of the upper cool storage case 60 has a higher melting point than the cool storage material 50b of the lower cool storage case 60. Since the air heat load on the windward side of the evaporator 40 tends to increase, a high melting point regenerator material 50a that is easy to solidify even at a high temperature is disposed on the windward side, and a low melting point regenerator material 50b is disposed on the leeward side. Yes.

The melting point of the high-melting-point regenerator material 50a, which is a regenerator material having a high melting point, may be not less than the cooling temperature zone during cooling, and may be not less than 5 degrees Celsius and not more than 25 degrees Celsius. The melting point of the low melting point regenerator material 50b, which is a regenerator material having a low melting point, may be 0 degrees Celsius or more and 15 degrees Celsius or less. Further, when the melting point of the high melting point regenerator material 50a is 5 degrees Celsius or more and 15 degrees Celsius or less, the low melting point regenerator material 50b has a melting point of 0 degrees Celsius or more and lower than the melting point of the high melting point regenerator material 50a. Furthermore, since the melting point of the high melting point regenerator material 50a does not exceed the allowable temperature sensation of the blown air (= 15 to 17 ° C.), it may be 15 ° C. or less. The melting point of the low melting point regenerator material 50b may be 0 ° C. or higher and 10 ° C. or lower so that it can be solidified and melted even at low temperatures such as in winter. The necessary heat quantity of the two

cold storage materials

50a and 50b may be 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.

Generally, organic materials have low thermal conductivity and large 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, two types of paraffin are used as the

cold storage materials

50a and 50b.

The paraffin used for the high melting point regenerator material 50a may have 16 or 15 carbon atoms. Moreover, the paraffin used for the low melting-point cold storage material 50b should just have 15 or 14 carbon atoms. And when the carbon number of the paraffin of the high melting point regenerator material 50a is 16, the carbon number of the low melting point regenerator material 50b may be 15 or 14, and when the carbon number of the paraffin of the high melting point regenerator material 50a is 15, The number of carbon atoms in the paraffin of the melting point regenerator material 50b may be 14. Thereby, even if it is the same paraffin, melting | fusing point can mutually differ. Moreover, you may use the cool storage material which has a hydrate as a main component.

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, cools the cold storage container 47, and cools the surrounding 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

regenerator materials

50a and 50b gradually cool and cool the air. At this time, the heat of the air is conducted to the

cold storage materials

50a and 50b 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 air can be cooled by the

cold storage materials

50a and 50b. 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 materials

50a and 50b again, and the

cold storage materials

50a and 50b store cold.

A more specific operation will be described with reference to FIG. 5. When the air conditioner is operated under normal high load control in the summer or intermediate period, the refrigerant temperature is the high melting point regenerator 50a (in FIG. 5). A) is below the melting point of both of the low melting point regenerator material 50b (B in FIG. 5) and solidifies to cool. And during idle stop, the solidified cold storage material melts and releases the cool air accumulated while being released into the air, thereby suppressing the temperature rise of the blown air and extending the idle stop time.

When using the fuel saving mode, the refrigerant temperature is higher than when the load is high. In such a case, only the high-melting-point regenerator material 50a can solidify and store cold air when the air conditioner is activated. During the idling stop in the fuel saving mode, the high-melting-point regenerator material 50a is released while the cold air accumulated while being melted is released into the air, thereby suppressing the temperature rise of the blown air and extending the idling stop time.

As described above, in the evaporator 40 of the present embodiment, in the cool storage container 47, two

cool storage materials

50a and 50b are separately accommodated as the plurality of

cool storage materials

50a and 50b having different melting points. Yes. And the cool storage material 50a with high melting | fusing point is provided in the upstream of an air flow rather than the cool storage material 50b with low melting | fusing point. Therefore, when the temperature of the refrigerant is, for example, equal to or lower than the melting point of the high melting point regenerator material 50a and equal to or higher than the melting point of the low melting point regenerator material 50b, only the high melting point regenerator material 50a is solidified. Therefore, cold storage can be performed even when the temperature of the refrigerant is high. Moreover, if the temperature of a refrigerant | coolant becomes still lower, all the

cool storage materials

50a and 50b will solidify. Therefore, since cold storage can be performed in stages according to the temperature of the refrigerant, the cold storage function can be maintained in a wider range of air temperatures.

The sealing port 61 is provided on the upstream side or the downstream side of the air flow in the outer periphery of the cold storage case 60. Therefore, since the sealing port 61 is not provided in the air passage 460, it is possible to prevent a ventilation resistance.
(Second Embodiment)
Next, a second embodiment will be described using FIG. 6 and FIG. The present embodiment is characterized in that the cold storage cases 60A are arranged so as to contact each other. Since it is the structure which is contacting in this way, space can be utilized more effectively. Therefore, the amount of the

regenerator materials

50a and 50b that can be filled can be increased. The operations and effects in the other configurations are the same as those in the first embodiment.
(Third embodiment)
Next, a third embodiment will be described with reference to FIG. The present embodiment is characterized in that the inside of the cold storage container 47C is partitioned by the partition 70, and the

cold storage materials

50a and 50b having different melting points are accommodated in the partitioned spaces. The cool storage container 47C is provided with one sealing port 61 for sealing the

cool storage materials

50a and 50b. Therefore, two kinds of

cool storage materials

50a and 50b are sealed from one sealing port 61. Therefore, the configuration is simplified, and handling as the cold storage container 47C is facilitated. Further, the sealing port 61 is provided on the upstream side or the downstream side of the air flow in the outer periphery of the cold storage container 47C, and is provided on the leeward side in the present embodiment. Since it is such a structure, a space can be utilized more effectively. Therefore, the amount of the

regenerator materials

50a and 50b that can be filled can be increased. The operations and effects in the other configurations are the same as those in the first embodiment.
(Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG. The present embodiment is characterized in that the cold storage cases 60D are arranged so as to be separated from each other, and the two sealing ports 61 are on the same side. Even with such a configuration, it is possible to achieve the same operations and effects as in the first embodiment.
(Fifth embodiment)
Next, a fifth embodiment will be described with reference to FIG. The present embodiment is characterized in that the cold storage cases 60E are integrally formed so as to be in contact with each other, and the two sealing ports 61 are on the same side. Even with such a configuration, the same operations and effects as those of the second embodiment described above can be achieved.
(Sixth embodiment)
Next, a sixth embodiment will be described with reference to FIG. The present embodiment is characterized in that the cold storage cases 60F are integrally formed so as to be in contact with each other, and the two sealing ports 61 are on the same side. Furthermore, the one inlet 61 is constituted by a pipe 61F. Even with such a configuration, the same operations and effects as those of the second embodiment described above can be achieved.
(Seventh embodiment)
Next, a seventh embodiment will be described with reference to FIG. The present embodiment is characterized in that the cold storage case 60G is arranged on one surface of the refrigerant passage 45a. The configuration shown in FIG. 12 is a so-called drone cup type. By arranging it on one side of the refrigerant passage 45a, the entire space can be saved. Even with such a configuration, it is possible to achieve the same operations and effects as in the first embodiment.
(Eighth embodiment)
Next, an eighth embodiment will be described with reference to FIGS. 13 and 14. This embodiment is also characterized in that cold storage cases 60H and 60I are arranged on one side of the refrigerant passage 45a, as in the seventh embodiment. The two cold storage cases 60H and 60I extend along the air flow direction and are arranged along the air flow direction. Moreover, in the example shown in FIG. 13, the cool storage case 60H is arrange | positioned at intervals in the air flow direction. In the example illustrated in FIG. 14, the cold storage case 60I is disposed so as to be in contact with the air flow direction. By arranging the cold storage cases 60H and 60I on only one side of the refrigerant passage 45a as described above, the space can be saved as a whole. In addition, the same operations and effects as those of the first embodiment described above can be achieved.
(Ninth embodiment)
Next, a ninth embodiment will be described with reference to FIGS. As shown in FIGS. 15 and 16, this embodiment is characterized in that one type of cool storage material 50 is accommodated in each cool storage container 47 </ b> J. Further, one of the adjacent cool storage containers 47J is characterized in that the high melting point cold storage material 50a is accommodated and the other is accommodated in the low melting point cold storage material 50b. This embodiment can be applied when the cooling capacity of the evaporator 40J is sufficiently high.

Therefore, the cold storage container 47J for storing the high melting point cold storage material 50a and the cold storage container 47J for storing the low melting point cold storage material 50b are alternately arranged between the refrigerant tubes 45. 15 and 16 show a cold storage container 47J in which the high melting point cold storage material 50a is accommodated.

The specific operation will be described with reference to FIG. 17. When the air conditioner is operated under normal high load control in the summer or intermediate period, the refrigerant temperature is the high melting point regenerator 50a (A in FIG. 17). ), Lower than both melting points of the low-melting-point regenerator material 50b (B in FIG. 17), and solidifies to cool. And during idle stop, the solidified cold storage material melts and releases the cool air accumulated while being released into the air, thereby suppressing the temperature rise of the blown air and extending the idle stop time.

In the first embodiment described above, when the temperature on the windward side of the evaporator 40 is high and the low melting point regenerator material 50b does not solidify, the high melting point regenerator material 50a is disposed on the windward side and the low melting point regenerator material 50b is disposed on the leeward side. be able to. However, when the cooling capacity of the evaporator 40J is sufficiently high as in the present embodiment and the temperature of the evaporator 40J decreases substantially uniformly in the air flow direction, it is not necessary to arrange the high melting point regenerator 50a only on the windward side. . Therefore, even if the single cold storage container 47J is arranged in the air flow direction as in the present embodiment, the same operations and effects as those in the first embodiment can be achieved.

In this embodiment, the cold storage containers 47J having different melting points are alternately arranged (high melting point-low melting point-high melting point ...), but are not limited to each other, for example, not one by one but two by two. They may be arranged alternately (high melting point-high melting point-low melting point-low melting point-high melting point-high melting point ...), or may be alternately arranged in units of three. In other words, at least some of the

cool storage materials

50a and 50b accommodated in the plurality of cool storage containers 47J may be configured to have a different melting point from the cool storage material 50b accommodated in the other cool storage containers. . Therefore, it is not necessary that the number of the cold storage containers 47J for storing the high melting point cold storage material 50a and the number of the cold storage containers 47J for storing the low melting point cold storage material 50b are the same. Depending on the temperature distribution of the refrigerant flowing through the evaporator 40J, the melting point and the capacity of the cool storage material 50 accommodated in each cool storage container 47J may be selected as appropriate.

The embodiment has been described above, but the present disclosure is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present disclosure.

The structure of the above embodiment is merely an example, and the scope of the present disclosure is not limited to the scope of these descriptions. The scope of the present disclosure is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

In the first embodiment and the ninth embodiment described above, the

cold storage materials

50a and 50b are two types, but are not limited to two types, and may be three or more types. As a result, cold storage can be performed in stages, and a wider range of air-conditioning temperature can be accommodated.

The refrigerant pipe 45 can be provided by a multi-hole extruded pipe or a pipe 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.

Further, the cold storage case 60 may not be arranged on the outer periphery of the refrigerant pipe 45, and the cold storage case may be arranged in the refrigerant passage. Further, the number of cold storage cases 60 may be one. For example, a heat exchanger may be placed horizontally and a regenerator material having a high melting point and a high specific gravity and a regenerator material having a low melting point and a low specific gravity may be disposed and enclosed in a single container. Accordingly, a cold storage material having a high melting point can exist upstream of the air flow without preparing a plurality of cold storage cases and dividing them.

In the first embodiment described above, there are a plurality of types of regenerator materials. However, a mixture of the respective regenerator materials may be employed.

The present disclosure 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 disclosure may be applied to an evaporator such as a one-way type or a front and rear U-turn type.

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

Further, an inner fin may be provided inside the cold storage container 47. 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.

Although the present disclosure has been described based on an embodiment, it is understood that the present disclosure is not limited to the embodiment or the structure. The present disclosure includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, as well as other combinations and forms including only one element, more or less, are within the scope and spirit of the present disclosure.

Claims

A regenerative heat exchanger (40) for exchanging heat with air flowing around it,
A refrigerant passage (45a) through which the refrigerant flows;
A cold storage container (47, 47C, 47D, 47E, 47F, 47J) containing therein a cold storage material (50a, 50b) for exchanging heat with the refrigerant flowing through the refrigerant passage (45a) and retaining the amount of heat from the refrigerant; Including,
The regenerator (47, 47C, 47D, 47E, 47F, 47J) accommodates a plurality of the regenerators (50a, 50b) having different melting points.
The plurality of cold storage materials (50a, 50b) include a cold storage material (50a) having a high melting point and a cold storage material (50b) having a low melting point,
The regenerator heat exchanger according to claim 1, wherein the regenerator material (50a) having a high melting point is provided upstream of the regenerator material (50b) having a low melting point.
The cold storage containers (47, 47C, 47D, 47E, 47F, 47J) are plural (47J),
Each cool storage container (47J) contains one type of cool storage material (50a, 50b),
The regenerator material (50a) accommodated in at least a part of the plurality of regenerator containers (47J) is different in melting point from the regenerator material (50b) accommodated in the other regenerator container (47J). Item 2. The cold storage heat exchanger according to Item 1.
The plurality of regenerator materials (50a, 50b) are regenerator materials (50a, 50b) having two different melting points,
The melting point of the regenerator material (50a) having a high melting point is 5 degrees Celsius or more and 25 degrees Celsius or less,
The melting point of the cold storage material (50b) having a low melting point is 0 degree Celsius or more and 15 degrees Celsius or less,
When the melting point of the regenerator material (50a) having a high melting point is not less than 5 degrees Celsius and not more than 15 degrees Celsius, the regenerator material (50b) having a low melting point is not less than 0 degrees Celsius, and the regenerator material having a high melting point The regenerative heat exchanger according to any one of claims 1 to 3, wherein the regenerator heat exchanger is less than the melting point of (50a).
The refrigerant pipe (45) forming the refrigerant passage (45a) is disposed on at least one surface of the cold storage container (47, 47C, 47D, 47E, 47F, 47J). The cold storage heat exchanger as described in any one of these.
The cold storage container (47, 47D, 47E, 47F) includes a plurality of cases (60, 60A, 60D, 60E, 60F, 60G, 60H, 60I) independent from each other,
The plurality of cases (60, 60A, 60D, 60E, 60F, 60G, 60H, 60I) are arranged to be different cases on the upstream side and the downstream side of the air flow,
Each of the plurality of cases (60, 60A, 60D, 60E, 60F, 60G, 60H, 60I) contains a corresponding cold storage material (50a, 50b) having a different melting point. 2. The cold storage heat exchanger according to 2.
Each of the plurality of cases (60, 60A, 60D, 60E, 60F) is provided with one or more sealing ports (61, 61F) for sealing the corresponding cold storage material (50a, 50b). The regenerative heat exchanger according to claim 6.
The inside of the cold storage container (47C) is partitioned by a partition (70),
The cold storage material (50a, 50b) having a different melting point is accommodated in each of the plurality of spaces partitioned by the partition (70), according to any one of claims 1 and 2. The regenerative heat exchanger described.
The cool storage heat according to claim 8, wherein the cool storage container (47C) is provided with one or more sealing ports (61) for sealing the plurality of cool storage materials (50a, 50b). Exchanger.
The one or more sealing ports (61, 61F) are arranged on the upstream side or the downstream side of the air flow in the outer periphery of the cold storage container (47C) or the corresponding case (60, 60A, 60D, 60E, 60F). The regenerative heat exchanger according to claim 7 or 9, wherein the regenerative heat exchanger is provided.
The cold storage heat exchanger according to any one of claims 1 to 10, wherein the plurality of cold storage materials (50a, 50b) are mainly composed of paraffin or hydrate.
The paraffin used for the cold storage material (50a) having a high melting point has 16 or 15 carbon atoms,
The paraffin used for the cold storage material (50b) having a low melting point has 15 or 14 carbon atoms,
When the carbon number of the paraffin of the cold storage material (50a) having a high melting point is 16, the carbon number of the paraffin of the cold storage material (50b) having a low melting point is 15 or 14,
The regenerator heat according to claim 4, wherein when the carbon number of the paraffin of the regenerator material (50a) having a high melting point is 15, the carbon number of the paraffin of the regenerator material (50b) having a low melting point is 14. Exchanger.